JP2001082831A - Adsorber for absorption refrigerating machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent refrigeration capacity from lowering by eliminating valves disposed between the casing of an adsorber, the casing of an evaporator and the casing of a condenser. SOLUTION: A heat exchanger 230 serving as an evaporator and a condenser is provided with fins 232. Since the surface area can be prevented from decreasing at a part function as an evaporator or a condenser, heat exchanging capacity as an evaporator or a condenser can be prevented from lowering. Since liquid phase refrigerant evaporating (boiling) and scattering to the upper side touch a part of the heat exchanger 230 located above the liquid level at high probability, the scattering liquid phase refrigerant can also be evaporated. Since a small heat exchanger 230 can serve as an evaporator and a condenser, no valve is required in the vacuum system.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an adsorber for an adsorption refrigerator, and is effective when applied to an air conditioner.

[0002]

2. Description of the Related Art As is well known, an adsorption type refrigerator obtains a refrigerating capacity by evaporating a liquid-phase refrigerant such as water in a casing maintained at a substantially vacuum, and obtains a refrigerating capacity by evaporating latent heat. (Steam) is adsorbed by the adsorbent to promote evaporation and to exert a refrigerating ability continuously.

When the water adsorbing capacity of the adsorbent is saturated, the adsorbent is heated to evaporate and desorb (regenerate) the adsorbed refrigerant (water), and the desorbed gas-phase refrigerant (regenerated). (Water vapor) is cooled and condensed and returned to the liquid-phase refrigerant.

For this reason, in the casing of the adsorber for the adsorption refrigerator, an adsorption core to which an adsorbent is adhered, a condenser for condensing (cooling) the desorbed vapor refrigerant, and evaporating the liquid-phase refrigerant. An evaporator was needed.

The evaporator and the condenser have no means for increasing the outer surface area such as fins, and are constructed by disposing a tube through which a heat medium flows in a meandering state in a casing. It was done.

[0006]

Since the evaporator evaporates the liquid-phase refrigerant, the evaporator needs to be immersed in the liquid-phase refrigerant, whereas the condenser has the desorbed gas. Since it is for cooling the phase refrigerant, it must be located above the liquid level (water level) of the liquid phase refrigerant.

In addition, in the adsorption type refrigerator, when obtaining the refrigerating capacity, a heat medium such as water is circulated in the evaporator to take out the refrigerating capacity generated in the adsorber, and on the other hand, the adsorbent is regenerated (water content). ), It is necessary to circulate a heat medium through the condenser to cool the gas-phase refrigerant, so that the evaporator and the condenser are generally disposed in separate casings,
Each of the casings was connected to a casing provided with an adsorption core by a pipe through which steam flows. Then, the flow of the heat medium (including steam) is switched by switching means such as a valve provided in the pipe.

[0008] However, if movable parts such as valves are provided in the piping for steam which is a vacuum system, air enters the vacuum system from the movable part, the pressure in the casing rises, and the refrigerating capacity decreases. Is easy to occur.

Further, if a single heat exchanger serves as both an evaporator and a condenser, for example, a portion above the liquid surface does not function as an evaporator, while a portion below the liquid surface does not function as a condenser. Since the heat exchanger does not function as a heat exchanger, the heat exchanger (adsorber) that serves as the heat evaporator and the condenser is increased in size.

SUMMARY OF THE INVENTION In view of the foregoing, it is an object of the present invention to eliminate a vacuum system valve and prevent a decrease in refrigeration capacity while suppressing an increase in the size of an adsorber.

[0011]

According to the present invention, in order to achieve the above object, according to the first aspect of the present invention, a casing (210) in which a refrigerant is sealed, and a casing (210).
Between the adsorbent core (220), which is disposed on the upper side and to which the adsorbent (221) is adhered, and the fluid and the refrigerant, which are disposed on the lower side in the casing (210) and which are supplied from the outside. A heat exchanger (230) for performing heat exchange. The heat exchanger (230) includes a tube (231) through which a fluid flows and a fin (2) that increases the outer surface area of the tube (231).
32) and a core portion (234).

Thus, even when one heat exchanger (230) is used as both an evaporator and a condenser,
Since the surface area of the portion functioning as the evaporator or the condenser can be prevented from being reduced, it is possible to prevent the heat exchange capacity of the evaporator or the condenser from being reduced.

When the liquid-phase refrigerant evaporates (boils), the liquid-phase refrigerant scatters above the liquid surface due to the evaporation pressure. At this time, in the present invention, the fins (23
Since the outer surface area is increased by providing (2), there is a high possibility that the scattered liquid-phase refrigerant comes into contact with the portion of the heat exchanger (230) located above the liquid surface.

Therefore, in addition to the increase in the outer surface area below the liquid surface, the scattered liquid-phase refrigerant can also be evaporated, so that the water level is lowered and the condensation area is increased to improve the condensation performance. In addition, it is possible to prevent the evaporation performance from being lowered by lowering the water level.

Therefore, compared to a heat exchanger in which an evaporator and a condenser are simply combined, while reducing the size thereof,
Since the function of the evaporator and the function of the condenser can be performed by one heat exchanger (230), the vacuum system valve can be eliminated while preventing the adsorber from being enlarged.

[0016] For this reason, it is possible to prevent the fluidity of the vaporized gaseous refrigerant from being impaired, so that it is possible to prevent the adsorbent (221) from lowering the water adsorption speed. As a result, an increase in pressure in the casing (210) can be reliably suppressed, so that a decrease in refrigeration capacity can be reliably prevented.

The outer surface area of the tube (231) is
As in the second aspect of the present invention, it is desirable that the inner surface area of the tube (231) be 5 times or more and 15 times or less.

According to a third aspect of the present invention, the pitch of the fins (232) is 0.7 mm or more and 2 mm or more.
The fin height of the fin (232) is 4.5 mm
As mentioned above, it is desirable to set it to 8 mm or less.

According to the fourth aspect of the present invention, the heat exchanger (2)
30) is a casing (21) such that the ridge direction (D) connecting the peaks of the fins (232) matches the vertical direction.
0).

Thus, when the heat exchanger (230) functions as an evaporator, the vaporized refrigerant can smoothly flow toward the adsorption core (220).

The maximum liquid level of the liquid-phase refrigerant present in the casing (210) is at least １ ／ of the vertical dimension (h) of the core portion (234). It is desirable to set so as to be 1/2 or less.

Further, the liquid-phase refrigerant present in the casing (210) due to the evaporation or condensation of the refrigerant has a liquid level fluctuation width of 25 times the vertical dimension of the core part (234). % Is desirable.

According to the seventh aspect of the present invention, the suction core (2
20) has a plurality of flat core tubes (222) through which fluid flows and core fins (223) disposed between the core tubes (222);
An adsorbent (221) is attached to at least one of the core tube (222) and the core fin (223).

Thus, the contact area between the adsorbent (221) and the adsorption core (220) can be increased.
The heat transfer (heat transfer amount) between the two can be improved.

The dimension (W) in the major axis direction of the core tube (222) is 5 mm as in the invention according to claim 8.
As mentioned above, it is desirable to set it to 25 mm or less.

According to the ninth aspect of the present invention, the pitch of the core fins (223) is at least 0.4 mm.
4mm or less, fin height is 5mm or more, 10m
m or less.

The average particle size of the adsorbent (221) is at least 0.05 mm, as in the tenth aspect of the present invention.
It is desirable to set it to 0.6 mm or less.

According to the eleventh aspect of the present invention, the adsorbent (2
21) The upstream adsorbent positioned upstream in the flow direction of the fluid flowing through the core tube (222) and the downstream adsorbent positioned downstream in the flow direction of the fluid flowing through the core tube (222) Is the difference in the moisture adsorption characteristics determined by the ratio of the amount of change in the amount of moisture adsorption to the amount of change in the relative humidity, and furthermore, the relative humidity at the rising point where the moisture adsorption characteristics of the upstream adsorbent greatly changes. Is characterized by being higher than the relative humidity at the rising point of the downstream adsorbent.

Thus, the conditioned air can be efficiently dehumidified and cooled.

Further, the adsorbent (221) can secure a difference of 15% or more in water adsorption rate when the relative humidity is 10% or more and 30% or less, as in the twelfth aspect. Desirably.

By the way, the reference numerals in parentheses of the respective means are examples showing the correspondence with specific means described in the embodiments described later.

[0032]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
FIG. 1 is a schematic diagram of an air conditioner in which an adsorber for an adsorption refrigerator (hereinafter, abbreviated as an adsorber) according to the present invention is applied to an adsorption refrigerator for a vehicle air conditioner.

In FIG. 1, reference numeral 100 denotes a water-cooled engine (water-cooled internal combustion engine) for running a vehicle, and reference numerals 200 and 300 denote first and second adsorbers according to the present embodiment. Since the first and second adsorbers 200 and 300 are the same, when there is no need to particularly distinguish them (when they are collectively referred to), they are simply referred to as the adsorber 200.

Reference numeral 400 denotes an air-conditioning casing (hereinafter abbreviated as a casing) which constitutes a passage of air blown into the room. (Hereinafter, it is abbreviated as a blower.) 410 is provided. 420
Is an indoor heat exchanger that cools the air flowing through the casing 400. The indoor heat exchanger obtains the refrigerating capacity from the adsorber 200 via a heat medium. In this embodiment, a fluid in which ethylene glycol-based antifreeze is mixed with water as a heat medium (the same as the cooling water of engine 100)
Is adopted.

FIG. 2 is a schematic view of the adsorber 200. A predetermined amount of refrigerant (in this embodiment, water) is sealed in a casing 210 maintained in a substantially vacuum state. On the upper side, an adsorption core 220 to which an adsorbent 221 (see FIG. 1) is attached is housed and arranged, while on the lower side, heat exchange is performed between the heat medium fluid and the refrigerant in the casing 210. Heat exchanger (evaporation / condensation core) 23
0 is stored and arranged. In the present embodiment, silica gel is employed as the adsorbent 221.

As shown in FIG. 3, the suction core 220 is composed of a plurality of flat core tubes 222 through which a heat medium flows and corrugated core fins 223 disposed between the core tubes 222. And an adsorbent 221 bonded to at least one of the core tube 222 and the core fin 223.

Reference numeral 224 denotes a first header tank for distributing and supplying a heat medium to each core tube 222.
A second header tank collects and recovers the heat medium that has exchanged heat with the adsorbent 221.

As shown in FIG. 4, the heat exchanger 230 has a flat tube 23 through which a heat medium flows.
1 and a core part 234 composed of fins 232 for increasing the outer surface area of the tube 231.
The outer surface area S ₁ of the tube 231 is
5 times or more and 15 times or less of the inner surface area S ₂ of 1
In the present embodiment, the outer surface area S ₁ is about 13 times the inner surface area S ₂ .

Incidentally, reference numeral 235 denotes a first header tank for distributing and supplying a heat medium to each tube 222, and 236 denotes a second header for collecting and recovering the heat medium having exchanged heat with the refrigerant.
It is a header tank.

The fins 232 are corrugated fins having a plurality of peaks and valleys and formed in a wavy shape. The heat exchanger 230 is formed by connecting the peaks (or valleys) of the fins 232. The ridge direction D is arranged in the casing 210 such that the ridge direction D matches the vertical direction.

By the way, in FIG.
An outdoor heat exchanger for exchanging heat between the heat medium flowing out of the heat exchanger and the outdoor air to cool the heat medium, and 510 and 520 are switching valves for switching the circulation path of the heat medium.
The operations of the pumps 10 and 520, a pump (not shown) for circulating the heat medium, and the blower 410 are controlled by an electronic control unit (not shown).

Next, the operation of the air conditioner according to this embodiment will be described.

First, as shown in FIG. 1, the pump and the blower 410 are operated to circulate the heat medium and the air, and the switching valves 510 and 520 are operated to operate the first adsorber 2.
00 between the adsorption core 220 (core tube 222) and the outdoor heat exchanger 500, and the heat exchanger 330 of the second adsorber 300.
(Tube 331) and the outdoor heat exchanger 500, between the engine 100 and the adsorption core 320 (core tube 322) of the second adsorber 300, and the heat exchanger 230 (tube 231) of the first adsorber 200. And indoor heat exchanger 420
The heat medium is circulated between the heat medium and the heat medium. Hereinafter, such a state is referred to as a first state.

At this time, the heat exchanger 2 of the first adsorber 200
In 30, the heat medium heated by the air blown into the room circulates, so that the liquid-phase refrigerant in the first adsorber 200 is evaporated, and the latent heat of evaporation at the time of evaporation of the liquid-phase refrigerant is applied to the heat exchanger 230. The air that is blown into the room is cooled by the cooled heat medium.

At the same time, the adsorption core 220 of the first adsorber 200 adsorbs the evaporated gas-phase refrigerant to promote evaporation. The adsorbent 221 generates heat (condensation heat) when adsorbing the gas-phase refrigerant, and when the temperature of the adsorbent 221 increases, the adsorbing capacity of moisture decreases. The heat medium is circulated between the core 220 and the core 220 to suppress the temperature rise of the adsorbent 221. Note that
The adsorber in such a state is called an adsorber in an evaporating / adsorbing state.

On the other hand, the suction core 320 of the second suction device 300
Since the cooling water of the engine 100 flows into the, the adsorbent 321 bonded to the adsorption core 320 is heated, and the adsorbed moisture is released (desorbed). At this time, since the heat medium cooled by the outdoor heat exchanger 500 is flowing through the heat exchanger 330 of the second adsorber 300, the desorbed gas-phase refrigerant (steam) flows into the heat exchanger 330. Is cooled and condensed. Hereinafter, the adsorber in such a state is referred to as an adsorber in a condensation / desorption state.

As described above, in the first state, the first adsorber 2
At 00, evaporation of the refrigerant and adsorption of the evaporated gas-phase refrigerant are performed, while, at the second adsorber 300,
Desorption of the adsorbed water and cooling and condensation of the evaporated gas-phase refrigerant are performed. Therefore, the heat exchanger 230 of the first adsorber 200 functions as an evaporator for evaporating the liquid-phase refrigerant, and the heat exchanger 330 of the second adsorber 300 functions as a condenser for condensing the gas-phase refrigerant.

Next, when the operation in the first state has elapsed for a predetermined time, as shown in FIG.
To operate between the adsorption core 320 (core tube 322) of the second adsorber 300 and the outdoor heat exchanger 500, and between the heat exchanger 230 (tube 231) of the first adsorber 200 and the outdoor heat exchanger 500. , Engine 100 and first adsorber 20
0 and the heat exchanger 330 (the tube 33) of the second adsorber 300.
The heat medium is circulated between 1) and the indoor heat exchanger 420. Hereinafter, such a state is referred to as a second state.

At this time, the heat exchanger 3 of the second adsorber 300
In 30, the heat medium heated by the air blown into the room circulates, so that the liquid-phase refrigerant in the second adsorber 300 is evaporated, and the heat of evaporation of the liquid-phase refrigerant is transferred to the heat exchanger 330 by the latent heat of evaporation. The air that is blown into the room is cooled by the cooled heat medium.

At the same time, the adsorption core 320 of the second adsorber 300 adsorbs the vaporized refrigerant and suppresses a rise in the pressure in the casing 210, and the outdoor heat exchanger 500 and the adsorption core 320 The heat medium is circulated between the heat sink and the temperature controller to suppress the temperature rise of the adsorbent 321.

On the other hand, the suction core 220 of the first suction device 200
In the first state, the adsorbent 221 adhered to the adsorption core 220 is heated in the first state, and the adsorbed water is released (desorbed). At this time, since the heat medium cooled by the outdoor heat exchanger 500 flows through the heat exchanger 230 of the first adsorber 200,
The desorbed gas-phase refrigerant (steam) is cooled by the heat exchanger 230 and condensed.

As described above, in the second state, the second adsorber 3
In 00, evaporation of the refrigerant and adsorption of the evaporated gas-phase refrigerant are performed, while in the first adsorber 200,
Desorption of the adsorbed water and cooling and condensation of the evaporated gas-phase refrigerant are performed. Therefore, the heat exchanger 330 of the second adsorber 300 functions as an evaporator for evaporating the liquid-phase refrigerant, and the heat exchanger 230 of the first adsorber 200 functions as a condenser for condensing the gas-phase refrigerant.

When the predetermined time has elapsed, the first state is set again. As described above, the air conditioner (adsorption refrigerator) is continuously operated while repeating the first state and the second state at predetermined time intervals. The predetermined time is selected based on the moisture adsorption capacity of the adsorbent 221 in the adsorber 200 (adsorption core 220).

Next, the features of this embodiment will be described.

According to this embodiment, the heat exchanger 230 of the adsorber 200 functions as an evaporator when the adsorber 200 is in the evaporating / adsorbing state, and when the adsorber 200 is in the condensing / desorbing state. Functions as a condenser.

That is, unlike the prior art, there is no need to provide an evaporator and a condenser independently of each other, so there is no need to provide a valve as a movable part in the vacuum system. Therefore, it is possible to prevent the fluidity of the evaporated gas-phase refrigerant from being impaired, so that it is possible to prevent the moisture adsorption speed of the adsorption core (adsorbent) 220 from decreasing. As a result, an increase in the pressure in the casing 210 can be reliably suppressed, so that a decrease in the refrigerating capacity can be reliably prevented.

Incidentally, in order for one heat exchanger 230 to serve as both an evaporator and a condenser, one heat exchanger 23 is used.
It is necessary that at least a part of zero is immersed below the liquid surface of the liquid-phase refrigerant, and other parts are exposed (exposed) above the liquid surface.

For this reason, if the evaporator and the condenser are simply used by one heat exchanger, the surface area of the part functioning as the evaporator or the condenser has the evaporator and the condenser provided independently. And the heat exchange capacity as an evaporator or a condenser may be reduced.

On the other hand, in the present embodiment, the fin 2
Since the outer surface area is increased by providing 32, the surface area of a portion functioning as an evaporator or a condenser can be prevented from being reduced, and the heat exchange capacity as an evaporator or a condenser can be prevented from being reduced. .

When the liquid-phase refrigerant evaporates (boils), the liquid-phase refrigerant scatters above the liquid surface due to the evaporation pressure. At this time, in this embodiment, the fin 2
Since the outer surface area is increased by the provision of 32, there is a high possibility that the scattered liquid-phase refrigerant comes into contact with the portion of the heat exchanger 230 located above the liquid surface.

For this reason, in addition to the increase in the outer surface area below the liquid surface, the scattered liquid-phase refrigerant can also be evaporated. Can be prevented from decreasing. By the way,
In the present embodiment, the size was reduced by 35% as compared with the conventional technology.

As is clear from the above embodiment, if the fin height is increased while the pitch size of the fins 232 is reduced, the outer surface area of the tube 231 can be increased. However, in practice, as shown in FIG. 5A, the pitch dimension is set to 0.7 mm or more and 2 mm or less (0.9 mm in the present embodiment), which can exhibit 80% or more of the maximum capacity. 4.5mm fin height
As described above, it is desirable that the thickness be 8 mm or less (5 mm in the present embodiment).

The pitch dimension is, as is well known, the distance between adjacent peaks (valleys), and the fin height is
It refers to the height difference between a mountain and a valley.

Further, the higher the liquid level of the liquid-phase refrigerant, the greater the function as an evaporator, and the lower the liquid level, the greater the function as a condenser.
The highest liquid level of the liquid-phase refrigerant is determined by the heat exchanger 230 (core portion 23).
4) The vertical dimension h of FIG.
It has been concluded that it is desirable to set the height to not more than 2 and to set the fluctuation range of the liquid level to be within the vertical dimension h25% of the heat exchanger 230 (core part 234).

The heat exchanger 230 has a fin (23
Since the ridge direction D of 2) is disposed in the casing 410 so as to coincide with the vertical direction, when the heat exchanger 230 functions as an evaporator, the evaporated gas-phase refrigerant is smoothly transferred to the adsorption core 220. Can be distributed to.

The adsorbent 221 of the adsorption core 220
Since the smaller the average particle size, the larger the surface area of the adsorbent 221 as a whole, if the average particle size is reduced,
Although the adsorption capacity can be increased, the adsorbent 22
Since the gap between the two is small, the permeability of the gas-phase refrigerant (water vapor) is deteriorated (the ventilation resistance is increased), and on the contrary, the adsorption capacity may be reduced.

On the other hand, as shown in FIG. 7 (test results of the inventors), when the water vapor pressure is relatively low, around 10 Torr, the average particle diameter is around 0.25 mm and the water adsorption efficiency is the maximum. And the steam pressure is 30 Torr
When it is relatively high before and after, the average particle diameter is around 0.13 mm, and the moisture adsorption efficiency becomes maximum.

Therefore, when the steam pressure is relatively low, it is desirable that the average particle size capable of exhibiting 80% or more of the maximum capacity is 0.12 mm or more and 0.58 mm or less. Also, when the steam pressure is relatively high,
It is desirable that the average particle size capable of exhibiting 80% or more of the maximum capacity is 0.05 mm or more and 0.48 mm or less. However, according to the study by the inventors, the average particle size is 0.05%.
It has been confirmed that a practically sufficient capacity can be obtained when the thickness is not less than mm and not more than 0.6 mm.

Further, as the core width (the major diameter of the core tube 222) W of the suction core 220 is smaller, the airflow resistance is smaller and the suction efficiency (suction speed) is increased. As shown in (Result), when the water vapor pressure is relatively low, around 10 Torr, the core width W
Is about 5 mm, the adsorption efficiency is saturated, and the steam pressure is 30 T
When the core width W is relatively high at around orr, the core width W is 10 mm.
The adsorption efficiency saturates in the degree.

Accordingly, the core width W can exhibit 80% or more of the maximum capacity when the steam pressure is relatively low, and is 5 mm or more and 15 mm or less. When the steam pressure is relatively high, the core width W is 80% of the maximum capacity. It is preferable that the thickness is 10 mm or more and 25 mm or less, which can exhibit the above, and in the present embodiment, the core width W is 10 mm.

Also, if the fin pitch size of the suction core 220 is reduced, the heat transfer area of the suction core 220 is increased. Therefore, if the fin pitch size is reduced, the heat transfer capability can be improved. If the size is excessively reduced, the amount of the adsorbent 211 to be filled is reduced.
There is a possibility that the adsorption capacity is reduced.

On the other hand, as shown in FIG. 9 (results of tests and examinations by the inventors), it is desirable that the fin pitch size be about eight times the average particle size regardless of the steam pressure. When the water vapor pressure is relatively low at around 10 Torr, the fin pitch size is desirably 1 mm or more and 4.6 mm or less. When the water vapor pressure is relatively high at around 30 Torr, the fin pitch size is 0.4 m
It is desirable to set the fin pitch to 0.4 mm or more and 4 mm or less in practice. At this time, the fin height of the core fin 223 is desirably 5 mm or more and 10 mm or less.

The adsorbent 211 has a relative humidity of 10%.
As described above, in the state of 30% or less, it is necessary to ensure a difference of 15% or more in the moisture adsorption rate between when the adsorption of moisture is saturated and when the desorption of moisture is saturated.

(Second Embodiment) This embodiment focuses on the fact that the heat medium flowing in the core tube 222 flows from the upstream side to the downstream side while increasing its temperature. An adsorbent 221 (hereinafter referred to as an upstream adsorbent) located on the upstream side of the heat medium flow of the core tube 222 and an adsorbent 221 (hereinafter, referred to as an upstream adsorbent) located on the downstream side of the heat medium flow of the core tube 222. (The adsorbent is referred to as a downstream adsorbent.). Here, the moisture adsorption characteristic means a characteristic determined by a ratio of a change amount of the water adsorption amount to a change amount of the relative humidity.

More specifically, as shown in FIG. 10, the rising point P at which the water adsorption characteristic of the upstream adsorbent greatly changes is changed.
1 is the rising point P of the downstream adsorbent.
2 is higher than the relative humidity at 2. In other words, the upstream adsorbent has a high relative humidity,
It adsorbs more water than the downstream adsorbent, but adsorbs less water than the downstream adsorbent when the relative humidity is low.

Here, the state where the relative humidity is high means a portion where the heat medium having a low temperature on the upstream side flows, and the state where the relative humidity is low means that the heat medium having a high temperature on the downstream side flows. Means the part that does.

As a result, the conditioned air can be efficiently dehumidified and cooled, and the refrigeration capacity of the air conditioner can be increased.

(Other Embodiments) In the above embodiment, silica gel was used as an adsorbent. However, the present invention is not limited to this, and other adsorbents such as zeolite and activated alumina may be used. Good.

[Brief description of the drawings]

FIG. 1 is a schematic diagram illustrating a first state of an air conditioner according to a first embodiment of the present invention.

FIG. 2 is a schematic diagram of an adsorber according to the first embodiment of the present invention.

FIG. 3A is a schematic view of a suction core, and FIG. 3B is a partially enlarged view of FIG.

FIG. 4A is a schematic view of a heat exchanger, and FIG. 4B is a partially enlarged view of FIG.

FIG. 5 is a schematic diagram showing a second state of the air conditioner according to the first embodiment of the present invention.

FIG. 6A is a graph showing the relationship between the heat exchange capacity and the water level, and FIG. 6B is an explanatory diagram of the water level.

FIG. 7 is a graph showing the relationship between adsorption efficiency and average particle size.

FIG. 8 is a graph showing a relationship between an adsorption efficiency and a core width W.

FIG. 9 is a graph showing a relationship between a product of a filling amount of an adsorbent converted into a unit volume and an adsorption efficiency and a pitch dimension (a multiple of an average particle diameter).

FIG. 10 is a graph showing the relationship between the amount of adsorption and the relative humidity.

[Explanation of symbols]

200: adsorber, 210: casing, 220: adsorption core, 230: heat exchanger, 231, tube, 232: fin.

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hisao Nagashima 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Hideaki Sato 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Denso Corporation (72) Inventor Toshiaki Tanaka 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Shin Shin 1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside Denso Corporation (72) Inventor Person Katsuya Ishii 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside DENSO Corporation (72) Inventor Kazuhisa Yano 41-41, Oku-cho, Oku-machi, Nagakute-cho, Aichi-gun, Aichi Prefecture Inside Toyota Central Research Laboratory, Inc.

Claims (12)

[Claims] 1. A casing (210) enclosing a refrigerant.
An adsorption core (220) disposed on the upper side in the casing (210) and to which the adsorbent (221) is adhered; and an adsorption core (220) disposed on the lower side in the casing (210) and supplied from outside. A heat exchanger (230) for exchanging heat between the fluid and the refrigerant, wherein the heat exchanger (230) includes a tube (231) through which the fluid flows and an outer surface area of the tube (231). (234) consisting of fins (232) that increase
An adsorber for an adsorption refrigerating machine, comprising: 2. The outer surface area of the tube (231) is
The adsorber according to claim 1, wherein the inner surface area of the tube (231) is 5 times or more and 15 times or less. 3. The fin (232) is a corrugated fin having a plurality of peaks and valleys and formed in a wave shape, and a pitch dimension of the fin (232) is 0.7 mm or more and 2 mm. The fin height of the fin (232) is not less than 4.5 mm and not more than 8 mm.
4. The adsorber for an adsorption refrigerator according to claim 1. 4. The heat exchanger (230) is disposed in the casing (210) such that a ridge direction (D) connecting the ridges of the fins (232) coincides with a vertical direction. 4. The method according to claim 1, wherein
An adsorber for an adsorption refrigerator according to any one of the above. 5. The liquid phase refrigerant present in the casing (210) has a maximum liquid level of not less than ４ and not more than の of a vertical dimension (h) of the core part (234). The adsorber for an adsorption refrigerator according to any one of claims 1 to 4, wherein the adsorber is set. 6. A liquid surface refrigerant present in the casing (210) due to evaporation or condensation of the refrigerant has a liquid surface fluctuation width of 25 (h) of the vertical dimension (h) of the core part (234).
%. The adsorber for an adsorption type refrigerator according to any one of claims 1 to 5, wherein the adsorbent is set to be within%. 7. The flattened core tube (22) through which a fluid flows is provided with the suction core (220).
2) and a core fin (223) disposed between the core tube (222) and the adsorbent (221) bonded to at least one of the core tube (222) and the core fin (223). The adsorber for an adsorption type refrigerator according to any one of claims 1 to 6, wherein 8. The adsorber according to claim 7, wherein a length (W) of the core tube (222) in a major diameter direction is 5 mm or more and 25 mm or less. 9. The core fin (223) is a corrugated fin having a plurality of peaks and valleys and formed in a wavy shape, and a pitch dimension of the core fin (223) is 0.4 mm.
The fin height of the core fins (223) is 5 mm or more and 10 mm or less, and the fin height of the core fin (223) is 5 mm or more and 10 mm or less. 10. The average particle diameter of the adsorbent (221) is as follows:
The adsorber for an adsorption refrigerator according to any one of claims 1 to 9, wherein the adsorber has a length of 0.05 mm or more and 0.6 mm or less. 11. The adsorbent (221), an upstream adsorbent located upstream of a flow direction of a fluid flowing through the core tube (222), and the core tube (22).
2) The downstream adsorbent located downstream of the flow direction of the fluid flowing therethrough has different moisture adsorption characteristics determined by the ratio of the change amount of the water adsorption amount to the change amount of the relative humidity, Furthermore, the relative humidity at the rising point where the moisture adsorption characteristic of the upstream adsorbent greatly changes is higher than the relative humidity at the rising point of the downstream adsorbent. An adsorber for an adsorption refrigerator according to one of the above. 12. The adsorbent (221) has a water adsorption rate of 1% when the relative humidity is 10% or more and 30% or less.
The adsorber for an adsorption refrigerator according to any one of claims 1 to 11, wherein a difference of 5% or more can be secured.