JP2000046425A - Cooling apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make more effective cooling effect and assure cooling controllability with an adjustment of a water spray amount by individually acting cooling action by low temperature air. SOLUTION: In a closed air refrigerating cycle where a compressor 51, a heat dissipation heat exchanger 53, an expansion machine 52, and a cooling heat load 20 are disposed in order, a pair of adsorbers 11, 12 are provided for dehumidification. The cooling heat load 20 comprises a chamber 18 to be cooled which includes a cooling heat exchanger therein and a water spray cooling apparatus 10 provided in contact with the chamber 18.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention uses an air refrigeration cycle which compresses air as a refrigerant, cools high-temperature and high-pressure compressed air to near normal temperature, and then obtains low-temperature air through an expander. Cooling device.

[0002]

2. Description of the Related Art A conventional cooling device using an air refrigeration cycle arranges a compressor, a heat-radiating heat exchanger and an expander along a flow path of air serving as a working medium, and the compressor and the expansion are used as prime movers. Operate the machine, perform adiabatic compression with the compressor, cool to ambient temperature with a heat exchanger for heat dissipation, perform adiabatic expansion with an expander,
This is to obtain low-temperature air.

[0003] However, in the above-mentioned cooling device, since the working medium is air, it does not accompany evaporation and condensation in the temperature range of a normal air conditioner, so that it is impossible to use latent heat. For this reason, the flow rate of air as the refrigerant is inevitably increased,
The capacity of compressors and expanders is increased, the number of revolutions and noise are increased, and the heat transfer area of the heat exchanger for heat dissipation is increased.

[0004] Therefore, the above problem is solved by performing cooling by a combined cycle of an inverse Brayton cycle in which adiabatic compression and adiabatic expansion are performed to obtain low-temperature air and an inverse ranking cycle in which water is evaporated to remove latent heat of evaporation. A proposal has been made.

That is, according to the proposal disclosed in Japanese Patent Application Laid-Open No. 62-102061, a cooling device using the above-described combined cycle is arranged along a flow path of air as a working medium as shown in FIG. The compressor 51, the heat-exchanging heat exchanger 53, the expander 52, and the water spray device 56 are arranged in this order. The water spray device 56 having the function of the reverse ranking cycle causes the latent heat of evaporation of water to generate low-temperature air. This is for further lowering the temperature. A steam separator 57 using a steam separation membrane or the like is provided between the heat exchanger 53 for heat dissipation and the expander 52 to separate steam contained in the air passing through the heat exchanger 53 for heat dissipation. The dried air is sent to the expander 52, and the separated water vapor is removed outside the system. A throttle 58 is provided at the spraying portion of the water spraying device 56 so that air and water come into uniform contact to further lower the temperature by latent heat of evaporation. The air that has passed through the water spray device 56 is sent to the cooling heat exchanger 59 and the indoor air is cooled by the fan 60. Alternatively, the air that has passed through the water spray device 56 without using the heat exchanger 59 is directly used for cooling or the like.

In the above cooling device, the indoor air is converted into high-temperature and high-pressure air by a compressor 51 driven by a prime mover 54, then cooled down to a temperature close to the indoor air temperature by a radiating heat exchanger 53, and moisture is removed by a steam separating device 57. Is done. Then, it is adiabatically expanded in the expander 52 and becomes low-temperature (lower than room air) and low-pressure air.
Sent to 8. Here, the latent heat of evaporation removes heat from the low-temperature low-pressure air by spraying water, thereby further lowering the temperature. The low-temperature air thus obtained is blown directly into the room and used for indoor cooling, or used for indoor cooling via the cooling heat exchanger 59.

[0007]

By the way, in the conventional air refrigeration cycle, the air flow rate is increased, and the compressor,
Although the enlargement of the expander and the responsiveness to the load have been somewhat solved by the above-mentioned water spraying device, it is still insufficient, and there is still room for improvement of the cooling capacity.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and has as its object to provide a cooling device which can improve the function of a cooling device using an air refrigeration cycle.

In order to achieve the above-mentioned object, a conventional water spray device which sprays water onto low-temperature air as a working medium and further lowers the temperature of low-temperature air through generation of latent heat due to evaporation of water has been reviewed. A water spray cooling device that functions effectively is required.

[0010]

Therefore, a first aspect of the cooling device of the present invention is to provide a cooling device using air as a medium through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander in that order. In an air refrigeration cycle for forming a low-temperature air and cooling a cooling heat load, a main cooling means for cooling a heat load by the low-temperature air, and a cold heat obtained by spraying water on the low-temperature air used for the cooling means. And a re-cooling means for re-cooling the heat load by the cold heat source.

According to the first aspect of the present invention, low-temperature air obtained through a flow path consisting of a compressor, a heat-dissipating heat exchanger, a dehumidifier, and an expander in the order of air is used as a medium, and The cooling heat load is cooled via cooling means, and the heated low-temperature air is cooled by spraying water to deprive the heat amount corresponding to the latent heat of evaporation, thereby forming a further low-temperature cold heat source. The heat load is cooled by the recooling means.

The main cooling means may have a configuration in which a heat exchanger is interposed in a heat medium forming a heat load.

Alternatively, the main cooling means may be constituted by blowing low-temperature air directly into a heat medium constituting a heat load.

Further, the temperature of the cold heat source may be adjusted by adjusting the spray amount of the water spray.

Further, the recooling means according to claim 1 is characterized in that a cooling water film is formed on an outer wall of a heat exchanger containing a target cooling medium of the main cooling means.

That is, according to the present invention, a part of the outer wall of the container of the heat medium to be the main cooling means is used as a heat exchanger, and the non-vaporized spray which is further cooled by water spray is applied to the outer wall. A cold water film made of cold water is formed to re-cool the heat medium from the outer wall.

Further, the recooling means according to claim 1 is characterized in that cold water is circulated in a heat exchanger provided separately from the main cooling means.

That is, according to the third aspect of the present invention, a heat exchanger is provided in a container containing a heat medium to be subjected to main cooling means, and a cold heat source of low-temperature cold water further cooled by water spray and the heat source are provided. By circulating cold water between the exchanger and
The heat medium is re-cooled.

Further, the recooling means according to claim 1 is characterized in that a heat pipe for propagating cold heat is provided between the main cooling means and the cold heat source.

That is, in the invention according to claim 4, a heat pipe is provided between the heat medium targeted by the main cooling means and the low-temperature air further cooled by water spray, and the heat medium is re-cooled. It is like that.

The second invention of the cooling device of the present invention is as follows.
In the air refrigeration cycle that forms low-temperature air through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander using air as a medium to cool the cooling heat load, A water spray cooling heat exchanger device comprising a low temperature air intake means, an adjustable water fine particle spraying means, a reduced pressure evaporating means, and a chamber to be cooled, and obtains a low temperature air whose temperature can be appropriately adjusted by the apparatus. It is characterized by doing so.

According to a fifth aspect of the present invention, the low-temperature air obtained through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander in the order of air is used as the medium of the expander. A water spray cooling heat exchanger device provided at the subsequent stage is provided, and the device is configured to include a low-temperature air intake means, an adjustable water fine particle spray means, and a reduced pressure vaporization means, which is suitable for a cooling heat load. The cooling air is supplied to the cooled room so that the required cooling can be appropriately performed.

Further, the dehumidifier according to the first and fifth aspects is configured to use a pair of adsorbers, and the high-temperature and high-pressure air from the compressor flows through the adsorber that has already been adsorbed to regenerate the air. Next, the high-pressure air before the adiabatic expansion from the heat-dissipating heat exchanger flows through the other regenerated adsorber to dehumidify it, regenerate one adsorber and dehumidify the other adsorber, and perform regeneration and dehumidification. It is characterized by being configured to be switchable alternately.

According to the sixth aspect of the present invention, the high-pressure air before the adiabatic expansion can always maintain a dry state.
Further, since high-temperature compressed air is used for regeneration, the energy saving effect is great.

[0025]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to an embodiment shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not merely intended to limit the scope of the present invention, but are merely illustrative examples unless otherwise specified. Absent. Note that the same reference numerals are used when using components having the same product name and the same function as the components described in the drawings showing the conventional example.
FIG. 1 is a system diagram showing a schematic configuration of a first embodiment of a cooling device of the present invention, and FIG. 2 is a diagram showing a modification of an adsorption regeneration circuit using the adsorber of FIG. 3A and 3B show the re-cooling means of the cooling heat load in FIGS. 1 and 2, wherein FIG. 3A shows a cooling water circulation and FIG. 3B shows a heat pipe. FIG. 4 is a system diagram showing a schematic configuration of a second embodiment of the present invention.

As shown in FIG. 1, a cooling device according to a first embodiment of the present invention includes a compressor 51, a heat-radiating heat exchanger 53,
A pair of adsorbers 11 and 12 are provided for dehumidification in a closed air refrigeration cycle arranged in the order of the expander 52 and the cooling heat load 20, and the cooling heat load 20 incorporates a cooling heat exchanger 59. A cooled chamber 18 to form a cooling heat load;
The water spray cooling device 10 provided in contact with the cooled chamber 18
It is comprised by these.

The adsorber 12 is provided between the heat-radiating heat exchanger 53 and the expander 52, and dehumidifies the high-pressure, high-humidity air cooled by the heat-radiating heat exchanger 53 via a built-in adsorbent. It is like that. The adsorber 11 is provided between the compressor 51 and the heat exchanger 53 for heat radiation, and the adsorbent that has already been adsorbed is regenerated by the high-temperature and high-pressure air from the compressor 51. And are performed alternately.

The water spray cooling device 10 is provided adjacent to the cooled room 18 containing the cooling heat exchanger 59,
It comprises a water spray pipe 10a provided with a control valve 10b.
Water is sprayed on the low-temperature air adiabatically expanded by the expander whose temperature has been raised to about 0 ° C., and the low-temperature air thus heated is cooled by latent heat to form a low-temperature vaporized fluid containing unvaporized water droplets. A cold water film is formed by spraying on the wall surface and flows down along the wall surface. The cooling medium re-cools the heat medium in the chamber to be cooled. The amount of water spray is adjusted by the control valve 10b to control the degree of cooling by latent heat, and the cooled chamber 1 is cooled by spraying a low-temperature vaporized fluid.
The room temperature of No. 8 can be adjusted appropriately. Note that low-temperature air may be directly blown into the cooled chamber 18 instead of the cooling heat exchanger 59.

In the cooling device shown in FIG. 1 having the above structure, the air as the working medium flows along the flow path shown by the solid line arrow, and the compressor 51, the heating coil 11 a of the adsorber 11, the radiating heat exchanger 53, The closed air refrigerating cycle is formed by circulating the adsorber 12, the expander 52, and the cooling heat load 20.
The air as the working medium is adiabatically compressed by the compressor 51 to become high-temperature and high-pressure air, and then cooled to the ambient temperature by the heat radiating heat exchanger 53, and excess moisture equivalent to the saturation of the ambient temperature is condensed and external water (not shown). Is discharged to The high-pressure air that has dropped in temperature to the ambient temperature that has exited the heat-radiating heat exchanger 53 is further dehumidified by the adsorbent incorporated in the adsorber 12 to become high-pressure dry air. Then, it is adiabatically expanded by the expander 52 to become low-temperature air of about 0 ° C., and is introduced into the cooling heat exchanger 59 incorporated in the cooled room 18 of the cooling heat load 20. The heat medium contained in the cooled room 18 is cooled by the cooling heat exchanger 59 to form a main cooling means. The low-temperature air at approximately 0 ° C. passing through the cooling heat exchanger 59 is approximately 3 ° C.
Although the temperature is raised to about 5 ° C., it is cooled again by the latent heat of vaporization of the spray water in the water spray cooling device 10 and becomes a low-temperature fluid, forming a cold heat source. Then, a cold water film made of the low-temperature fluid is sprayed on the wall surface of the cooled room 18 to flow down, and the built-in heat medium is re-cooled. Therefore, the cooled room 18 undergoes re-cooling in addition to the main cooling, and the cooling heat load 20 is individually cooled by the low-temperature air and the low-temperature fluid to enable high-efficiency cooling. Since the water spray pipe 10a of the water spray cooling device 10 is provided with the control valve 10b, the temperature of the cooled room 18 can be controlled by adjusting the opening degree.

The high-temperature, high-pressure air exiting the compressor 51 passes through the heating coil 11a of the adsorber 11, heats the adsorbent, desorbs and regenerates the water, and is sent to the heat exchanger 53 for heat radiation. Cool to ambient temperature. The air that has exited the heat exchanger 53 is dried by the moisture adsorption reaction of the adsorbent contained in the adsorber 12. The reaction heat at this time is returned from the outlet of the expander 52 or from the middle thereof as shown in FIG.
The air is removed from the low-temperature air via a and 21b and is returned to the introduction side of the compressor 51. The flow path indicated by the solid arrow indicates the case where the adsorber 12 is used for adsorption and the adsorber 11 is used for regeneration, and the flow path indicated by the dotted arrow indicates that the adsorber 11 is used for adsorption and the adsorber 12 is used. Is used for regeneration, and a pair of adsorbers is configured to be capable of switching between adsorption and regeneration. That is, the flow path system in the case of the solid arrow is the compressor 51 → the heating coil 11a of the adsorber 11.
→ heat-radiating heat exchanger 53 → adsorber 12 → expander 52, the flow path system in the case of the dotted arrow is compressor 51 → heating coil 12a of adsorber 12 → heat-radiating heat exchanger 53 → adsorber 11 → expansion Machine 52.

FIG. 2 is a diagram showing a channel system in which the heat of the adsorption reaction is returned from the middle of the expander 52 to the inlet channel 21b of the compressor 51 via the return channel 21a as described above. The reflux path is a return flow path system in the case of a practical arrow, the flow path 21 → the heating coil 12a of the adsorber 12 → the valve O → the adsorber 11 → 21b, and the return flow path system in the case of the dotted arrow is:
Flow path 21 → heating coil 11a of adsorber 11 → valve S →
It becomes like the adsorber 12 → 21b.

FIG. 3 shows re-cooling means for cooling the cooling heat load shown in FIGS. 1 and 2, wherein (A) is based on circulating cold water by a pump and (B) is based on a heat pipe. FIG. 3A shows that a heat exchanger 59 is provided in a cooled room 18 containing a heat medium to be subjected to main cooling means.
A pump 2 is supplied to the heat exchanger from a cold water tank 21 as a cold heat source.
2 means that a re-cooling means is formed by circulation. The cold heat source introduces the low-temperature air supplied from the expander 52 into a heat exchanger 59 built in the cooled room 18 to form a main cooling unit to cool the heat medium in the cooled room. As a result of the cooling, the raised low-temperature air receives the water spray pumped up through the water spray pipe 10a and the control valve 10b. Has formed.

FIG. 3B shows the inside of the cooled chamber 18 containing the heat medium to be the main cooling means and the cold water tank 21.
A heat pipe 23 is provided between the cooling medium and the heat source formed therein, and the heat pipe 23 forms means for re-cooling the heat medium incorporated in the cooled room 18. In the cold heat source, low-temperature air supplied from the expander 52 is blown into a cooled room 18 containing a heat medium, and cools the heat medium to form a main cooling unit. The low-temperature air after the main cooling is introduced into the cold water tank 21. The low-temperature air receives the water spray pumped up through the water spray pipe 10a and the control valve 10b, and is further cooled by the latent heat of evaporation. Forming a cold heat source.

FIG. 4 is a system diagram showing a schematic configuration of a second embodiment of the present invention. As shown in the figure, in the case of the present embodiment, the cooling heat exchanger 59 and the water spray cooling device 1 of FIG.
Instead of cooling the chamber 18 to be cooled by using
The cooling heat load 20 is provided with a water spray cooling heat exchanger device 15 so as to obtain a temperature-adjustable cold air from the low-temperature air obtained by the expander 52, thereby cooling the cooled room 18. is there.

In the case of the second embodiment, as in FIG.
The air as the working medium is adiabatically compressed by the compressor 51 to become high-temperature and high-pressure air, and then cooled to the ambient temperature by the heat-radiating heat exchanger 53, and excess moisture corresponding to the ambient temperature saturation is condensed and not shown. It is discharged outside. The high-pressure air whose temperature has dropped to the ambient temperature exiting the heat-radiating heat exchanger 53 is further dehumidified by the adsorbent incorporated in the adsorber 12 to become high-pressure dry air. Then, it is adiabatically expanded by the expander 52 to become low-temperature air of about 0 ° C. and sent to the water spray cooling heat exchanger device 15 shown in the figure.

The water spray cooling heat exchanger device 15 comprises a water spray vaporizing chamber 16, a reduced pressure vaporizing chamber 17, and a cooled chamber 18. The water spray vaporization chamber 16 includes a low-temperature air intake 16e, a control valve 16c, a water pump 16b, and a water spray pipe 16.
a) and a tank 16d, and the reduced-pressure vaporization chamber is provided with a suction fan 17a and a return air port 17a.
b. The surplus water droplets are stored in the lower tank 16d.

Then, the low-temperature air introduced into the water-spray cooling heat exchanger device 15 is exposed to high-pressure fine particle spray via a water pump 16b, and water vaporization is promoted under reduced pressure. Cooled. The low-temperature air further cooled as described above becomes cold air in the reduced-pressure evaporating chamber 17 and is introduced into the cooled chamber 18 by the suction fan 17a to be cooled.
8 is cooled. A control valve 16c for regulating the amount of water spray is provided in the water fine particle spraying means, and a cooled chamber 18 is provided in the reduced-pressure vaporization chamber 17.
A cooling air return port 17b is provided, and the temperature of the cooled room 18 can be adjusted.

[0038]

According to the first aspect of the present invention, in the first aspect of the present invention, the low-temperature air after forming the main cooling means by the low-temperature air for the cooling heat load is sprayed with water, and the cold heat source is formed by the latent heat of evaporation of the water. Then, a re-cooling means for the cooling heat load is formed by the heat source.
Therefore, the cooling action by low-temperature air is applied individually,
The cooling effect can be made more efficient, and cooling controllability can be imparted by adjusting the amount of water spray.

According to the second, third and fourth aspects of the present invention, the recooling means is provided by flowing a cold water film,
It can be diversified into those using cold water circulation and those using heat pipes, each of which can be adapted to the right place.

According to the fifth aspect of the present invention, the low-temperature air obtained through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander using air as a medium is supplied to the expander. Introduced by a water spray cooling heat exchanger device provided at the subsequent stage, the low-temperature air is further cooled down in a water spray vaporization chamber, and then its temperature is further lowered in a decompression vaporization chamber, and covered by a suction fan and a return air port. By controlling the temperature of the cooling chamber to an appropriate temperature, it is possible to blow cool air suitable for the cooling heat load.

According to the sixth aspect of the present invention, the high-pressure air before adiabatic expansion can always maintain a dry state. Further, since high-temperature compressed air is used for regeneration, the energy saving effect is great.

[Brief description of the drawings]

FIG. 1 is a system diagram showing a schematic configuration of a cooling device according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a modification of the suction regeneration circuit using the suction device of FIG. 1;

FIGS. 3A and 3B show the re-cooling means of the cooling heat load in FIGS. 1 and 2, wherein FIG. 3A shows a cooling water load, and FIG. 3B shows a heat pipe.

FIG. 4 is a system diagram showing a schematic configuration of a second embodiment of the present invention.

FIG. 5 is a system diagram showing a schematic configuration of a cooling device using a conventional air refrigeration cycle.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Water spray cooling apparatus 10a, 16a Water spray pipe 10b, 16c Control valve 11, 12 Adsorber 15 Water spray cooling heat exchanger apparatus 16 Water spray vaporization chamber 16b, 22 Water pump 17 Decompression vaporization chamber 18 Cooling chamber 20 For cooling Heat load 21 Cold water tank 23 Heat pipe

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Makoto Sano 2-13-1, Botan, Koto-ku, Tokyo Inside Maekawa Manufacturing Co., Ltd. (72) Inventor Katsumi Fujima 2-3-1 Botan, Koto-ku, Tokyo Stock Inside the company Maekawa Works

Claims (6)

[Claims] 1. An air refrigeration cycle in which low-temperature air is formed using air as a medium through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander to cool a cooling heat load. A main cooling means for cooling the heat load by the low-temperature air, a cold heat source obtained by spraying water on the low-temperature air used for the cooling means, and a re-cooling means for re-cooling the heat load by the cold heat source. A cooling device comprising: 2. The cooling apparatus according to claim 1, wherein said re-cooling unit is formed by forming a cold water film on an outer wall of a container containing a target cooling medium of the main cooling unit. 3. The cooling device according to claim 1, wherein said re-cooling means is configured to circulate cold water in a heat exchanger separately provided in the main cooling means. 4. The cooling device according to claim 1, wherein said re-cooling means is provided with a heat pipe for transmitting cold heat between the main cooling means and the cold heat source. 5. An air refrigeration cycle in which low-temperature air is formed through a flow path consisting of a compressor, a heat-radiating heat exchanger, a dehumidifier, and an expander using air as a medium to cool a cooling heat load. In the latter stage of the expander, a water spray cooling heat exchanger device provided with a low temperature air intake means, an adjustable water fine particle spraying means, and a reduced pressure vaporization means is provided, and the apparatus obtains low temperature air whose temperature can be appropriately adjusted. A cooling device characterized in that: 6. The dehumidifier has a configuration using a pair of adsorbers, and regenerates high-temperature and high-pressure air from a compressor through the adsorber which has been adsorbed, before adiabatic expansion from a heat-radiating heat exchanger. The cooling device according to claim 1, wherein the high-pressure air is dehumidified by flowing into another regenerated adsorber, so that regeneration and dehumidification can be alternately switched.