JPH1137597A - Adsorption-type freezer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve the miniaturization of an adsorption-type freezer that can continuously refrigerate an object to be refrigerated. SOLUTION: In an adsorption-type freezer, a heat exchange fluid is refrigerated due to chill being generated by evaporating a refrigerant in an evaporation condenser 13 when the refrigerant is absorbed by an adsorption core 12, the refrigerated heat exchange fluid is circulated in an indoor heat exchanger 27 and a cold storage device 28 through a fluid circulation path C, indoor air is cooled, at the same time, the cold heat is stored in the cold storage device 28, the heat exchange fluid is refrigerated by the chill being stored by the cold storage device 28 when the adsorption core 12 desorbs the refrigerant, the refrigerated heat exchange fluid is circulated in the indoor heat exchanger 27 through a fluid circulation path D, and the indoor air is cooled, thus eliminating the need for desorbing another adsorption core and preventing the number of the adsorption cores 12 to be required from being increased when the adsorption core 12 is adsorbed.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an adsorption refrigeration apparatus utilizing adsorption and desorption of a refrigerant such as water by an adsorbent.

[0002]

2. Description of the Related Art A conventional adsorption refrigerating apparatus has two adsorption cores each having a large number of adsorbents arranged around a heat exchanger through which a cooling fluid and a heating fluid alternately flow. Then, a first step in which one adsorption core adsorbs the refrigerant and the other adsorption core desorbs the refrigerant, and one adsorption core desorbs the refrigerant,
By alternately performing the second step in which the other adsorption core adsorbs the refrigerant at predetermined time intervals, the adsorption of the refrigerant (in other words, the evaporation of the refrigerant) is continuously performed. Body) is cooling continuously.

[0003]

However, in the prior art, in order to continuously cool the indoor air, the adsorption and desorption of the refrigerant are performed in parallel as in the first and second steps. Therefore, there is a problem that at least two adsorption cores are required, and the size of the adsorption refrigeration apparatus becomes large.

The present invention has been made in view of the above problems, and has as its object to reduce the size of an adsorption refrigeration apparatus capable of continuously cooling an object to be cooled.

[0005]

According to the prior art, the present inventors require at least two adsorption cores in order to perform adsorption and desorption of a refrigerant in parallel, which results in an increase in the size of the apparatus. Focusing on that, by performing the adsorption and desorption of the refrigerant alone, it is found that the object to be cooled is continuously cooled, the number of necessary adsorption cores is reduced, and the above object is achieved. Was.

In other words, according to the first, second, fourth and fifth aspects of the present invention, when the refrigerant is adsorbed by the adsorption core (12), the refrigerant is cooled by the evaporator (13). In addition to cooling the cooled object, the cold heat is stored in the regenerator (28), and when the refrigerant is desorbed by the adsorption core (12) to desorb the refrigerant, the cold stored by the regenerator (28) at the time of adsorbing the refrigerant is used. It is characterized in that the object to be cooled is cooled.

[0007] Therefore, since the cooled portion can be cooled at the time of desorbing the refrigerant by using the cold stored in the regenerator (28) at the time of adsorbing the refrigerant, another adsorption core is detached at the time of adsorbing the refrigerant. No need. As a result, the number of necessary adsorption cores (12) can be reduced as compared with the conventional art, so that the adsorption refrigeration apparatus can be reduced in size and cost can be reduced.

The amount of cold required for performing the adsorption and desorption of the refrigerant once (ie, the total amount of cold required for exhibiting the predetermined cooling capacity) is reduced during the operation for performing the adsorption of the refrigerant once. The physique (specifically, the filling amount of the adsorbent (S), etc.) of the adsorption core (12) is set so that it can be generated by the evaporator (13). According to the second aspect of the present invention, the first fluid circulation for circulating the heat exchange fluid between the evaporator (13), the regenerator (28), and the cooler (27) for cooling the object to be cooled. A second fluid circulation path (D) for circulating a heat exchange fluid between the path (C), the regenerator (28), and the cooler (27); The heat exchange fluid is circulated in (C), and the heat exchange fluid is circulated in the second fluid circulation path (D) when the refrigerant is desorbed.

In this manner, the present invention can be satisfactorily implemented. According to the third, fourth and fifth aspects of the present invention, the evaporator (13) and the cooler (2) for cooling the object to be cooled are provided.
70), and a main fluid circulation path (C) for circulating the heat exchange fluid between the main fluid circulation path (C) and the heat exchange fluid in the cooler (270) bypassing the evaporator (13) in the main fluid circulation path (C). And a bypass fluid circulation path (D) for circulating the heat exchange fluid. At the time of refrigerant adsorption, the heat exchange fluid is cooled by cold heat when the refrigerant evaporates in the evaporator (13). The object to be cooled is cooled by circulating through the body circulation path (C) to the cooler (270), and the cooled heat exchange fluid is supplied to the bypass fluid circulation path (D) when the refrigerant is desorbed.
Then, the object to be cooled is cooled by circulating through a cooler (270).

Therefore, the heat exchange fluid cooled at the time of adsorption of the refrigerant is circulated to the cooler (270) via the bypass fluid circulation path (D) at the time of desorption of the refrigerant, whereby the portion to be cooled can be cooled. Therefore, it is not necessary to detach another adsorption core when adsorbing the refrigerant. As a result, the number of necessary adsorption cores (12) can be reduced as compared with the conventional art, so that the adsorption refrigeration apparatus can be reduced in size and cost can be reduced.

According to the present invention, a main cooling water circuit (E) for circulating engine cooling water between the engine (22) and the adsorption core (12), and a main cooling water circuit (E) are provided. E), a bypass cooling water circulation path (E0) for bypassing the adsorption core (12) is provided, and the engine cooling water is circulated to the adsorption core (12) through the main cooling water circulation path (E) when the refrigerant is desorbed. , Adsorption core (1
2) is heated and the engine cooling water is circulated through the bypass cooling water circulation path (E0) when the refrigerant is adsorbed, thereby storing the heat of the engine (22) in the engine cooling water circulating through the bypass cooling water circulation path (E0). It is characterized by:

[0012] Thus, the engine cooling water storing the heat of the engine (22) during the adsorption of the refrigerant can be circulated to the adsorption core (12) during the desorption of the refrigerant, so that the heat of the engine (22) is absorbed during the adsorption of the refrigerant. The heat of the engine (22) can be used more effectively for heating the adsorption core (12) than in the case where the heat is released outside the room. According to the fifth aspect of the present invention, the heating temperature of the adsorption core (12) and the condenser (13)
The difference between the cooling temperature of the adsorption core (12) and the difference between the cooling temperature of the adsorption core (12) and the evaporation temperature of the evaporator (13) is set so that the adsorption core (12) is heated to desorb the refrigerant. (T2) is characterized in that it is shorter than the time (T1) for cooling the adsorption core (12) and adsorbing the refrigerant.

[0013] Here, the heating temperature of the adsorption core (12),
The difference between the condensation temperature in the condenser (13) and the adsorption core (1)
When the cooling temperature in 2) is larger than the evaporation temperature in the evaporator (13), the speed at which the adsorption core (12) desorbs the refrigerant is higher than the speed at which the adsorption core (12) adsorbs the refrigerant. Will also be faster. For this reason, as described above, the suction core (12)
Even if the time (T2) for heating and desorbing the refrigerant is shorter than the time (T1) for cooling the adsorption core (12) and adsorbing the refrigerant, the adsorption core (12) is completely desorbed (regeneration state). ).

[0014] The time required to perform the adsorption and desorption of the refrigerant once each becomes shorter by the amount of time required to desorb the refrigerant to and from the adsorption core (12).
Since less heat is required during each cycle,
The size of the suction core (12) can be reduced.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. (First Embodiment) FIG. 1 is an overall configuration diagram of an adsorption-type refrigeration apparatus 1 showing a first embodiment of the present invention. In the present embodiment, the cooling capacity of the adsorption-type refrigeration apparatus 1 is used for cooling the vehicle interior air (the object to be cooled) (that is, for cooling the vehicle interior).

The adsorption refrigeration system 1 includes an adsorption core 12, an evaporative condenser (evaporator and condenser) 13 inside a closed vessel (sealed circuit) 11 forming one closed space. 10 in which are stored in order from the top
It has. The closed container 11 includes an adsorption core accommodating section 111 accommodating the adsorption core 12, an evaporating condenser accommodating section 112 accommodating the evaporating condenser 13, and
1 and 112, and a refrigerant vapor passage 110 located between the two.

A predetermined amount of liquid refrigerant L is sealed inside the evaporative condenser accommodating section 112 of the closed vessel 11. The entire or a part of the main evaporative condenser 13 is provided in contact with the liquid refrigerant L, and the entire adsorption core 12 is not in contact with the liquid refrigerant L (that is, above the surface of the liquid refrigerant L). Is provided. In the present embodiment, the evaporative condenser 13
About half in the height direction is in contact with the liquid refrigerant L. As the refrigerant, for example, water, alcohol, chlorofluorocarbon or the like is used.

The adsorbing core 12 has a large number of adsorbents S held in a heat exchanger 121 having a well-known heat exchanger shape. The heat exchanger 121 includes a pair of tanks 121a,
A plurality of fluid pipes 121c and a plurality of meandering heat transfer fins 121d are alternately arranged in parallel between 121b. One of the pair of tanks 121a and 121b 121a
An inlet 12a through which the heat exchange fluid flows is formed, and an outlet 12b through which the heat exchange fluid flows out is formed at the other end 121b. As the heat exchange fluid, so-called water obtained by mixing ethylene glycol or the like into water is used. Uses antifreeze.

The adsorbent S adsorbs the refrigerant vapor when cooled and desorbs the adsorbed refrigerant vapor when heated, and is made of, for example, silica gel, zeolite, activated carbon, activated alumina and the like. . And among the heat exchangers 121, the tanks 121a and 121b
And a plurality of fluid pipes 121c, a plurality of heat transfer fins 12
A large number of adsorbents S are filled during 1d and fixed by adhesion. Note that the suction cores 12 are arranged in parallel in the vertical direction. Thereby, the refrigerant vapor from the refrigerant vapor passage 110 is favorably supplied to the adsorbent S from both surfaces of the adsorption core 12.

The evaporative condenser 13 is provided with the above-described adsorption core 12.
Has the same heat exchanger shape as the heat exchanger 121 of
It has an inlet 13a through which the heat exchange fluid flows in and an outlet 13b through which the heat exchange fluid flows out. And the heat exchanger 121 of the adsorption core 12 and the outdoor heat exchanger 24
They are connected in series by a fluid pipe, thereby forming a fluid circulation path A for circulating a heat exchange fluid between the heat exchanger 121 of the adsorption core 12 and the outdoor heat exchanger 24. Further, the heat exchanger 121 of the adsorption core 12 and the engine 22 are connected in series by a fluid pipe, whereby the heat exchanger 121 of the adsorption core 12 and the engine 22 are connected.
And a fluid circulation path (main cooling water circulation path) E for circulating the heat exchange fluid.

Further, the evaporative condenser 13 and the outdoor heat exchanger 2
4 is connected in series by a fluid pipe, thereby constituting a fluid circulation path B for circulating a heat exchange fluid between the evaporative condenser 13 and the outdoor heat exchanger 24. Further, the evaporative condenser 13 and the indoor heat exchanger (cooler) 27
And the regenerator 28 are connected in series in this order by a fluid pipe, whereby the heat exchange fluid is circulated between the evaporative condenser 13, the indoor heat exchanger 27, and the regenerator 28. A fluid circulation path (first fluid circulation path, main fluid circulation path) C is configured. Further, the evaporative condenser 13 is provided in the fluid circulation path C.
And a fluid circulation path (second fluid circulation path, bypass fluid circulation path) D for circulating the heat exchange fluid between the indoor heat exchanger 27 and the regenerator 28 by bypassing the heat exchange fluid.

A three-way switch is provided near the inlet 12a of the heat exchanger 121 of the adsorption core 12 (on the way of the fluid circulation paths A and E) and near the outlet 12b (on the way of the fluid circulation paths A and E). The valves 21 and 23 are provided, and the engine cooling water (heating fluid) from the engine 22 is circulated to the heat exchanger 121 of the adsorption core 12 by the three-way switching valves 21 and 23 (that is, the fluid circulation path E Or the heat exchanger fluid (cooling fluid) from the outdoor heat exchanger 24 is circulated to the heat exchanger 121 of the adsorption core 12 (that is, the heat exchanger is circulated to the fluid circulation path A). Or switch).

A three-way switching valve 25 is provided near the inlet 13a of the evaporative condenser 13 (midway of the fluid circulation paths B and C) and near the outlet 13b (midway of the fluid circulation paths B and C).
The three-way switching valves 25 and 26 allow the heat exchange fluid from the outdoor heat exchanger 24 to flow through the evaporative condenser 1.
3 (that is, whether the heat exchanger is circulated through the fluid circulation path B), or the heat exchange fluid from the indoor heat exchanger 27 is circulated through the evaporative condenser 13 (that is, the fluid circulation path C).
Circulating the heat exchanger).

Further, the regenerator 28 described above is
Inside the heat exchanger 28 is a heat exchanger 28 of a well-known heat exchanger shape.
1 and a cold storage agent 282. Heat storage material 282
A material having a melting point about the target temperature (for example, 10 ° C.) of the heat exchange fluid flowing into the indoor heat exchanger 27 is used. For example, polyethylene glycol having a molecular weight of 400 to 600 is used.

The inlet 27a of the indoor heat exchanger 27
Near (in the middle of the fluid circulation paths C and D) and the regenerator 28
In the vicinity of the outlet 28b (in the middle of the fluid circulation paths C and D)
The three-way switching valves 29 and 30 are provided, and the evaporating condenser 13 and the indoor heat exchanger 2 are provided by the three-way switching valves 29 and 30.
7 and the regenerator 28 in this order (that is, whether to circulate the heat exchange fluid in the fluid circulation path C) or to circulate the heat exchange fluid between the indoor heat exchanger 27 and the regenerator 28. (That is, whether to circulate the heat exchange fluid through the fluid circulation path D).

The heat exchange fluid is pressure-fed by an electric pump 25 provided in the vicinity of the outdoor heat exchanger 24 (the portion where the fluid circulation paths A and B join), and the fluid circulation path A or the fluid circulation path B The heat exchange fluid is circulated through In addition, the vicinity of the indoor heat exchanger 27 (the portion where the fluid circulation paths C and D join).
The heat exchange fluid is pumped by the electric pump 32 provided in
The heat exchange fluid is circulated through the fluid circulation path C or the fluid circulation path D. Further, engine cooling water (heat exchange fluid) is circulated in the fluid circulation path E by a mechanical pump 33 driven by the engine 22.

Note that the indoor heat exchanger 27 is
The room air is cooled by exchanging heat between the room air (cooled body) blown by the blower fan 4 and the refrigerant. Next, the operation of the above configuration will be described. First, when the user turns on an air conditioner switch (not shown), the electric pumps 25, 32 are operated, and the three-way switching valves 21, 23, 25, 26, 2,
The adsorption mode in which the refrigerant vapor is adsorbed on the adsorbent S of the adsorption core 12 is executed by rotating 9, 9 to the solid line position in FIG.

That is, the heat exchange fluid circulates through the fluid circulation paths A and C, the adsorbent S adsorbs the refrigerant vapor, and the liquid refrigerant L evaporates. Then, the evaporative condenser 1 is heated by the evaporative latent heat generated when the liquid refrigerant evaporates.
3 is cooled to, for example, about 0 ° C. to 5 ° C., and the cooled heat exchange fluid is supplied to the indoor heat exchanger 27 via the fluid circulation path C, thereby indoors (the part to be cooled). , And the relatively low-temperature heat exchange fluid that has passed through the indoor heat exchanger 27 is supplied to the regenerator 28. Thereby, cold heat is stored in the cool storage device 28.

The temperature of the heat exchange fluid passing through the indoor heat exchanger 27 fluctuates depending on the indoor temperature. When the temperature of the heat exchange fluid is lower than the melting point of the heat storage agent 282, Is well stored as the latent heat of fusion of the heat storage agent 282. Here, in the present embodiment, the desorption mode time T2 (for example, 50 seconds) for desorbing the refrigerant to and from the adsorption core 12
To the adsorption mode time T for adsorbing the refrigerant on the adsorption core 12.
1 (for example, 70 seconds). this is,
The heating temperature of the adsorption core 12 (that is, the temperature of the heat exchange fluid from the engine 22, for example, 90 ° C.)
The difference (for example, about 60 ° C.) from the condensation temperature of the refrigerant (for example, about 30 ° C.) depends on the cooling temperature of the adsorption core 12 (that is,
The temperature of the heat exchange fluid from the outdoor heat exchanger 24, for example, 40
° C) and the evaporation temperature of the refrigerant in the evaporative condenser 13 (for example, 1
0 ° C.) (eg, about 30 ° C.)
The time when the adsorption core 12 completes desorption (that is, the adsorbent S
This is because the time required for desorbing a predetermined amount of refrigerant from the adsorption core 12) is shorter than the time required for the adsorption core 12 to complete adsorption (that is, the time required for causing the adsorbent S to adsorb a predetermined amount of refrigerant). is there.

Accordingly, the cooling capacity required in the adsorption mode is, for example, 3 kW, and the cooling capacity required in the desorption mode, which will be described later, is, for example, 2 kW. 5 kW. For this reason, in the adsorption mode, a cooling capacity of 5 kW is generated by the adsorption core 12 and the evaporative condenser 13, and 3 kW of the generated cooling capacity is used for indoor cooling and 2 kW is stored in the regenerator 28. ing.

The heat exchange fluid circulating in the heat exchanger 121 of the adsorption core 12 is heated by the heat of adsorption, and the heated heat exchange fluid is passed through the fluid circulation path A to the outdoor heat exchanger 2.
By circulating the heat to the outside, heat is radiated from the heat exchange fluid to the outside of the room. After performing such an adsorption mode for the time T1, the three-way switching valves 21, 23, 25, 26, 2
The desorption mode for desorbing the refrigerant vapor from the adsorbent S is executed by switching the positions 9 and 30 to the positions indicated by the alternate long and short dash lines in FIG. In addition, at the time of switching this mode, the adsorption capacity of the adsorbent S is reduced.

In the desorption mode, the heat exchange fluid circulates through the fluid circuit B, the fluid circulation path D, and the fluid circulation path E. As a result, the engine coolant (heat exchange fluid) of the engine 22 is circulated through the heat exchanger 121 of the adsorption core 12, so that the adsorbent S is heated and the refrigerant on which the adsorbent S is adsorbed is desorbed. . The desorbed refrigerant vapor is condensed near the evaporative condenser 13. The heat of condensation at this time heats the heat exchange fluid flowing through the evaporative condenser 13,
The heated heat exchange fluid is circulated to the indoor heat exchanger 24 via the second fluid circulation path B, so that heat is released from the heat exchange fluid to the outside.

Further, since the cold heat is released into the room in the indoor heat exchanger 27, the temperature of the heat exchange fluid flowing through the indoor heat exchanger 27 rises and becomes higher than the melting point of the cold storage material 282. As a result, the cold storage material 282 emits cold heat corresponding to the latent heat of fusion to the heat exchange fluid (in other words, absorbs the latent heat of fusion from the heat exchange fluid), so that the heat exchange fluid is cooled and the cooled heat is cooled. By circulating the exchange fluid through the indoor heat exchanger 27, the room can be cooled in the desorption mode. Then, such a desorption mode is set to the time T2.
After that, the adsorption capacity of the adsorbent S is regenerated, so that the adsorption mode is executed again.

According to the present embodiment, the suction core 1
2 uses the cold stored in the regenerator 28 in the adsorption mode in which the refrigerant is adsorbed (when the refrigerant is adsorbed), and cools the vehicle interior air in the desorption mode in which the adsorption core 12 desorbs the refrigerant (when the refrigerant is desorbed). (Cooling of the passenger compartment). Therefore, the air in the passenger compartment can be continuously cooled by one suction core 12, so that it is not necessary to detach and attach another suction core from the suction core 12 in the suction mode. Therefore, the number of adsorption cores required for continuous cooling can be reduced as compared with the conventional case, so that the adsorption refrigeration apparatus 1 can be reduced in size and cost can be reduced.

In particular, since the number of required adsorbing cores is smaller than before, the structure of a fluid circulation path for circulating a heat exchange fluid (cooling fluid or heating fluid) through the adsorbing cores becomes simpler. The size of the refrigerating apparatus 1 can be reduced, and the cost can be reduced. In the present embodiment,
Since the desorption mode time T2 is set shorter than the adsorption mode time T1, the cooling capacity to be generated by the adsorption refrigeration apparatus 1 can be reduced. This effect will be described in detail below in comparison with a conventional adsorption refrigeration apparatus.

First, a conventional adsorption refrigerating apparatus is provided with two units A and B having the same structure as the unit 10, and the two units A and B are provided with the above adsorption mode and desorption mode. The first predetermined time T1
It is assumed that it is performed alternately every time. Then, assuming that the cooling capacity per unit time to be generated by the adsorption refrigeration apparatus is Q, in the conventional adsorption refrigeration apparatus, unit A
While the refrigerant is adsorbed and desorbed once (in other words, while the desorption and adsorption of the refrigerant is performed once in the unit B), the cooling capacity corresponding to 2T1 × Q is reduced by the evaporative condenser 1.
3 must be generated. On the other hand, in the adsorption refrigeration apparatus of the present embodiment, the adsorption and desorption of the refrigerant by the unit 10 is performed by 1 unit.
It is necessary to generate a cooling capacity equivalent to (T1 + T2) × Q during each cycle.

Here, since the desorption mode time T2 <the adsorption mode time T1, (T1 + T2) × Q <2T1 × Q
Thus, in the present embodiment, the cooling capacity to be generated during the one-time adsorption and desorption of the refrigerant is smaller than in the conventional technology. On the other hand, the larger the filling amount of the adsorbent S, the larger the amount of adsorbed refrigerant, and the larger the cooling capacity that can be generated by the evaporative condenser 13. Therefore, in the present embodiment, the amount of the adsorbent S to be filled is smaller than in the conventional technique, so that the size of the adsorption core 12 can be reduced, and the adsorption refrigeration apparatus 1 can be reduced in size.

(Second Embodiment) As shown in FIG. 2, the adsorption refrigeration apparatus of this embodiment includes a plurality (for example, three) of units 10. Then, the plurality of suction cores 12
Are arranged in series in the fluid circulation paths A and E, and the plurality of evaporative condensers 13 are arranged in series in the fluid circulation paths B, C and D. Then, the flow direction of the heat exchange fluid flowing through the plurality of adsorption cores 12 and the flow direction of the heat exchange fluid flowing through the plurality of evaporative condensers 13 are countercurrent (that is, opposite to each other). The heat exchange fluid is circulated. Thereby, the cooling capacity of the adsorption refrigeration apparatus 1 can be improved.

In such an adsorption-type refrigeration system 1, the heat storage device 28 is provided as in the first embodiment, and the same operation as in the first embodiment is performed.
Here, conventionally, a plurality of units are provided in one pair (two sets), and when one of the plurality of units performs the adsorption of the refrigerant,
The cooling was continuously performed by allowing the other plurality of units to desorb and cool the refrigerant. In the present embodiment, however, a process of performing adsorption by one of the plurality of units and then performing desorption is performed. By repeating, cooling can be performed continuously.

(Third Embodiment) In this embodiment, FIG.
As shown in (1), the cooling capacity obtained by the adsorption refrigeration apparatus 1 is used for cooling the refrigerant (cooling target) flowing through the supercooling section 43 of the vapor compression refrigeration apparatus 2. The vapor compression refrigeration apparatus 2 includes a refrigerant compressor 41 that sucks and compresses a gas refrigerant, an outdoor heat exchanger 42 that exchanges heat between the outside air blown by a blower fan 42a and the refrigerant, a supercooling unit 43, and an expansion unit. Valve 44
And an indoor heat exchanger 45 for exchanging heat between the inside air blown by the blower fan 45a and the refrigerant, and an accumulator 46 for separating the refrigerant into gas and liquid and leading out a gas refrigerant.

When the four-way switching valve 47 is switched to the solid line position in FIG. 3, the refrigerant from the compressor 1 is condensed in the outdoor heat exchanger 42 and the condensed refrigerant is The supercooled refrigerant is decompressed by the expansion valve 44, the depressurized refrigerant is evaporated by the indoor heat exchanger 45, and the evaporated refrigerant is gas-liquid separated by the accumulator 46. Only the gas refrigerant is sucked into the compressor 1 again. Thereby, cooling of the vehicle interior is performed.

When the four-way switching valve 47 is switched to the position indicated by the dotted line in FIG. 3, the refrigerant from the compressor 1 is condensed in the indoor heat exchanger 45, and the condensed refrigerant is supplied to the expansion valve 44. The decompressed refrigerant is supplied to the subcooling unit 43
(That is, the supercooling section 43 does not operate), evaporates in the outdoor heat exchanger 42, the evaporated refrigerant is gas-liquid separated in the accumulator 46, and only the gas refrigerant is sucked into the compressor 1 again. Let me. Thereby, heating of the vehicle interior is performed.

In the vapor compression refrigeration system 2, all the devices (41, 42, 44, 4) except the indoor heat exchanger 43 are used.
5, 46) are installed outside the vehicle compartment (the room where the traveling motor is mounted). Then, the above-described fluid circulation path E
, A cooling water tank 51 composed of a heat insulating container is connected downstream of the engine 22, and further, the fluid circulation path E bypasses the outdoor heat exchanger 24 and
2 and a cooling water tank 51, a fluid circulation path (bypass cooling water circulation furnace) E0 for circulating a heat exchange fluid is provided. The cooling water tank 51 is provided to increase the amount of the engine cooling water filled in the fluid circulation path E0, thereby increasing the heat capacity of the engine cooling water in the fluid circulation path E0 and increasing the temperature of the engine cooling water. It is mitigating change.

The engine 22 is controlled by a three-way switching valve 52 provided at the branch between the fluid circulation path E and the fluid circulation path E0.
Is circulated through the heat exchanger 121 of the adsorption core 12 (that is, the fluid circulation path E
Circulates the heat exchange fluid) or bypasses the heat exchanger 121 of the adsorption core 12 (that is, the fluid circulation path E0).
Or circulate the heat exchange fluid).

A subcooling unit cooler (cooler) 270 is connected to the fluid circulation path D instead of the indoor heat exchanger 27 (see FIG. 1). This supercooler cooler 270
Is configured such that the heat exchange fluid comes into contact with the refrigerant passage of the subcooling unit 43. Further, instead of the regenerator 28 described above, the heat exchange fluid tank 2 made of a heat insulating container is used.
8a is connected to the downstream side of the indoor heat exchanger 27 in the fluid circulation path D. The heat exchange fluid tank 28a is provided to increase the amount of heat exchange fluid enclosed in the fluid circulation paths C and D, thereby increasing the heat capacity of the heat exchange fluid in the fluid circulation paths C and D, The temperature change of the heat exchange fluid is reduced.

When the above-described suction mode is executed (the four-way valves 21, 23, 25, 26, 29, 47, and 52 are
In the position indicated by the solid line, the heat exchange fluid is cooled by the cold heat when the refrigerant evaporates in the evaporative condenser 13, and the cooled heat exchange fluid is circulated to the supercooling unit cooler 270, whereby the supercooling unit 43 To cool. Here, of the cold heat when the refrigerant evaporates, the portion not used for cooling the supercooling unit cooler 270 is all stored in the heat exchange fluid circulating in the fluid circulation path C. Further, since the engine cooling water circulates through the cooling water circuit E0, all the heat of the engine 22 is stored in the engine cooling water circulating through the cooling water circuit E0.
Since the heat capacity is large by the amount of the cooling water tank 51 and the adsorption mode is relatively short (the above-described adsorption mode time T1, for example, 70 seconds), the engine cooling water circulating through the cooling water circulation path E0 is used. Extremely high water temperature is suppressed.

Then, the above-mentioned desorption mode (four-way valve 2)
When the positions 1, 23, 25, 26, 29, 47, and 52 are switched to the positions indicated by the dotted lines in FIG. 3), the heat exchange fluid storing the cold heat is circulated to the supercooling unit cooler 270 via the fluid circulation path D. The supercooling unit cooler 270 is cooled. In addition, in the adsorption mode, the heat of the engine 22 is stored in the engine cooling water circulating through the fluid circulation path E0, and the engine cooling water is circulated to the adsorption core 12 via the fluid circulation path E when the refrigerant is desorbed. The heat of the engine 22 can be used more effectively for heating the adsorption core 12 as compared with the case where the heat of the engine 22 is released outside the room at the time of refrigerant adsorption.

Since it is necessary to cool the refrigerant flowing through the supercooling section 43 only when the vapor compression refrigeration apparatus 2 is being cooled, the adsorption refrigeration apparatus 1 is operated only when the vapor compression refrigeration apparatus 2 is being cooled. During heating of the vapor compression refrigeration system 2, the adsorption refrigeration system 1 is not operated. In the present embodiment, in the adsorption mode, cold heat is stored in the heat exchange fluid circulating in the fluid circulation path C, and in the desorption mode, the heat exchange fluid that has accumulated cold heat in the adsorption mode is cooled through the bypass fluid circulation path D. By circulating through the heater 270, the refrigerant flowing through the heating unit 43 can be cooled, so that the refrigerant flowing through the supercooling unit 43 can be continuously cooled by one adsorption core 12. Therefore, in the suction mode, it is not necessary to desorb a suction core different from the suction core 12. As a result, the number of adsorption cores 12 required for continuous cooling can be reduced as compared with the related art, so that the adsorption refrigeration apparatus 1 can be reduced in size and cost can be reduced.

(Other Embodiments) First, in the first and second embodiments, the regenerator 28 is arranged downstream of the indoor heat exchanger 27 in the fluid flow. It may be arranged upstream of the fluid flow of the vessel 27. In the third embodiment, instead of providing the tanks 51 and 28a, the heat capacity of the fluid in each fluid circulation path may be increased by lengthening the fluid pipe.

In the first to third embodiments, the evaporator and the condenser are constituted by the evaporative condenser 13, but the evaporator and the condenser are provided separately. Is also good. In addition, the present invention is not limited to each of the above-described embodiments. For example, a configuration may be employed in which the heat exchange with the outside (outside air) is directly performed in the evaporating core accommodating portion 112 accommodating the evaporating core. However, the present invention can be implemented with appropriate changes without departing from the scope of the present invention.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of an adsorption-type refrigeration apparatus according to a first embodiment of the present invention.

FIG. 2 is a schematic configuration diagram of an adsorption refrigeration apparatus according to a second embodiment of the present invention.

FIG. 3 is a schematic configuration diagram of an adsorption-type refrigeration apparatus according to a third embodiment of the present invention.

[Explanation of symbols]

12: adsorption core, 13: evaporative condenser (evaporator, condenser), 27: indoor heat exchanger (cooler), 28: regenerator
C, D: fluid circulation path.

Claims (5)

[Claims] An adsorption core (12) that adsorbs a refrigerant by being cooled and desorbs the refrigerant by being heated.
When the refrigerant is adsorbed by the adsorption core (12) to adsorb the refrigerant,
An evaporator (13) for evaporating the refrigerant; and a refrigerant desorption where the adsorption core (12) desorbs the refrigerant.
A condenser (13) for condensing the refrigerant; and a regenerator (28) for storing cold heat when the refrigerant evaporates in the evaporator (13). While cooling, the cold heat is stored in the regenerator (28), and when the refrigerant is desorbed, the regenerator (2
8) An adsorption refrigerating apparatus, wherein the object to be cooled is cooled by the cold heat stored in 8). 2. A cooler (27) for cooling the object to be cooled.
A first fluid circulation path (C) for circulating a heat exchange fluid between the evaporator (13), the regenerator (28), and the cooler (27); ), And a second fluid circulation path (D) for circulating a heat exchange fluid between the cooler (27) and a heat exchange fluid in the first fluid circulation path (C) when the refrigerant is adsorbed. 2. The adsorptive refrigeration apparatus according to claim 1, wherein a heat exchange fluid is circulated through the second fluid circulation path (D) during the desorption of the refrigerant. 3. 3. An adsorption core for adsorbing a refrigerant by being cooled and desorbing the refrigerant by being heated.
When the refrigerant is adsorbed by the adsorption core (12) to adsorb the refrigerant,
An evaporator (13) for evaporating the refrigerant; and a refrigerant desorption where the adsorption core (12) desorbs the refrigerant.
A condenser (13) for condensing the refrigerant; a cooler (270) for cooling the object to be cooled; and a main fluid circulation for circulating a heat exchange fluid between the evaporator (13) and the cooler (270). The evaporator (13) in the path (C) and the main fluid circulation path (C).
And a bypass fluid circulation path (D) for circulating a heat exchange fluid to the cooler (270) by bypassing the cooling medium. When the refrigerant is adsorbed, the refrigerant is evaporated by the evaporator (13). The heat exchange fluid is cooled, and the cooled object is cooled by circulating the cooled heat exchange fluid through the main fluid circulation path (C) to the cooler (270). The cooling object is cooled by circulating the heat exchange fluid cooled by the cold heat during the adsorption of the refrigerant to the cooler (270) through the bypass fluid circulation path (D). Adsorption refrigeration equipment. 4. An engine (22) and said adsorption core (1).
2) a main cooling water circulation path (E) for circulating engine cooling water, and the cooling water circulation path (E).
2) a bypass cooling water circulation path (E0) for bypassing 2), wherein the engine cooling water is circulated to the adsorption core (12) through the main cooling water circulation path (E) at the time of desorption of the refrigerant. The core (12) is heated, and when the refrigerant is adsorbed, the bypass cooling water circulation path (E0)
The heat of the engine (22) is stored in the engine cooling water circulating in the bypass cooling water circulation path (E0) by circulating the engine cooling water to the engine. The adsorption-type refrigeration apparatus according to the above. 5. The difference between the heating temperature of the adsorption core (12) and the condensation temperature in the condenser (13) is determined by the cooling temperature of the adsorption core (12) and the temperature in the evaporator (13). The time (T2) for heating the adsorption core (12) to desorb the refrigerant is made longer than the time for cooling the adsorption core (12) and adsorbing the refrigerant (T1). The adsorption refrigeration apparatus according to any one of claims 1 to 4, wherein the refrigeration apparatus is shortened.