JP2001215068A - Adsorption type refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To cool air which has been diffused indoors to a satisfactory level while raising coefficient of performance of an adsorption type refrigerator. SOLUTION: Total adsorption capacity of refrigerant of second and fourth adsorbers 110b, 110d is rendered to be not less than 0.2 times and not more than 0.8 times of the total adsorption capacity of refrigerant of first and third adsorbers 110a, 110c. Thus, coefficient of performance of an adsorption type refrigerator 100 is raised while maintaining a sufficient cooling capacity for utilization. In addition, the sizes of the second adsorber 110b and the fourth adsorber 110d can be made compact.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an adsorption refrigerator in which a vapor (gas phase) refrigerant in an adsorber is adsorbed by an adsorbent, thereby evaporating a liquid phase refrigerant in the adsorber to obtain a refrigerating capacity. It is effective when applied to an air conditioner.

[0002]

2. Description of the Related Art As an air conditioner using an adsorption refrigerator,
For example, in the invention described in Japanese Patent Application Laid-Open No. H8-240357, sufficient cooling capacity (refrigeration capacity) when the outside air temperature is high.
The adsorbent stored in the low-stage adsorber is cooled by the high-stage adsorber while the heat medium that cools the air blown into the room is cooled by the low-stage adsorber, are doing.

[0003]

However, in the invention described in the above publication, the coefficient of performance of the adsorption refrigerator is not necessarily high, as described in the "Embodiment of the invention".

[0004] In view of the above, it is an object of the present invention to secure a sufficient refrigerating capacity while increasing the coefficient of performance.

[0005]

According to the present invention, in order to achieve the above object, according to the first aspect of the present invention, a vapor refrigerant is adsorbed and the refrigerant adsorbed by being heated is desorbed. A plurality of adsorbers (110a to 110d) each containing an adsorbent (111) to be adsorbed, and a first adsorber (110) among the plurality of adsorbers (110a to 110d).
a, 110c), the heat medium cooled in the first adsorber (110a of the plurality of adsorbers (110a to 110d)).
a, 110c) and different second adsorbers (110b, 11c).
0d), re-cools the air, and circulates it through the indoor unit (120) that exchanges heat with indoor air.
0b, 110d) in the indoor unit (12).
0), wherein the total refrigerant adsorption capacity of the adsorbent (111) stored in the second adsorber (110b, 110d) is reduced by the first adsorption. Adsorbent (11) stored in the vessel (110a, 110c)
It is characterized in that it is smaller than the total refrigerant adsorption capacity of 1).

Accordingly, as described later, a sufficient refrigerating capacity can be secured while the coefficient of performance is increased, and the size of the second adsorbers (110b, 110d) can be reduced.

According to the second aspect of the present invention, the total adsorbing capacity of the adsorbent (111) contained in the second adsorber (110b, 110d) is determined by the first adsorber (11).
0a, 110c) is desirably 0.2 times or more and 0.8 times or less the total refrigerant adsorption capacity of the adsorbent (111) stored in the adsorbent (111).

According to the third aspect of the present invention, the adsorbent (111) contained in the first adsorber (110a, 110c) is a refrigerant per unit mass when the relative humidity is 0.08. It is desirable to adopt one that has a difference of 0.15 or more between the adsorption capacity and the refrigerant adsorption capacity per unit mass when the relative humidity is 0.3.

According to the fourth aspect of the present invention, the adsorbent (11) accommodated in the first adsorber (110a, 110c).
1) and the adsorbent (111) stored in the second adsorbers (110b, 110d) may have different refrigerant adsorption characteristics.

[0010] According to the fifth aspect of the present invention, the adsorbent (111) contained in the first adsorber (110a, 110c) has a relative humidity per unit mass of 0.08 per unit mass. The difference between the refrigerant adsorption capacity and the refrigerant adsorption capacity per unit mass when the relative humidity is 0.3 is 0.15 or more, and is accommodated in the second adsorber (110b, 110d). The adsorbent (111) has a relative humidity of 0.08
It is desirable to adopt a refrigerant having a difference of 0.3 or more between the refrigerant adsorbing capacity at the time of (1) and the refrigerant adsorbing capacity at a relative humidity of 0.5.

Further, in the present invention, the total adsorbing capacity of the adsorbent (111) contained in the second adsorber (110b, 110d) is equal to the first adsorber (110).
a, 110c) is 0.3 times or more and 0.5 times or less the total refrigerant adsorption capacity of the adsorbent (111) stored in the first and second adsorbers (110a, 110c, 110b, 11).
0d), the adsorbent (111) stored in the first adsorber (110a, 110c) has a refrigerant adsorbing capacity per unit mass at a relative humidity of 0.14 and a relative humidity of 0.17. , The difference from the refrigerant adsorption capacity per unit mass is 0.3 or more, and the first and second adsorbers (11
0a, 110c, 110b, 110d) contained in the first adsorber (110a, 110c).
It is desirable that the packing density of 11) be 500 (kg / m ³ ) or more.

Incidentally, the reference numerals in parentheses of the above-mentioned means are examples showing the correspondence with specific means described in the embodiments described later.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
FIG. 1 is a schematic view of an adsorption type refrigerator 100 in which an adsorption type refrigerator according to the present invention is applied to a vehicle air conditioner, and 110a to 110d contain (enclose) an adsorbent 111a and a refrigerant. And the first to fourth adsorbers whose insides are kept substantially in vacuum. In addition, the 1st-4th adsorbers 110a-
110d have the same structure, and when these are collectively referred to as adsorber 110.

The adsorbent 111 adsorbs the vapor refrigerant and desorbs and releases the adsorbed refrigerant when heated. In the present embodiment, the adsorbent 111 is used.
As disclosed in Japanese Patent Application Laid-Open No. 9-178292 (hereinafter referred to as FSM-C10), the refrigerant is water. In the present embodiment, the adsorbent 11
The waste heat (engine cooling water) of the running engine is used as a heat source for heating (regeneration) of No. 1.

FIG. 2 shows an adsorber 110. The adsorber 110 is made of stainless steel (in this embodiment, SUS in this embodiment) in which a refrigerant is sealed in a state where the inside is kept substantially in a vacuum.
304), a first heat exchanger (evaporation / condensation core) for exchanging heat between a heat medium (in this embodiment, an ethylene glycol-based antifreeze fluid in water) and a refrigerant in the casing 112. ) 113, and a second heat exchanger (adsorption core) 114 for cooling or heating the adsorbent 111.

In FIG. 1, reference numeral 120 denotes a heat medium cooled by the adsorber 110 and air blown into the vehicle interior (object to be cooled).
Is an indoor heat exchanger (hereinafter, abbreviated as an indoor unit) that cools the heat medium, and 130 is an outdoor heat exchanger (hereinafter, abbreviated as an outdoor unit) that exchanges heat between the heat medium and the outdoor air to cool the heat medium. It is.

Incidentally, 141 and 142 are pumps for circulating the heat medium, and 151 to 156 are switching valves for switching the flow of the heat medium.

Next, the general operation of this embodiment will be described.

1. First state (see FIG. 3) In the first state, the liquid-phase refrigerant in the first and second adsorbers 110a and 110b is evaporated and the first and second adsorbers 110a and 110b are evaporated.
b to exhibit the refrigerating capacity and adsorb the evaporated gas-phase refrigerant with the adsorbent 111, while the high temperature supplied from the engine to the second heat exchanger 114 of the third and fourth adsorbers 110c and 10d. Is circulated to desorb the adsorbed refrigerant.

Hereinafter, the step of adsorbing the vapor refrigerant is called an adsorption step, and the step of desorbing the adsorbed refrigerant is called a desorption step.

At this time, the first and second adsorbers 110a, 110
The heat medium circulating in the first heat exchanger 113b is cooled by the first and second adsorbers 110a and 110b, flows into the indoor unit 120, cools the air blown into the room, and then cools the second adsorber. 110b (the second heat exchanger 114 thereof),
The adsorbent 111 in the second adsorber 110b is cooled. In addition, the adsorbent 111 in the first adsorber 110a is
It is cooled by the heat medium cooled at 30.

2. Second state (see FIG. 4) In the second state, the liquid-phase refrigerant in the third and fourth adsorbers 110c and 110d is evaporated, and the third and fourth adsorbers 110c and 110d are evaporated.
d to exhibit the refrigerating capacity and adsorb the evaporated gas-phase refrigerant with the adsorbent 111, while the high temperature supplied from the engine to the second heat exchanger 114 of the first and second adsorbers 110a and 10b. Is circulated to desorb the adsorbed refrigerant.

At this time, the third and fourth adsorbers 110c, 11
The heat medium circulating in the first heat exchanger 113 of 0d is cooled by the third and fourth adsorbers 110c and 110d, flows into the indoor unit 120, cools the air blown into the room, and then cools the fourth adsorber. 110d (to the second heat exchanger 114),
The adsorbent 111 in the fourth adsorber 110d is cooled. Also, the adsorbent 111 in the third adsorber 110c is
It is cooled by the heat medium cooled at 30.

Then, the first state and the second state are switched at predetermined time intervals, and the cooled heat medium is continuously supplied to the indoor unit 1.
20. The predetermined time is determined based on the time required to desorb the adsorbed refrigerant or the time during which the adsorbent 111 can sufficiently adsorb the refrigerant, and the amount and type of the adsorbent 111 are determined. Is selected as appropriate.

The switching between the first state and the second state is performed by the first and second adsorbers 110a and 110b and the third and fourth adsorbers.
Adsorbers 110c, 110d each as a set of two
Since the process is switched between the adsorption process and the desorption process at predetermined time intervals, the coefficient of performance of the adsorption refrigerator 100 according to the present embodiment will be considered using the first and second adsorbers 110a and 110b as an example.

In the first state, the amount of heat Q (+) given to the heat medium circulating in the indoor unit 120 is the amount of heat (cooling capacity) Q absorbed by the air blown into the room by the indoor unit 120.
And the amount of heat Qc absorbed by the second adsorber 110b. Here, the amount of heat Q absorbed by the second adsorber 110b
c is Qa2 absorbed from the heat of adsorption (equivalent to the heat of condensation of the refrigerant) generated when the adsorbent 111 adsorbs the vapor refrigerant;
This is the sum with qa2 that has absorbed heat from the heat exchanger 114. Therefore, the amount of heat Q (+) given to the heat medium circulating in the indoor unit 120 is represented by the following Equation 1.

[0027]

Q (+) = Q + Qa2 + qa2 On the other hand, in the first state, the amount of heat Q (-) from which the heat medium circulating in the indoor unit 120 has been taken is determined by the first heat exchanger 113 of the first adsorber 110a. This is the sum of the heat quantity Qe1 absorbed and the heat quantity Qe2 absorbed by the first heat exchanger 113 of the second adsorber 110b. Therefore, in the first state,
Heat quantity Q by which heat medium circulating in indoor unit 120 has absorbed heat
(−) Is given by the following equation (2).

[0028]

Q (-) = Qe1 + Qe2 Further, the heat quantity Q (+) given to the heat medium circulating in the indoor unit 120 is equal to the heat quantity Q (-) absorbed by the heat medium circulating in the indoor unit 120. Equation 3 below holds.

[0029]

Q + Qa2 + qa2 = Qe1 + Qe2 Qa absorbed from the heat of adsorption (equivalent to the heat of condensation of the refrigerant) generated when the second adsorbent adsorbent 111 adsorbs the vapor refrigerant.
Reference numeral 2 denotes the latent heat of evaporation absorbed when the liquid-phase refrigerant evaporates, and the amount of heat is equal to the amount of heat Qe2 absorbed from the heat medium and the first amount.
It is equal to the sum of the amount of heat qe2 absorbed from the heat exchanger 113, and the following equation 4 is obtained.

[0030]

## EQU4 ## Qa2 = Qe2 + qe2 Further, the following Expression 5 is obtained from Expressions 3 and 4.

[0031]

Qe1 = Q + qe2 + qa2 Q = Qe1− (qe2 + qa2) As is apparent from Equation 5, the cooling capacity Q is determined by the amount of heat Qe1 absorbed by the refrigerant in the first adsorber 110a and the amount of heat in the second adsorber 110b. First and second heat exchangers 113, 11
4 is obtained by subtracting the amount of heat required for cooling the cooling water, and the refrigerating capacity generated in the second adsorber 110b is not directly related to the cooling capacity.

This is because the amount of heat absorbed from the heat medium in the first heat exchanger 113 of the second adsorber 110b is reduced by the second adsorber 1b.
This is because the heat medium is supplied to the heat medium by the second heat exchanger 114 of 10b. The heat amounts qe2 and qa2 are determined by the second adsorber 1
This is a heat loss generated when heat moves in the first and second heat exchangers 113 and 114 in 10b, and is an amount proportional to the heat capacity (heat mass) of the first and second heat exchangers 113 and 114. Refrigeration capacity Qe2 generated in second adsorber 110b
Is used to lower the temperature of the heat medium flowing into the indoor unit 120. As the refrigerating capacity Qe2 increases, the temperature of the heat medium flowing into the indoor unit 120 can be lowered.

By the way, the first and second adsorbers 110a, 110
The amount of heat Qs required to regenerate the adsorbent 111 in Ob is
First heat exchanger 11 of first and second adsorbers 110a and 110b
The heat quantity Qe1 and Qe2 absorbed from the heat medium in 3
(2) Heat loss qe generated in the heat exchangers 113 and 114
1, qe2, qa1, and qa2 are added, and specifically, the following Expression 6 is obtained.

[0034]

Qs = Qe1 + Qe2 + qe1 + qe2 + qa
1 + qa2 Further, when Expression 5 is substituted into Expression 6, Expression 7 below is obtained.

[0035]

Qs = Q + Qe2 + 2 (qe2 + qa2) ++
qe1 + qa1 Therefore, the coefficient of performance (COP) is, as is apparent from the following Expression 8, the first heat exchanger 1 of the second adsorber 110d.
13 is a function related to the amount of heat Qe2 absorbing heat from the heat medium.

[0036]

COP = Q / Qs = Q / {Q + Qe2 + 2 (qe2 + qa2) + qe1 + qa1} By the way, in the first state, the heat quantity Qe2 absorbed by the heat medium in the first heat exchanger 113 is equal to the first heat exchanger 113.
The temperature of the heat medium flowing out of the second adsorber 110b
As the temperature difference between the heat medium flowing into the first heat exchanger 113 and the temperature T1 increases, the temperature increases in proportion to the temperature difference. Therefore, the inventors have set the outside air temperature (the first adsorber 1).
10a) is 40 ° C., the indoor unit 12
Numerical simulation of the relationship between the temperature T1 and the coefficient of performance when the heat medium temperature at the heat medium inlet at 0 was cooled to 10 ° C. resulted in conclusions as shown in FIG. FIG.
Is a graph showing the refrigerant adsorption characteristics of FSM-C10 (the relationship between the ambient relative humidity of the adsorbent and the amount of refrigerant adsorption and adsorption).

Here, in FIG. 5, the temperature T1 = 10 ° C.
Means that the heating medium at 40 ° C.
° C (hereinafter, this is referred to as single-stage cooling). When the temperature T1 is higher than 10 ° C, the heat medium is removed by both the first adsorber 110a and the second adsorber 110b. This means cooling to 10 ° C., and in this numerical simulation, the first temperature is set at a temperature T1 = 25 ° C.
The amount of heat Qe1 that absorbs heat from the heat medium in the first heat exchanger 113 of the adsorber 110a is substantially equal to the amount of heat Qe2 that absorbs heat from the heat medium in the first heat exchanger 113 of the second adsorber 110b (hereinafter, referred to as the heat amount Qe2). This state is called two-stage cooling.)

As is apparent from FIG. 5, it can be seen that there is a peak point P where the coefficient of performance is highest between the single-stage cooling and the two-stage cooling.

Incidentally, as described above, the temperature T1 = 10
C means single-stage cooling, and temperature T1 = 25C means two-stage cooling. Therefore, the fact that the peak point P is in the middle means that 0 <Qe1 <Qe2 at this point.

The amounts of heat Qe1 and Qe2 increase in proportion to the amount of refrigerant evaporated in the first and second adsorbers 110a and 110b.
The amount of refrigerant that evaporates in b is an amount that increases in proportion to the total refrigerant adsorption capacity of the adsorbent 111.

Here, the total refrigerant adsorbing capacity of the adsorbent 111 is determined by the product of the amount of refrigerant that can be adsorbed by the adsorbent 111 per unit mass and the total amount of the adsorbent 111 stored in the adsorber. Is what is done.

Therefore, in the present embodiment, the second adsorber 11
The total refrigerant adsorption capacity of the second adsorber 110b is set to 0.6 times the total refrigerant adsorption capacity of the adsorbent 111 stored in the first adsorber 110a. Is made smaller than the total refrigerant adsorption capacity of the first adsorber 110a. The third adsorber 110c and the fourth adsorber 110d are the same as the first adsorber 110a and the second adsorber 11d.
0b, the total refrigerant adsorption capacity of the third adsorber 110c is equal to the total refrigerant adsorption capacity of the first adsorber 110a, and the total refrigerant adsorption capacity of the fourth adsorber 110d is equal to the total adsorbent capacity of the second adsorber 110b. Equal to refrigerant adsorption capacity.

As described above, according to this embodiment, the air blown into the room can be cooled to a sufficient temperature while the coefficient of performance of the adsorption refrigerator 100 is increased.
In addition, the second adsorber 110b and the fourth adsorber 110d can be reduced in size.

In this embodiment, the adsorbent 111 is used.
However, the present invention is not limited to this, and other adsorbents such as silica gel may be used.

At this time, when silica gel is used as the adsorbent, the total refrigerant adsorption capacity of the second adsorber 110b is 0.5 times or more the total refrigerant adsorption capacity of the first adsorber 110a.
0.8 times or less.
When FSM-C10 is adopted as 1, it is desirable that the total refrigerant adsorption capacity of the second adsorber 110b is 0.4 times or more and 0.6 times or less of the total refrigerant adsorption capacity of the first adsorber 110a. .

Regardless of the type of adsorbent, if the total refrigerant adsorption capacity of the second adsorber 110b is set to be 0.2 times or more and 0.8 times or less of the total refrigerant adsorption capacity of the first adsorber 110a,
While ensuring sufficient cooling capacity for practical use, the adsorption refrigerator 10
The coefficient of performance of 0 can be increased.

In the present embodiment, the adsorbent 111 contained in the first and third adsorbers 110a and 110c is a refrigerant adsorbing capacity per unit mass when the relative humidity is 0.08 (kg / kg). And a refrigerant having a refrigerant adsorption characteristic in which a difference between the refrigerant adsorption capacity per unit mass (kg / kg) at a relative humidity of 0.3 and 0.15 (kg / kg) or more is used. The second adsorber 110b and the fourth adsorber 110d can be downsized while reliably increasing the coefficient of performance.

In the present embodiment, the total refrigerant adsorption capacity of the second and fourth adsorbers 110b and 110d is set to 0.3 times or more of the total refrigerant adsorption capacity of the first and third adsorbers 110a and 110c. And the first and third adsorbers 110
a, adsorbent 111 stored in 110c, refrigerant adsorbing capacity per unit mass when relative humidity is 0.14 (kg / kg) and refrigerant per unit mass when relative humidity is 0.17 0.3 difference with adsorption capacity (kg / kg)
(Kg / kg) or more, and the packing density of the adsorbent 111 stored in the first and third adsorbers 110a and 110c is set to 500 (kg / m ³ ) or more. It is a target.

The packing density refers to the first and third adsorbers 11
This is a value obtained by dividing the mass of the adsorbent 111 stored in the first and third adsorbers 110a and 110c by the volume of the portion filled with the adsorbent 111 in the first and third adsorbers 110a and 110c.

(Second Embodiment) In the first embodiment, the first
Although the adsorbent 111 housed in the first to third adsorbers 110a to 110d has the same refrigerant adsorption characteristics, the present embodiment employs the first and third adsorbers 110a and 110c.
Adsorption characteristics of adsorbent 111 in the second and fourth and fourth adsorbers 11
0b, 110d, the second and fourth adsorbers 110b, 110d have different refrigerant adsorption characteristics.
d, the first and third adsorbers 110a, 110
c is smaller than the total refrigerant adsorption capacity.

Specifically, the first and third adsorbers 110a, 110a
As the adsorbent 111 housed in 10c, the difference between the refrigerant adsorption capacity per unit mass when the relative humidity is 0.08 and the refrigerant adsorption capacity per unit mass when the relative humidity is 0.3 is 0. The adsorbent contained in the second and fourth adsorbers 110b and 110d is adopted as the adsorbent contained in the second and fourth adsorbers 110b and 110d.
The difference between the total refrigerant adsorption capacity when the relative humidity is 0.08 and the total refrigerant adsorption capacity when the relative humidity is 0.5 is 0.3 or more.

(Other Embodiments) In the above embodiment, the adsorption refrigerator according to the present invention is applied to an air conditioner for a vehicle. However, the present invention is not limited to this. The present invention can be applied to other devices such as an air conditioner.

In the above embodiment, the adsorbent 111
The temperature of the heat medium (engine cooling water) for regenerating the adsorbent 111 was substantially constant, but the temperature of the heat medium for regenerating the adsorbent 111 (hereinafter, this temperature is referred to as the regeneration temperature) is adjusted according to the outside air temperature. You may. In this case, when the outside air temperature is 40 ° C. or lower, it is desirable that the regeneration temperature be approximately 90 ° C., and when the outside air temperature exceeds 40 ° C., it is desirable that the regeneration temperature be approximately 100 ° C.

[Brief description of the drawings]

FIG. 1 is a schematic view of an adsorption refrigerator according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram of an adsorber used in the adsorption refrigerator according to the first embodiment of the present invention.

FIG. 3 is a schematic diagram showing a first state in the adsorption refrigerator according to the first embodiment of the present invention.

FIG. 4 is a schematic diagram showing a second state in the adsorption refrigerator according to the first embodiment of the present invention.

FIG. 5 is a graph showing a relationship between a coefficient of performance and a temperature T1 in the adsorption refrigerator according to the first embodiment of the present invention.

FIG. 6 is a graph showing refrigerant adsorption characteristics of FSM-C10.

[Explanation of symbols]

110a: first adsorber, 110b: second adsorber, 110
c: third adsorber, 110d: fourth adsorber, 111: adsorbent.

 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Hisao Nagashima 1-1-1, Showa-cho, Kariya-shi, Aichi Pref. Inside Denso Corporation (72) Inventor: Akiaki Tanaka 1-1-1, Showa-cho, Kariya-shi, Aichi Co., Ltd. Inside DENSO (72) Inventor Tetsu Inoue 1-1-1 Showa-cho, Kariya-shi, Aichi F-term in DENSO Corporation (Reference) 3L093 NN03 PP03 PP07 PP15

Claims (6)

[Claims] An adsorbent (11) that adsorbs a vapor refrigerant and desorbs the adsorbed refrigerant by being heated.
1) a plurality of adsorbers (110a to 110)
d), and the first of the plurality of adsorbers (110a to 110d)
The heat medium cooled by the adsorbers (110a, 110c) is supplied to a second one of the plurality of adsorbers (110a to 110d) which is different from the first adsorber (110a, 110c).
The adsorbent (111) in the second adsorber (110b, 110d) is re-cooled by the adsorber (110b, 110d) and passed through the indoor unit (120) that exchanges heat with indoor air. A cooling medium cooled by a heat medium flowing out of the indoor unit (120), wherein the total refrigerant adsorption of the adsorbent (111) housed in the second adsorbers (110b, 110d). Ability to the first
An adsorbent refrigerating machine characterized in that the total adsorbing capacity of the adsorbent (111) contained in the adsorbers (110a, 110c) is smaller than that of the adsorbent (111). 2. The second adsorber (110b, 110)
d) is the total refrigerant adsorption capacity of the adsorbent (111) stored in the first adsorber (110a, 110c), which is 0.1% of the total refrigerant adsorption capacity of the adsorbent (111) stored in the first adsorber (110a, 110c). An adsorption type refrigerator characterized by being at least 2 times and not more than 0.8 times. 3. The first adsorber (110a, 110)
The adsorbent (111) stored in c) has a refrigerant adsorption capacity per unit mass when the relative humidity is 0.08,
The adsorption refrigerator according to claim 1 or 2, wherein a difference from a refrigerant adsorption capacity per unit mass when the relative humidity is 0.3 is 0.15 or more. 4. The first adsorber (110a, 110a)
c) said adsorbent (111) contained in said second
The adsorptive refrigerator according to claim 1 or 2, wherein the adsorbent (111) stored in the adsorber (110b, 110d) has a different refrigerant adsorption characteristic. 5. The first adsorber (110a, 110)
The adsorbent (111) stored in c) has a refrigerant adsorption capacity per unit mass when the relative humidity is 0.08,
The difference from the refrigerant adsorbing capacity per unit mass when the relative humidity is 0.3 is 0.15 or more, and the adsorbent (110b, 110d) contained in the second adsorber (110b, 110d) 111) wherein the difference between the refrigerant adsorption capacity when the relative humidity is 0.08 and the refrigerant adsorption capacity when the relative humidity is 0.5 is 0.3 or more. 5. The adsorption refrigerator according to 4. 6. The second adsorber (110b, 110b).
The total refrigerant adsorption capacity of the adsorbent (111) stored in the first adsorber (110a, 110c) is 0.1% of the total refrigerant adsorption capacity of the adsorbent (111) stored in the first adsorber (110a, 110c). The first and second adsorbers (110a, 110c, 110)
b, 110d) among the first adsorbers (110a, 1
The adsorbent (111) contained in 10c) has a refrigerant adsorption capacity per unit mass when the relative humidity is 0.14, and a refrigerant adsorption capacity per unit mass when the relative humidity is 0.17. The difference between the first and second adsorbers (110a, 110c,
110b, 110d) of the first adsorber (110
a, adsorption type refrigerating machine according to claim 1 or 2, wherein the housing has been the adsorbent within 110c) the packing density of (111) is 500 (kg / m ³⁾ or more.