JP2011133191A - Refrigerant adsorbent charging container, and bleed air recovering device for turbo refrigerating machine, turbo refrigerating machine and refrigerant recovering device, including the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant adsorbent charging container capable of being heated or cooled to a uniform temperature with small energy, and to provide a bleed air recovering device for a turbo refrigerating machine, the turbo refrigerating machine, and a refrigerant recovering device, including the same. <P>SOLUTION: In the refrigerant adsorbent charging container including a central member 10 forming a central section, an outer peripheral member 1 forming an outer peripheral section, and plate-shaped fins 2 connecting the central member 10 and the outer peripheral member 1 to each other, the charging container has a refrigerant adsorbent storage space 6 defined by the central member 10, the outer peripheral member 1 and the plate-shaped fins 2 inside thereof, and further has a gas inlet and a gas outlet, the inlet and the outlet are communicated with each other by a gas passage used also as the refrigerant adsorbent storage space 6, a gas can flow from the inlet toward the outlet, and the charging container can be heated and cooled from the external of the outer peripheral member 1. The outer peripheral member 1 may include plate-shaped fins 5 at its outer part, and the central member 10 and the outer peripheral member 1 may include plate-shaped fins 3, 4 extending from one side toward the other side. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a refrigerant adsorbent filling container for holding a refrigerant adsorbent, which is a substance having low thermal conductivity and poor fluidity, in a sealed state, and repeatedly heating and / or cooling the substance in a short time, For example, a refrigerant adsorbent filling container used for repeatedly adsorbing and desorbing a volatile gas such as fluorocarbon used as a working medium of a refrigerator to a refrigerant adsorbent held inside the container, and for a turbo refrigerator equipped with the same The present invention relates to an extraction recovery device, a turbo refrigerator, and a refrigerant recovery device.

In a turbo chiller using a so-called low-pressure refrigerant, the pressure of the entire chiller generally decreases to a value equal to or lower than the atmospheric pressure while the refrigerator is stopped, and the evaporator-side pressure decreases during operation of the refrigerator. In the turbo chiller, it is practically difficult to completely prevent leakage of air and the like from the atmosphere into the refrigerator, and the leaked air has various problems on the chiller. The leaked air must be discharged outside the machine. For this reason, this kind of turbo refrigerator is usually provided with a bleed recovery device.
In order to suppress the discharge amount of the refrigerant into the atmosphere in the “extracted air recovery device, its operating method, and the turbo refrigeration machine equipped with it (Japanese Patent Application No. 2009-227165)” previously filed by the present inventors, Using an adsorbent, we proposed a bleed air recovery device that can reduce the amount of refrigerant leaking from the bleed air recovery device of a turbo chiller into the atmosphere to the limit, and a method for operating the same.

  However, since the refrigerant adsorbent is a porous material, as represented by activated carbon and zeolite, for example, it generally has low thermal conductivity, and it is difficult to perform heating and cooling quickly and uniformly. This contributes to the difficulty of suitable operation of the extraction recovery device and the refrigerant recovery device. That is, when the refrigerant is adsorbed to a certain degree by the refrigerant adsorbing material, the refrigerant adsorbing material practically loses the refrigerant adsorbing capacity. Therefore, it is necessary to desorb the refrigerant in order to use it again as the refrigerant adsorbing material. However, since the refrigerant once adsorbed cannot be desorbed as it is, for example, the refrigerant adsorbent itself is heated to raise the temperature, or the environmental pressure is lowered to be exposed to a low pressure state. It is necessary to use both methods together. And even if the refrigerant is desorbed in this way, the refrigerant adsorbing power cannot be recovered by itself, and after that, it is necessary to cool the refrigerant adsorbing material to lower the temperature of the refrigerant adsorbing material itself. Thus, in order to repeatedly use the same refrigerant adsorbent, it is necessary to repeatedly heat and cool the refrigerant adsorbent in the refrigerant adsorbent filling container. Therefore, of course, in order to effectively use the refrigerant adsorbent, it is necessary to shorten the time required for heating and cooling to a level suitable for practical use.

  However, as described above, the refrigerant adsorbent generally has a low thermal conductivity, so that it takes a long time for heating and cooling, or if the heating / cooling time is short, it can exhibit sufficient adsorption capacity. There were problems such as being unable to. Furthermore, it is preferable that the temperature after heating of the refrigerant adsorbent itself and the temperature after cooling are uniform irrespective of the respective locations in the refrigerant adsorbent filled container. That is, when a considerable temperature difference occurs depending on the location, during heating, the average temperature of the refrigerant adsorbent is raised to a temperature suitable for refrigerant desorption. As a result of excessive temperature rise of the refrigerant adsorbent material at the relatively high temperature, the deterioration is promoted, and there is a problem that sufficient desorption of the refrigerant cannot be achieved at the low temperature. The refrigerant adsorbents in various locations have problems such as insufficient adsorption capacity. Also, in the case of heating, in order to set the average temperature to an appropriate value, for example, it is necessary to increase the maximum temperature reached by the refrigerant adsorbent, so that the required energy of the heater or the like increases, and in the case of cooling, for example, Since it is necessary to cool the refrigerant adsorbent filling container with a fan or the like for a long time, there is also a problem that the required energy is increased in this case.

As a reference example of the structure of the refrigerant adsorbent filled container, when considering the prior art, for example, as shown in Japanese Patent Application Laid-Open No. 2008-270297, a container composed of flat plate portions facing in parallel is provided. A heat radiating container having a plurality of fins is disclosed. This publication relates to a power unit including a semiconductor chip. When this mode is applied to a refrigerant adsorbent-filled container, the flat container shape must be enlarged while maintaining pressure resistance and airtightness. However, it is necessary to allow a certain pressure difference between the internal pressure and the external pressure of the container. For the refrigerant adsorbent-filled container, for example, considering the stress applied to the constituent members and the magnitude of the resulting strain, it is disadvantageous in design.
Furthermore, in a container that receives repeated heating and cooling cycles while containing an object with poor fluidity such as a refrigerant adsorbent inside, when the outer peripheral part, i.e., the member constituting the outer shape is formed of a flat plate, For example, in a rectangular parallelepiped shape, a temperature difference is likely to occur between the corner portion and the center of the flat plate portion. Therefore, the amount of thermal expansion and contraction is not uniform, and is caused by contact with the refrigerant adsorbent housed inside. Since thermal stress and strain are also likely to occur, it is difficult to realize a container that can withstand practical use as a result.

In the above, an example of a turbo refrigerator using a low-pressure refrigerant has been described. However, not only the low-pressure refrigerant but also a refrigerator using a so-called high-pressure refrigerant, for example, a non-condensable gas mixed at the time of refrigerant charging such as during decomposition and maintenance This causes various inconveniences such as a decrease in efficiency and corrosion of materials during operation of the refrigerator, so that it needs to be extracted outside the apparatus. When extracting the non-condensable gas once mixed inside the refrigerator, in the refrigerator using a high-pressure refrigerant, for example, the refrigerant gas is condensed using a refrigerant recovery device, and only the non-condensable gas is separated from the refrigerant gas. It is generally released to the atmosphere. Therefore, it is common for low-pressure refrigerants and high-pressure refrigerants to separate the non-condensable gas from the refrigerant in the shortest possible time and to keep the refrigerant component remaining in the separated non-condensable gas as small as possible. It was a problem.
JP 2008-270297 A

  In view of the above-mentioned background art, the present invention promptly removes the refrigerant adsorbent itself even if the internal filling material is a refrigerant adsorbent having a low thermal conductivity by at least heating or cooling from the outside. Regardless of the location of the filling container, a refrigerant adsorbent filling container that can be heated or cooled to a uniform temperature and with a small amount of energy and can withstand repeated temperature rise and fall cycles, and a turbo refrigerator equipped with the same It is an object to provide a bleed air recovery device, a turbo refrigerator, and a refrigerant recovery device.

In order to solve the above problems, the present invention includes a central member that forms a central portion, an outer peripheral member that forms an outer peripheral portion, and plate-like fins that interconnect the central member and the outer peripheral member. A refrigerant adsorbent-filled container, in which the refrigerant adsorbent storage space is formed by the central member, the outer peripheral member, and the plate-like fins, and further includes a gas inlet and an outlet. The inlet and the outlet are connected to each other by a gas passage also serving as the refrigerant adsorbing material storage space, the gas can flow from the inlet to the outlet, and the filling container is heated from the outside of the outer peripheral member. The refrigerant adsorbent-filled container is characterized in that it can be cooled.
In the refrigerant adsorbent filling container, the outer peripheral member may further include a plate-shaped fin on the outside, and the central member, the outer peripheral member, and the plate-shaped fin may be formed integrally with at least two of them. In addition, the central member and the outer peripheral member include plate-like fins extending from one side to the other side, and the fins can be formed in parallel to any other fin.

In the present invention, the refrigerant adsorbent filled with the refrigerant adsorbent and the refrigerant gas separation means for separating the noncondensable gas extracted from the turbo refrigerator together with the refrigerant gas from the refrigerant gas and discharging it into the atmosphere. A bleed air recovery apparatus comprising a filling container, wherein the refrigerant adsorbent filling container is a bleed air recovery apparatus for a turbo chiller as the refrigerant adsorbent filling container of the present invention described above. The turbo chiller provided with the apparatus is a turbo chiller using the above-described extraction recovery device for a turbo refrigeration unit as an extraction recovery device.
Furthermore, in the present invention, the refrigerant recovery device for adsorbing and recovering only the refrigerant gas from the refrigerant gas containing the non-condensable gas and discharging the non-condensable gas into the atmosphere is the refrigerant adsorbent of the present invention described above. The refrigerant recovery device is characterized in that a filling container is filled with a refrigerant adsorbent.

  By configuring the refrigerant adsorbent-filled container as in the present invention, it is possible to perform heating and cooling quickly and uniformly even with a refrigerant adsorbent that generally has low thermal conductivity and is difficult to heat and cool. Thus, the refrigerant can be desorbed and sufficiently removed from the refrigerant adsorbing material, and the adsorbing power of the adsorbing material can always be maintained at a high level. In addition, since the heat stress accompanying heating and cooling of the refrigerant adsorbent filling container, and the stress and strain due to the pressure difference inside and outside the filling container can be made small and uniform, it is resistant to repeated cycles of temperature rise and fall, And the airtightness of this filling container can be maintained suitably. Therefore, by using the refrigerant adsorbent filled container according to the present invention, it is possible to provide an extraction recovery device, a refrigerant recovery device, a turbo chiller, and a refrigerant recovery device that are excellent in environmental characteristics.

Hereinafter, the present invention will be described in detail.
Refrigerant adsorbents generally have low thermal conductivity, virtually no fluidity, and it is difficult to raise or lower the temperature quickly and uniformly during heating and cooling. Therefore, in the present invention, in the refrigerant adsorbent filling container that also serves to heat and cool the refrigerant adsorbent, the refrigerant adsorbent filling container surface and the refrigerant adsorbent per unit volume of the refrigerant adsorbent , While increasing the mutual contact area, that is, the heat transfer area, the stack thickness of the refrigerant adsorbent, that is, one contact surface between the refrigerant adsorbent and the filling container surface, and the contact surface adjacent to the contact surface By reducing the distance between them, the heat transfer resistance in the refrigerant adsorbent can be reduced, the average temperature difference between the refrigerant adsorbent and the filling container surface can be reduced, and by heating or cooling the filling container, The refrigerant adsorbent can be heated or cooled uniformly to a desired temperature with less heating or cooling energy.

For this reason, as the aspect of the cross section of the refrigerant adsorbent-filled container of the present invention, an outer peripheral member for partitioning the inside of the container from the outside with airtightness and maintaining strength as the container is provided. A gas passage also serving as a refrigerant adsorbing material storage space is formed, a central member is disposed in the central portion of the filling container as a means for increasing the surface area of the filling container, and between the outer peripheral member and the central member. A plurality of fins were provided, and the outer peripheral member and the central member were connected by these fins.
By configuring the cross section of the filling container in this way, the contact area between the filling container surface and the refrigerant adsorbent, that is, the heat transfer area can be dramatically increased as compared with a conventional filling container having no central member or fins. And the thickness of the refrigerant adsorbent stack can also be dramatically reduced.

  The overall shape of the refrigerant adsorbent filling container having such a cross-sectional shape has, for example, a cylindrical container constituent member having the cross-sectional shape as a filling container body, and openings at both ends of the cylindrical filling container body. And a refrigerant adsorbent after filling the refrigerant adsorbent storage space also serving as a gas passage formed in the main body of the filling container with a disc-shaped cover having a gas inlet or outlet. You may make it equip between the both opening parts of a filling container main body, and a disk-shaped cover with the metal mesh which has a mesh of a suitable magnitude | size for hold | maintaining so that it may not drop. Incidentally, in this case, in order to guide the gas from the inlet to the gas passage in the filling container main body, or to guide the gas from the gas passage of the filling container main body to the outlet, the inner surface side of the disk-shaped cover is processed into a concave shape. Is preferred. Needless to say, an end plate or a hemispherical body can be used instead of the disc-shaped cover. In the case of the refrigerant adsorbent-filled container as described above, for example, the heater for heating the filling container is inserted into a heater insertion hole formed in the filling container, or the surface of the filling container is required. There is no particular hindrance to the contact with the position, and similarly, heat can be released from the surface of the filled container, for example, by contacting with natural air convection of ambient air or forced air flow by a fan or the like. Since there is no hindrance, the filling container can be heated and cooled from the outside of the outer peripheral member of the refrigerant adsorbent filling container.

  In addition to the above-described evaluation from the aspect of heat transfer, the present invention also provides an excellent effect in terms of the strength of the refrigerant adsorbent-filled container. That is, as described above, in order to cause the refrigerant adsorbent to adsorb or desorb the refrigerant, it is necessary to heat or cool the refrigerant adsorbent itself, and for this purpose, the refrigerant adsorbent filling container is heated or cooled. In this case, the refrigerant adsorbent that is contained in the filling container and the filling container usually have different coefficients of thermal expansion, and the value of the normal filling container is usually larger. May occur. Here, for example, when the filling container has a rectangular parallelepiped shape, the displacement is not uniform and the thermal stress is not uniform between the corner portion and the plane portion, and an excessively large value may occur locally. As described above, if the cross-sectional shape is circular, the generated thermal stress is not largely biased, and it is easy to avoid the generation of excessive stress and non-uniform strain, and as a result, it is easy to maintain the airtightness of the filling container.

  In addition, the central member and the plate-like fins are formed with point symmetry or line symmetry with respect to the diameter or radius, for example, with respect to a circular center point, thereby maintaining the uniformity of thermal stress and strain generation as described above. it can. Furthermore, in addition to thermal stress, it is easy to equalize stress and strain generated by the pressure difference between the inside and outside of the filled container, and an excessive value can be avoided. Regarding the cross-sectional shape, the outer peripheral member is most preferably circular as described above, and the central member and the plate-like fin are preferably point-symmetric with respect to the center point of the circular shape or line-symmetric with respect to the diameter or radius. . The outer peripheral member may be a polygon, and a regular polygon having many corners is particularly preferable. The overall shape of the refrigerant adsorbent filling container may be a spherical shape or a spheroid shape, but the above shape is preferable in consideration of practicality such as ease of manufacture.

  In addition, the material for the refrigerant adsorbent filled container must be selected so that it has high thermal conductivity and does not cause a chemical reaction with the refrigerant adsorbent or refrigerant contained therein. Is preferably made of cast aluminum. Thereby, improvement of fin efficiency, weight reduction, and realization of an effective fin shape and arrangement become easy, and since it can be manufactured integrally, it is economically advantageous. However, for example, the refrigeration apparatus using fluorocarbon as a refrigerant, since the use of aluminum alloy containing magnesium exceeding 2% is prohibited for fluorocarbon in the refrigeration safety regulation related illustration standard of the High Pressure Gas Safety Law, for example. In the case of using for the above, it is preferable to comply with this without being limited to the refrigerant corresponding to the high-pressure gas. This is because the fluorocarbon refrigerant is corrosive to an aluminum alloy containing magnesium, and is most preferably free of magnesium, and is preferably aluminum having a magnesium content of at most 2%. Because.

Moreover, this invention can use the said outer peripheral member of the said refrigerant | coolant adsorbent filling container as a refrigerant | coolant adsorbent filling container further provided with the plate-shaped fin outside.
After the refrigerant adsorbent is heated and desorbed, it is necessary to cool the refrigerant adsorbent again in order to restore the refrigerant adsorption capacity. For this reason, the outside of the refrigerant adsorbent filling container is used, for example, a cooling fan or the like. It is preferable to apply a forced flow of the surrounding air and cool it quickly. Although a method of spraying fine water droplets directly on the outside of the filling container and using the latent heat of vaporization of water is also conceivable, it is preferable not to use moisture because it causes corrosion of the material, short-circuiting of electric wiring, and the like. In addition, there may be a method of cooling by flowing a cooling medium such as water by providing a flow path on the outer periphery or inside of the container. For example, when the container is heated, the cooling medium is also heated at the same time. Not only is it necessary to consume the extra energy required, but also when the heating temperature exceeds 100 ° C., for example, boiling occurs in water, and it is assumed that a situation where water cannot be passed through the flow path during cooling is not preferable. Since a larger surface area is advantageous for cooling from the outer surface of the filling container, it is preferable to provide fins on the outer peripheral member of the filling container, but the thermal effect, ease of manufacture, and mechanical strength In view of the above, the shape preferably includes a plate-like fin.

The heat possessed by the refrigerant adsorbent in the filled container is not only radiated to the surrounding environment directly via the outer peripheral member, but especially the heat from the refrigerant adsorbent near the center of the filled container is absorbed by the refrigerant. Since heat is transferred from the material to the outer peripheral member via the central member and the plate-like fins to be dissipated, it can be said that the central member and the plate-like fins form a heat dissipation path. By providing this, both inside and outside of the filling container can be effectively cooled.
Incidentally, at the time of heating the refrigerant adsorbent, for example, by providing a heater or the like so as to contact the outer surface of the outer peripheral member including the external plate-like fins and heating the outer peripheral member, the central member and the central member Since the plate-like fins connecting the outer peripheral member can also be heated from the inside of the container such as the center of the filling container, it can be said that the center member and the plate-like fins form a heat supply path. Further, when heating, for example, a rod-shaped heater is used to heat the heating element such as a heater directly to not only the outer peripheral member but also the central member and the plate-like fins connecting the central member and the outer peripheral member. If the filling container is configured so as to be inserted into the hole that reaches the central member via the fins, more preferable heating can be realized.

Further, according to the present invention, the refrigerant adsorbent filling container is integrally formed with at least two of the center member, the outer peripheral member, the plate-like fin connecting the two members, and the plate-like fin outside the outer peripheral member. Can do.
The central member, the outer peripheral member, the plate-like fin connecting the central member and the outer peripheral member, and further, when the outer peripheral member is provided with a plate-like fin, if the plate-like fin is integrally formed, for example, made of aluminum casting, the above The heat transfer resistance can be suppressed lower than when they are configured separately between members, and the refrigerant adsorbent can be effectively heated and cooled. Furthermore, the manufacturing cost can be reduced and the strength as a filling container can be improved.
Needless to say, all of the above members need not be integrally formed. For example, a central member and a plate-like fin connecting the central member and the outer peripheral member are integrally formed, and the outer peripheral member is brazed. However, it is most preferable that all of the members are integrally formed from at least a heat transfer surface.

Further, according to the present invention, the refrigerant adsorbent filling container includes a plate-like fin extending from one side of the central member or the outer peripheral member toward the other side, and the fin is connected to any one of the other fins. They can be formed parallel to each other.
As in the present invention, the cross-sectional shape of the refrigerant adsorbent filling container is typically provided with a circular outer peripheral member, a central member and a plurality of plate-like fins that connect them, and the outer peripheral member side and the central member. A plate-like fin extending from at least one of the sides toward the other, and when the plate-like fin is formed in parallel with any other plate-like fin, between the plate-like fins facing each other, The sandwiched refrigerant adsorbent is heated uniformly from both fin surfaces when heated, and can be dissipated uniformly to both fin surfaces during cooling, so the refrigerant adsorbent temperature inside the refrigerant adsorbent filling container Can be changed uniformly.

The plate-like fins do not necessarily have to be completely parallel to each other. For example, as long as they face each other even if they are in an oblique positional relationship, they contribute to heat supply and heat dissipation as described above. This can contribute to uniform temperature throughout the adsorbent. Therefore, the term “parallel” in the present invention includes not only perfect parallelism but also the meaning of “parallel” to the extent that a substantial effect on the above-described heat supply and heat dissipation is recognized based on empirical rules.
By the way, although it is easy to densely arrange a plurality of fins in a heat radiation container composed of flat plate portions facing in parallel, the refrigerant adsorbent is, for example, a powdery solid, a granular solid, a fibrous solid, Since it is a gel or the like and is generally a substance having poor fluidity, it is difficult to fill the heat radiating container as described above. However, if the refrigerant filling container is configured as in the present invention, sufficient and effective heat transfer fins are provided, and for example, the refrigerant adsorbing material can be easily filled from the open end of the cylindrical refrigerant filling container.

The present invention also provides a non-condensable gas extracted from the turbo refrigerator together with the refrigerant gas and then separated from the refrigerant gas through the refrigerant adsorbent-filled container filled with the refrigerant adsorbent and then into the atmosphere. In the bleed air recovery apparatus for a turbo chiller configured to be discharged at the same time, the refrigerant adsorbent filling container of the present invention described above is used as the refrigerant adsorbent filling container.
A turbo refrigerator using a so-called low-pressure refrigerant is usually provided with a bleed gas recovery device in order to discharge non-condensable gas such as air leaked into the refrigerator to the outside of the apparatus. With this extraction air recovery device, the non-condensable gas in the refrigerator is extracted together with the refrigerant gas, and the extracted gas is separated into, for example, refrigerant gas and non-condensable gas by cooling, and the separated refrigerant is recovered in the refrigerator. At the same time, non-condensable gas is discharged outside the machine. Here, when gas separation is performed by cooling as described above, it is normal that refrigerant gas is also included in the non-condensable gas at a partial pressure corresponding to the saturation pressure of the temperature at the time of cooling. Yes, the non-condensable gas at this point is in the state of a mixed gas. Therefore, after performing the second stage gas separation and removing most of the refrigerant gas from the mixed gas, almost completely non-condensable gas is removed outside the aircraft, that is, usually in the atmosphere, with little accompanying refrigerant gas. It is especially required as an environmental measure. Note that the refrigerant gas separated and removed from the mixed gas in the second stage is also usually recovered by the refrigerator.

  In order to separate the second stage refrigerant gas from the non-condensable gas, the refrigerant gas is adsorbed from the mixed gas by passing the mixed gas through a refrigerant adsorbent filling container filled with a refrigerant adsorbent. If the filling container according to the present invention is used as a refrigerant adsorbent filling container in a bleed air recovery apparatus configured to remove only the remaining non-condensable gas outside the apparatus, the refrigerant adsorbent is necessary and sufficient. Since the heating and cooling can be performed quickly, the refrigerant can be quickly and sufficiently desorbed from the refrigerant adsorbing material that has adsorbed the refrigerant, and the refrigerant adsorbing material can be suitably regenerated. An excellent extraction / recovery device can be realized that is economical without requiring time and effort for replacement, and that can significantly reduce the release of refrigerant to the outside of the apparatus.

Further, according to the present invention, in the turbo refrigerator equipped with the extraction recovery device, the extraction recovery device of the present invention described above is provided as the extraction recovery device.
In the turbo chiller equipped with the extraction recovery device, even if non-condensable gas such as air leaks into the apparatus, the non-condensable gas is removed by extraction with the extraction recovery device, and the extraction is performed together with the non-condensation gas. Since the refrigerant gas thus obtained can be recovered by the refrigerator, the refrigerant filling amount is extremely small. In other words, even if non-condensable gas leaks, it is possible to remove only the non-condensable gas from the inside of the machine, and the decrease in the amount of refrigerant is extremely small, and virtually no refrigerant is discharged into the atmosphere. An excellent turbo refrigerator can be provided.

Furthermore, the present invention provides a refrigerant adsorbent-filled container according to the present invention as a refrigerant recovery device for adsorbing and recovering only refrigerant gas from refrigerant gas containing non-condensable gas and discharging the non-condensable gas into the atmosphere. Filled with refrigerant adsorbent.
In the refrigerant recovery device that recovers the refrigerant from the refrigerator, non-condensable gas such as air that leaks into the refrigerator or leaks during the refrigerant recovery operation is also temporarily recovered in the refrigerant recovery device. May end up. In this case, in order to discharge the non-condensable gas once taken into the refrigerant recovery apparatus to the outside of the refrigerant recovery apparatus, all the refrigerant gases including the non-condensable gas taken from the refrigerator are cooled, for example, by cooling the refrigerant gas. The refrigerant is separated into non-condensable gas, and only the separated refrigerant is transferred and stored in the refrigerant-filled container, and the non-condensable gas is discharged out of the refrigerant recovery device. Here, for example, when gas separation is performed by cooling as described above, refrigerant gas is usually included in the non-condensable gas at a partial pressure corresponding to the saturation pressure of the temperature at the time of cooling. Yes, the non-condensable gas at this point is in the state of a mixed gas. Therefore, after the second stage gas separation is performed and most of the refrigerant gas is further removed from the mixed gas, almost completely non-condensable gas is removed from the refrigerant recovery apparatus, that is, usually without any accompanying refrigerant gas. Is required to be released into the atmosphere as an environmental measure.

  In order to separate the second stage refrigerant gas from the non-condensable gas, the refrigerant gas is adsorbed from the mixed gas by passing the mixed gas through a refrigerant adsorbent filling container filled with a refrigerant adsorbent. If the filling container according to the present invention is used as the refrigerant adsorbent filling container in the refrigerant recovery apparatus configured to discharge only the remaining non-condensable gas to the outside of the refrigerant recovery apparatus, the refrigerant adsorbent is necessary. Sufficient heating and cooling can be performed quickly, so that the refrigerant can be quickly and sufficiently desorbed from the refrigerant adsorbing material that has adsorbed the refrigerant, and the refrigerant adsorbing material can be suitably regenerated, so that the same refrigerant adsorbing material can be used repeatedly. An excellent refrigerant recovery apparatus can be realized that is economical without requiring troubles such as replacement and that can significantly reduce the release of the refrigerant to the outside of the refrigerant recovery apparatus. Further, the application range of the refrigerant recovery apparatus according to the present invention is not limited to the turbo refrigerator, but can naturally be applied to other vapor compression refrigerators.

Hereinafter, the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional configuration diagram showing an example of a typical refrigerant adsorbent filling container according to the present invention. In FIG. 1, a container is formed by a wall surface 1 which is a cylindrical outer peripheral member, and an internal space is formed by integrally formed internal fins 2 to 4 while forming a space 6 in which a refrigerant adsorbing material and the like can be accommodated. When the distance is shortened and the heat transfer area is expanded, the temperature unevenness and the time required for heat transfer can be reduced when heating and cooling the refrigerant adsorbent and the like stored in the internal storage space 6.
The typical particle size of the refrigerant adsorbent powder, granule or gel is about 2 mesh to 200 mesh (about 0.1 mm to about 10 mm), and a chip of about several mm square can be used for the fibrous solid. At this time, the distance between the internal fins 2 to 4 needs to be larger than the particle diameter of the refrigerant adsorbent or the like to be filled therein, and is 5 times or less, preferably 2 to 5 times the particle diameter of the refrigerant adsorbent or the like. Can be doubled. When the distance between the fins is narrower than this, it is difficult to densely fill the inside with particles such as the refrigerant adsorbent, and the filling rate of the refrigerant adsorbent etc. decreases, so the refrigerant adsorbent is relatively This is because it is necessary to enlarge the filling container. On the other hand, if the filling container is wider than this, the ratio of the particles not in contact with the fins occupies the majority, so that the heat transfer promoting effect is reduced.

  The internal fin 2 has an effect of improving the maintenance of the overall shape and the uniform heat transfer in cooperation between the central member 10 and the outer peripheral member 1, and the internal fin 3 provides the uniform heat transfer of the outer peripheral portion. The internal fins 4 have the effect of increasing the uniform heat transfer at the center. By arranging the surface of the internal fin 3, the surface of the internal fin 4 and the surface of the internal fin 2 to be parallel to each other, the heat transfer distance of each part such as the refrigerant adsorbent filled in the internal storage space 6 can be made uniform and promptly Moreover, heating and cooling can be performed uniformly (depending on the size, the temperature difference in the refrigerant adsorbent is, for example, about 10 ° C. or less). At this time, the number of the radial fins 2 is preferably 8 to 12. Although not shown in the drawing, the number of the internal fins 3 or 4 is not necessarily the same as that of the radial fins 2, and an appropriate heat transfer is possible depending on the relative relationship with the particle diameter filled in the internal storage space 6. For example, a plurality of fins 3 or fins 4 can be selected within a compartment of the refrigerant adsorbent storage space composed of a pair of fins 2, the central member 10, and the outer peripheral member 1. Can be arranged alternately in parallel so that the distance between them becomes an appropriate heat transfer distance. However, in the case of manufacturing the refrigerant adsorbent filled container by casting, it is preferable that the shape and size of the refrigerant adsorbent storage space 6 and the fins in each section are the same in consideration of ease of manufacture. By doing so, the core of the casting can be manufactured in the same shape, so that the manufacturing cost can be reduced.

For example, when a cartridge type heater or the like is used as the heating means, it is possible to easily attach the fin 2 by providing a thick portion in advance and providing the attachment hole 8 therein. Although not shown in the drawing, a method of inserting the heater into the center of the center member 10 from the direction perpendicular to the paper surface may be used. It is necessary to be careful because it is necessary to hold. In addition, a method of sticking a sheet-like heater to the outer peripheral surface of the container wall surface 1 may be used, but in this case, care must be taken that the cooling time becomes long because the heater itself can become a thermal resistance during cooling.
As a material for the refrigerant adsorbent-filled container, it is preferable that the heat conductivity is as high as possible. For example, by using an aluminum alloy casting, the temperature unevenness of the container itself is kept to a minimum within several degrees Celsius depending on the size. Can do.
Further, by providing the fin 5 on the outer peripheral member 1 on the outer surface of the container, it is possible to enhance the effect of quickly radiating heat to the outside during cooling.
In addition, a cover is installed in both ends using the screw hole 9 provided in the overhang | projection part 7 of the flange connected to the front and rear both ends of the external fin 5. The shape of the cover will be described with reference to FIG.

2-4 is a cross-sectional block diagram which shows another example of the cross section of the refrigerant | coolant adsorbent filling container concerning this invention.
FIG. 2 shows an example in which the internal fins 2 are arranged radially, and the number of radial fins is preferably 12 to 16 or less. If the number of fins is smaller than this, the heat transfer promoting effect by the fins is relatively reduced, and it is difficult to increase the capacity while maintaining an appropriate heat transfer distance.
On the other hand, FIG. 3 shows an example (unfavorable example) in which the number of fins in FIG. 2 is relatively increased in order to increase the capacity while maintaining an appropriate heat transfer distance. As shown in FIG. 3, when the number of fins is extremely increased in order to shorten the distance of the internal space, the wasteful volume of the central portion is relatively increased, and the effective space for filling the adsorbent is decreased. Therefore, it is not preferable.

  FIG. 4 shows that the fin 3 is further provided from the inner surface of the outer peripheral member 1 toward the center in the space constituted by the radial fins 2, thereby increasing the capacity, reducing the internal space distance, and the heat transfer area compared to FIG. It is an example which aimed at expansion. In particular, when heating from the outer peripheral surface of the container and dissipating heat to the outer periphery, heating and cooling can be quickly performed by placing the internal fins on the outer peripheral side in this manner. At this time, the number of the radial fins 2 is preferably 8 to 16. When the capacity is further increased while maintaining an appropriate heat transfer distance, it is necessary to further increase the number of fins, and the same problem as in FIG. 3 arises. In the configuration, that is, the configuration using only the fins 2 and 3, it becomes difficult to cope with the problem. Therefore, an arrangement in which fins 4 as shown in FIG. 1 are further added is preferable. As can be seen from the above, the optimum arrangement of the internal fins can be changed depending on the particle diameter and the filling amount of the refrigerant adsorbent.

  FIG. 5 is a longitudinal sectional configuration diagram showing an example of the overall shape of the refrigerant adsorbent filling container. When the refrigerant adsorbent or the like is filled inside and used as a sealed container, first, the refrigerant adsorbent-filled container main body 18 constituting the cylindrical container having the cross-sectional shape as shown in FIG. A mesh of an appropriate size for holding the refrigerant adsorbent so as not to drop off so as to cover the opening at one end of the medium (of course, it is necessary to be smaller than the mesh diameter of the refrigerant adsorbent particles themselves) The metal mesh 13 is attached together with a reinforcing plate and / or a metal mesh that can maintain the mass of the adsorbent while maintaining its flat surface, and further supports the metal mesh 13 while covering and storing it, and a gas passage is formed in a concave shape at the center of the inner surface. A disk-shaped cover 12 having a gas inlet or outlet communicating with the gas is installed. A sealing material 14 such as an O-ring is installed on the flange surface for airtightness. Thereby, after filling the refrigerant adsorbent into the refrigerant adsorbent storage space that also serves as the gas passage formed in the filling container main body that is open only on one side, the other end also has the metal mesh 13, the sealing material 14, Cover 11 is installed and sealed.

  In this way, the cover 12 and the cover 11 are each provided with the inlet 19 and the outlet 20, and the refrigerant adsorbent in which the non-condensable gas containing the refrigerant gas introduced from the inlet 19 is filled in the refrigerant adsorbent filling container main body 18. The refrigerant gas can be adsorbed by the refrigerant adsorbent by passing the entire amount through, and only the non-condensable gas containing almost no remaining refrigerant gas can be discharged from the outlet 20. Further, a cartridge heater having a predetermined heat generation capacity can be attached to the refrigerant adsorbent filling container body 18 using the heater attachment hole 17, and a temperature sensor such as a thermistor can be attached to the temperature sensor attachment hole 16. Therefore, the temperature of the refrigerant adsorbed by the refrigerant adsorbent can be increased uniformly and quickly to a temperature suitable for desorption and regeneration, and the desorbed refrigerant gas can be regenerated and recovered by holding for a predetermined time. Moreover, although the adsorptivity of the refrigerant adsorbent is restored by cooling again, the inside of the refrigerant adsorbent filled container can be uniformly and quickly cooled at this time as well. Since the lower cover 12 is self-supporting by attaching the legs 15, it can be installed and fixed at a predetermined position. In addition, the cooling time can be shortened by installing the cooling fan 62 outside (here, the lower part) and operating only during cooling. Further, by installing the duct 61 on the outer periphery, it is possible to shorten the heating time and the cooling time and reduce the input energy.

FIG. 6 is a schematic configuration diagram of a turbo chiller having an extraction recovery device using a refrigerant adsorbent filling container according to the present invention. The details of the extraction recovery device are as shown in FIG. FIG. 7 is an overall configuration diagram showing an example of a bleed air recovery device according to the present invention. Symbols a, b, c, d, and ho described in FIGS. 6 and 7 indicate that the portions to which the same symbol is attached are connected to each other.
A description will be given including the opening and closing of related valves from the mutual connection portion between the turbo refrigerator and the extraction device.

  In FIG. 7, the purge condenser 31 of the extraction recovery device 50 is cooled by using a part of the refrigerant constituting the refrigerant cycle of the turbo chiller. That is, a part of the liquid refrigerant is taken out from the condenser 41 of the turbo chiller using a pipe, and the pipe is routed inside the evaporator 42 to supercool the liquid refrigerant, and then the refrigerant filter 44 is installed by the refrigerant pump 43. Via, it is pumped toward the cooling coil 32 which is a heat exchanger installed in the purge condenser 31 (this is the second path). An orifice 45 is disposed at the inlet of the purge condenser 31 of the cooling coil 32 that is a heat exchanger, and the downstream side of the cooling coil 32 is connected to the evaporator of the refrigerator. It is cooled by the latent heat of vaporization of the liquid refrigerant to a low temperature that is almost equal to the evaporator of the refrigerator. After cooling the purge condenser, the refrigerant returns to the evaporator 42 (this is the second path). Since the purge condenser cooling refrigerant always flows during the operation of the refrigerator, the pressure of the purge condenser 31 is thereby kept lower than the pressure of the condenser 41.

Due to the pressure difference between the condenser 41 and the purge condenser 31, refrigerant gas containing non-condensable gas flows from the condenser 41 through the connecting pipe 37 into the purge condenser 31 via the orifice 39 (in the path a). is there). In the condenser chamber 31a, the refrigerant gas condenses and then flows into the float valve chamber 31b. When a certain amount or more of liquid refrigerant accumulates in the float valve chamber 31b, the float valve 33 is opened, and the refrigerant returns to the refrigerator (evaporator 42) (this is the path of E). On the other hand, the non-condensable gas stays in the purge condenser chamber 31 and gradually accumulates.
A pressure guiding pipe for detecting the pressure difference between the pressure of the condenser 41 and the pressure of the purge condenser 31 is taken out of the condenser 41 and connected to the differential pressure detector 34 (this is a path C). .

Next, the configuration, operation and effect of the bleed air recovery apparatus according to the present invention will be described in order.
As described above, during the operation of the centrifugal chiller, the refrigerant gas containing the non-condensable gas flows from the condenser 41 through the connection pipe 37 and the orifice 39 into the purge condenser 31, and the refrigerant gas in the refrigerant gas is contained in the condenser chamber 31 a. Then, it is cooled and liquefied by the cooling coil 32 and returns to the evaporator 42 via the float valve chamber 31b. On the other hand, the non-condensable gas gradually accumulates in the capacitor chamber 31a, and the internal pressure of the purge capacitor gradually increases.
Next, the operation of discharging non-condensable gas into the atmosphere will be described.
When the non-condensable gas is accumulated in the condenser chamber 31a of the purge condenser 31 and the pressure difference between the condenser 41 and the purge condenser 31 of the refrigerator becomes equal to or less than a predetermined value, the differential pressure detector 34 is activated and the control unit A signal is transmitted to 40. Thereafter, the control unit 40 opens the electromagnetic valve 51. Thereby, the non-condensable gas accumulated in the purge condenser 31 is introduced into the adsorption tank 63 together with the refrigerant gas via the connection pipe 54, the orifice 57 disposed in the middle thereof, and the electromagnetic valve 51. The adsorption tank 63 is filled with a refrigerant adsorbent 60, and most of the refrigerant gas is adsorbed by the adsorbent 60.

When the non-condensable gas including the refrigerant gas moves from the purge condenser 31 to the adsorption tank 63 in this way, the internal pressure of the purge condenser 31 decreases, so that the pressure difference with the condenser 41 of the refrigerator exceeds the predetermined value again. Therefore, the differential pressure detector 34 is cut off. As a result, the electromagnetic valve 51 is closed, and the discharge of the non-condensable gas accumulated in the purge condenser 31 is completed. By the way, when the differential pressure detector 34 is activated and the electromagnetic valve 51 is opened, the non-condensable gas containing the refrigerant gas is introduced into the adsorption tank 63 filled with the refrigerant adsorbent 60, and then the refrigerant gas becomes the refrigerant. The time required to complete the discharge of the non-condensable gas accumulated in the purge condenser 31 after the differential pressure detector 34 is cut off again by being adsorbed by the adsorbent 60 and the electromagnetic valve 51 is closed (hereinafter referred to as “adsorption time”). It has been confirmed that approximately 50 seconds to 70 seconds is sufficient although it depends on the size of the purge condenser 31 and the adsorption tank 63. Thus, for example, by providing such the suction completion confirmation timer is set a value equal to or greater than the adsorption time in advance in control unit 40, because it detects the completion of the adsorbing operation, still the differential pressure the adsorption time has elapsed If the detector 34 is not cut off, that is, if the pressure difference between the condenser 41 and the purge condenser 31 of the refrigerator remains below the predetermined value, a considerable amount of non-condensable gas in the adsorption tank 63. Means that the purge pump 36 is activated and the solenoid valve 52 is opened. In this way, as a result of the refrigerant gas being adsorbed by the adsorbent, almost only non-condensable gas is sucked and discharged by the purge pump 36 and is discharged to the atmosphere via the electromagnetic valve 52.

  As described above, when the pressure difference between the condenser 41 and the purge condenser 31 becomes a predetermined value or less, the noncondensable gas including the refrigerant gas is transferred from the purge condenser 31 to the adsorption tank 63. After the transfer, the differential pressure again exceeds a predetermined value, and the solenoid valve 51 is closed. Therefore, accumulation of non-condensable gas in the purge condenser 31 starts again. Thus, by detecting the differential pressure between the condenser 41 and the purge condenser 31, the transfer of the non-condensable gas including the refrigerant gas from the purge condenser 31 to the adsorption tank 63 is repeated. If this is repeated a plurality of times, the amount of non-condensable gas in the adsorption tank 63 will eventually increase, so that the value of the differential pressure will not recover to a value exceeding a predetermined value within the preset adsorption time. At this time, since a considerable amount of non-condensable gas has accumulated in the adsorption tank 63, the purge pump 36 is operated to open the electromagnetic valve 52 and discharge the non-condensable gas to the outside.

  Incidentally, although related to the refrigerant desorption described below, the refrigerant adsorption capacity of the refrigerant adsorbent 60 in the adsorption tank 63, that is, the adsorbable refrigerant mass, is the refrigerant mass discharged from the purge condenser 31 at one time. On the other hand, it is desirable to make it large enough. That is, since the required filling amount of the refrigerant adsorbent is determined, the size of the refrigerant adsorbent filling container needs to be larger than this. The reason is that, for example, when the adsorption capacity of the refrigerant adsorbent 60 is too small, the refrigerant adsorbed in the adsorption tank 63 immediately reaches saturation (that is, the adsorption limit amount), and non-condensable gas accumulation in the adsorption tank 63 occurs. Even if the amount is small, the pressure difference between the condenser 41 and the purge condenser 31 does not recover within a predetermined adsorption time until it exceeds a predetermined value, as if a considerable amount of non-condensable gas is present. A phenomenon similar to that accumulated in the adsorption tank 63 appears. In other words, the effect of installing the adsorption tank 63 cannot be sufficiently exhibited.

  When the mass of the refrigerant gas discharged together with the non-condensable gas toward the adsorption tank 63 per opening operation of the solenoid valve 51 from the purge capacitor and the refrigerant adsorption capacity of the adsorption tank 63 are in an appropriate relationship, For example, when the maximum possible refrigerant adsorption mass of the refrigerant adsorbent 60 is more than several times the refrigerant gas mass discharged together with the non-condensable gas per opening operation of the solenoid valve 51 from the purge capacitor, A sufficient amount of non-condensable gas is accumulated in the adsorption tank 63 before the refrigerant adsorbent 60 is saturated with the refrigerant, and the non-condensable gas discharge step to the outside is suitably performed. While such a non-condensable gas discharge step is performed a plurality of times, the refrigerant adsorbent 60 will eventually be saturated with the adsorbed refrigerant, so that it is necessary to perform a refrigerant desorption step.

Next, the refrigerant desorption operation from the refrigerant adsorbent 60 will be described.
Since the refrigerant adsorption capacity of the refrigerant adsorbent 60 is recovered by desorbing the adsorbed refrigerant, the refrigerant desorption process (refrigerant adsorbent regeneration process) is indispensable for reusing the refrigerant adsorbent 60. Since the extraction operation and the non-condensable gas discharge operation cannot be performed at the same time during the refrigerant desorption process, it is necessary to complete them as quickly as possible. In this desorption process, the control unit 40 issues an operation command to the heater 58 and the purge pump 36 and also issues an open signal for the electromagnetic valve 53. As a result, the refrigerant adsorbent 60 is heated by the heater 58 to a temperature level suitable for desorption, and the refrigerant gas desorbed by the purge pump 36 is sucked and exposed to low pressure conditions. The refrigerant is easily desorbed in terms of pressure, and the desorption of the refrigerant from the refrigerant adsorbent 60 is promoted. In other words, the regeneration of the refrigerant adsorbent proceeds. At this time, by using the refrigerant adsorbent filled container according to the present invention, it becomes possible to perform heating uniformly and promptly to the inside, so that not only the time for stopping the extraction operation can be minimized, but also the charging required for heating. Energy can be minimized, and the environmental load can be kept low.

When activated carbon is used as the refrigerant adsorbent 60, it is preferable to control the temperature of the refrigerant adsorbent 60 at the time of desorption to, for example, about 120 to 130 ° C., and it is necessary to heat it quickly and uniformly. By using the refrigerant adsorbent-filled container according to the present invention, it is possible to heat the inside uniformly and quickly, so that it is easy to effectively realize the desorption of the refrigerant. Further, since the thermostat 59 capable of detecting or controlling the temperature of the refrigerant adsorbent 60 can be easily installed, the temperature level of the refrigerant adsorbent 60 can be easily reached or maintained at a desired temperature level. In addition, since it is possible to install a temperature detector such as a thermocouple, a resistance temperature detector, or a thermistor instead of the thermostat, temperature control can be performed in combination with a controller such as a temperature controller.
By the way, the refrigerant gas desorbed from the refrigerant adsorbent 60 and sucked and discharged by the purge pump 36 is introduced into the purge capacitor 31 via the connection pipe 54 and the electromagnetic valve 53. As described above, since the condenser chamber 31a of the purge condenser 31 is cooled by the cooling coil 32, the refrigerant gas is condensed and liquefied, and returns to the evaporator 42 of the refrigerator via the float valve chamber 31b.

Next, the cooling operation of the refrigerant adsorbent 60 will be described.
In order to desorb the adsorbed refrigerant, the temperature of the refrigerant adsorbent 60 is raised by the heater 58 as described above. In order to regain the refrigerant adsorption capacity, the temperature of the refrigerant adsorbent 60 is set to the ambient temperature of the turbo chiller. It is necessary to cool to the extent. For this reason, the following operation is required. In this cooling process, the control unit 40 issues a start command to the fan 62. Since the refrigerant adsorbing material 60 is housed inside the adsorbing tank 63, a forced air flow is generated in the vicinity of the adsorbing tank 63 by the fan 62 so that the temperature of the refrigerant adsorbing material 60 is quickly reduced. In order for the forced air flow to flow in the vicinity of the surface of the adsorption tank 63 effectively for cooling, for example, a duct 61 is preferably provided around the adsorption tank 63.

Also in this case, by using the refrigerant adsorbent filling container according to the present invention, it becomes possible to uniformly and quickly cool the inside of the filling container, so that the time for stopping the extraction operation can be minimized. In addition, the input energy required for cooling can be minimized, and the environmental load can be kept low. Thus, the refrigerant adsorbing material 60 can regain the refrigerant adsorbing capacity (regenerated).
As described above, according to the present invention, the amount of refrigerant that leaks into the atmosphere accompanying the non-condensable gas discharged into the atmosphere from the extraction device can be reduced to the limit using the refrigerant adsorbent, and the refrigerant adsorbent is It is possible to provide a bleed air recovery device that can be regenerated and reused promptly until the sufficient refrigerant adsorption capacity is recovered, and can regenerate the refrigerant adsorbent and collect the refrigerant and return it to the refrigerator.
In addition, if a turbo chiller equipped with a bleed air recovery device using the refrigerant adsorbent filling container of the present invention is used, a cooling device or a refrigeration device with minimal refrigerant wear and improved environmental load is realized. be able to.

FIG. 8 is a diagram showing the connection status of the refrigerant recovery apparatus using the refrigerant adsorbent filling container according to the present invention, the compression refrigerator, and the refrigerant recovery container. FIG. 9 shows the details of the refrigerant recovery apparatus. FIG. 9 is an overall configuration diagram illustrating an example of a refrigerant recovery apparatus including the refrigerant adsorbent filling container according to the present invention. 8 and FIG. 9 indicates that the parts to which the same symbols are attached are connected to each other. Hereinafter, description will be made including opening and closing of related valves.
A description will be given from the mutual connection between the compression refrigerator, the refrigerant recovery container, and the refrigerant recovery device. The small condenser 71 of the refrigerant recovery device 70 is cooled by using a part of the cooling water that constitutes the heat source of the compression refrigerator. That is, a part of the cooling water is taken out from the cooling water pipe 104 of the condenser 101 of the compression refrigerator using the connecting pipe 82, and the cooling coil 72 which is a heat exchanger installed in the small condenser 71 by the pump 77. It is pumped towards (the path of the filter). The cooling medium introduced into the cooling coil 72 may be the cooling water of the compression refrigerator, general tap water or the like instead of the cooling water of the compression refrigerator, but here the cooling water of the compression refrigerator is used. This will be described using the example used.

Since the downstream side of the cooling coil 72, which is a heat exchanger, is connected again to the cooling water pipe 105 of the condenser 101 of the compression refrigeration machine, the cooling coil 72 has a low temperature that is substantially equal to the cooling water of the refrigeration machine. Until cooled by cooling water. After cooling the small condenser 71, the cooling water returns to the cooling water pipe 105 of the condenser 101 of the compression refrigerator. The cooling water for cooling the small condenser 71 always flows during the operation of the pump 77, so that the temperature of the small condenser 71 is adjusted to the outlet of the small compressor or the vacuum pump 76. Keeps below temperature. In the present invention, the term “small compressor or vacuum pump” means that the suction side functions as a vacuum pump and the discharge side functions as a compressor.
The small compressor or the vacuum pump 76 causes the refrigerant gas containing non-condensable gas to flow from the refrigerator 100 into the small condenser 71 through the connecting pipe 79 (this is the path). In the condenser chamber 71a, the refrigerant gas is condensed and liquefied and then flows into the float valve chamber 71b. When a certain amount or more of liquid refrigerant accumulates in the float valve chamber 71b, the float valve 73 is opened and the refrigerant is recovered in the refrigerant recovery container 106 (this is the path). On the other hand, the non-condensable gas stays in the capacitor chamber 71a, gradually accumulates, and the internal pressure of the small condenser 71 gradually increases.
A pressure guiding pipe for detecting the pressure of the small condenser 71 is taken out from the small condenser 71 and connected to the pressure switch 74.

Next, regarding the present invention, the configuration, operation, effect, and the like will be sequentially described for each operation state of the refrigerant recovery device.
As described above, during the refrigerant recovery operation, the refrigerant gas including the non-condensable gas is pumped to the small condenser 71 by the small compressor or the vacuum pump 76 from the refrigerator 100 via the communication pipe 79, The refrigerant gas is cooled and liquefied by the cooling coil 72 in the condenser chamber 71a, and is recovered in the refrigerant recovery container 106 via the float valve chamber 71b, the float valve 73, and the connection pipe 81. On the other hand, the non-condensable gas gradually accumulates in the condenser chamber 1a, and the internal pressure of the small condenser 1 gradually increases.

Next, the discharge operation of non-condensable gas into the atmosphere will be described.
As a result of the accumulation of non-condensable gas in the condenser chamber 71 a of the small condenser 71, when the pressure of the small condenser 71 exceeds a predetermined value, the pressure switch 74 is activated and a signal is transmitted to the control unit 84. Thereafter, the control unit 84 opens the electromagnetic valve 75. As a result, the non-condensable gas accumulated in the small condenser 71 is introduced into the adsorption tank 63 together with the refrigerant gas via the connection pipe 89, the orifice 90 disposed in the middle thereof, and the electromagnetic valve 75. The adsorption tank 63 is filled with a refrigerant adsorbent 60, and most of the refrigerant gas is adsorbed by the adsorbent 60. As the refrigerant adsorbent 60, for example, activated carbon can be used. Since the refrigerant gas introduced into the adsorption tank 63 is adsorbed by the refrigerant adsorbent 60, the pressure in the adsorption tank 63 is always lower than the pressure in the small condenser 71, and the pressure in the adsorption tank 63 is adsorbed. As the action progresses, it decreases with time and approaches the partial pressure of the non-condensable gas accumulated in the adsorption tank.

  Thus, when the non-condensable gas including the refrigerant gas moves from the small condenser 1 to the adsorption tank 63, the internal pressure of the small condenser 1 decreases, and thus the pressure switch 74 is turned off. As a result, the electromagnetic valve 75 is closed, and the discharge of the non-condensable gas accumulated in the small condenser 71 is completed. By the way, since the completion of the adsorption operation can be detected by providing, for example, an adsorption completion confirmation timer in which a value equal to or greater than the adsorption time is set in advance in the control unit 84, a predetermined adsorption time (small condenser 71 and adsorption tank) can be detected. If the pressure switch 74 still does not turn off after a lapse of approximately 50 seconds to 70 seconds, depending on the size of 63, that is, the pressure of the small condenser 71 remains above the predetermined value. In this case, it means that a considerable amount of non-condensable gas has accumulated in the adsorption tank 63, so the electromagnetic valve 93 is opened. As a result of the refrigerant gas being adsorbed on the adsorbent in this way, almost only non-condensable gas is discharged into the atmosphere via the electromagnetic valve 93, and the discharge amount of the refrigerant is suppressed to a very small amount.

  As described above, when the pressure of the small condenser 71 becomes a predetermined value or more, the non-condensable gas including the refrigerant gas is transferred from the small condenser 71 to the adsorption tank 63. After the transfer, the pressure again falls below a predetermined value, and the solenoid valve 75 is closed. Therefore, accumulation of non-condensable gas in the small condenser 71 starts again. Thus, by detecting the pressure of the small condenser 71, the transfer of the non-condensable gas including the refrigerant gas from the small condenser 71 to the adsorption tank 63 is repeated. If this is repeated a plurality of times, the amount of non-condensable gas in the adsorption tank 63 will eventually increase, so that the pressure value will not recover to a value below a predetermined value within the preset adsorption time. At this time, since a considerable amount of non-condensable gas is accumulated in the adsorption tank 63, the electromagnetic valve 93 is opened to discharge the non-condensable gas to the outside.

  Incidentally, although it relates to the refrigerant desorption described below, the refrigerant adsorption capacity of the refrigerant adsorbent 60 in the adsorption tank 63, that is, the adsorbable refrigerant mass, is the mass of the refrigerant discharged from the small condenser 71 at a time. On the other hand, it is desirable to make it large enough. That is, since the required filling amount of the refrigerant adsorbent is determined from the capacity of the small condenser 71, the size of the refrigerant adsorbent filling container needs to be larger than this. The reason is that, for example, if the adsorption capacity of the refrigerant adsorbent 60 is too small, the refrigerant adsorbed in the adsorption tank 63 immediately reaches saturation (that is, the adsorption limit amount), and the non-condensable gas accumulation amount in the adsorption tank 63 is reached. Even if there is a small amount, the pressure difference between the small condenser 71 and the adsorption tank 63 does not recover within a preset adsorption time until it exceeds a predetermined value, as if a considerable amount of non-condensable gas is adsorbed. A phenomenon similar to that accumulated in the tank 63 appears. In other words, the effect of installing the adsorption tank 63 cannot be sufficiently exhibited. Note that the mass of the refrigerant gas discharged together with the non-condensable gas toward the adsorption tank 63 and the refrigerant adsorption capacity of the adsorption tank 63 per opening operation of the electromagnetic valve 75 from the small condenser 71 are in an appropriate relationship. In this case, for example, the maximum possible refrigerant adsorption mass of the refrigerant adsorbent 60 is more than several times the refrigerant gas mass discharged from the small condenser 71 together with the non-condensable gas per opening operation of the electromagnetic valve 75. In this case, before the refrigerant adsorbent 60 is saturated with the refrigerant, a sufficient amount of non-condensable gas is accumulated in the adsorption tank 63, and the non-condensable gas discharge step to the outside is suitably performed. While such a non-condensable gas discharge step is performed a plurality of times, the refrigerant adsorbent 60 will eventually be saturated with the adsorbed refrigerant, so that it is necessary to perform a refrigerant desorption step.

  Since the heat is generated during the adsorption of the refrigerant, the temperature of the refrigerant adsorbent 60 temporarily increases. Especially when refrigerant recovery is performed due to poor airtightness of the refrigerator, non-condensable gas leaked into the refrigerator is frequently discharged, and the accompanying refrigerant gas is adsorbed in a large amount in a short time. In some cases, the temperature rise is so large that it cannot be ignored. In such a case, since the capacity capable of adsorbing the refrigerant decreases as the temperature of the refrigerant adsorbent 60 rises, cooling is necessary so that the temperature of the refrigerant adsorbent 60 does not rise above the temperature suitable for adsorption. It may become. For this reason, similarly to the case of the cooling step after the desorption regeneration processing step, which will be described later, the following operation is required even during the adsorption in the non-condensable gas discharge step. In this discharge process, the control unit 84 issues a start command to the fan 62. Since the refrigerant adsorbing material 60 is housed inside the adsorbing tank 63, a forced air flow is generated in the vicinity of the adsorbing tank 63 by the fan 62 so that the temperature of the refrigerant adsorbing material 60 is quickly reduced. In order for the forced air flow to flow in the vicinity of the surface of the adsorption tank 63 effectively for cooling, for example, a duct 61 is preferably provided around the adsorption tank 63. The operation of the fan 62 is, for example, detecting the surface temperature of the adsorption tank 63 with a temperature detector or the like instead of the temperature of the refrigerant adsorbent 60, or detecting the temperature by directly embedding the temperature detector in the refrigerant adsorbent 60. However, it may be started at a predetermined temperature or more and continued until the temperature is lower than the predetermined temperature, or it may be stopped at the same time as the discharge operation, the time required for cooling is measured in advance, a timer or the like You may make it stop after continuing driving | running only for the said time using.

Next, the refrigerant desorption operation from the refrigerant adsorbent 60 will be described.
Since the refrigerant adsorption capacity of the refrigerant adsorbent 60 is recovered by desorbing the adsorbed refrigerant, a refrigerant desorption process (refrigerant adsorbent regeneration process) is indispensable for reusing the refrigerant adsorbent 60. Since the refrigerant recovery operation and the non-condensable gas discharge operation cannot be performed simultaneously during the refrigerant desorption process, it is necessary to complete them as quickly as possible. In this desorption process, the switching valve 85 is closed and the switching valve 92 is opened, so that the connection pipe 94 is connected from the adsorption tank 63 to the small condenser 71 via the small compressor or vacuum pump 76. The control unit 84 issues an operation command to the heater 58 and the small compressor or vacuum pump 76. Thereby, the refrigerant adsorbent 60 is heated by the heater 58 to a temperature level suitable for desorption, and the refrigerant gas desorbed by the small compressor or the vacuum pump 76 is sucked and exposed to low pressure conditions. The refrigerant is easily desorbed both in terms of pressure and pressure, and the desorption of the refrigerant from the refrigerant adsorbent 60 is promoted, in other words, the regeneration of the refrigerant adsorbent proceeds. At this time, by using the refrigerant adsorbent-filled container according to the present invention, it is possible to perform heating uniformly and promptly to the inside, so that not only the time for stopping the refrigerant recovery operation can be minimized, but also heating. The input energy required can be minimized and the environmental load can be kept low.

When activated carbon is used as the refrigerant adsorbent 60, it is preferable to control the temperature of the refrigerant adsorbent 60 at the time of desorption to, for example, about 120 to 130 ° C., and it is necessary to heat it quickly and uniformly. By using the refrigerant adsorbent-filled container according to the present invention, it is possible to heat the inside uniformly and quickly, so that it is easy to effectively realize the desorption of the refrigerant. In addition, since the thermostat 59 that can detect or control the temperature of the refrigerant adsorbent 60 can be easily installed, the temperature level of the refrigerant adsorbent 60 can easily reach or be maintained at a desired temperature level. In addition, since a temperature detector such as a thermocouple, a resistance temperature detector, or a thermistor can be installed instead of the thermostat, temperature control can be performed in combination with a controller such as a temperature controller.
By the way, the refrigerant gas desorbed from the refrigerant adsorbent 60 and sucked and discharged by the small compressor or the vacuum pump 76 is introduced into the small condenser 71 via the connection pipe 94. As described above, since the condenser chamber 71a of the small condenser 71 is cooled by the cooling coil 72, the refrigerant gas is condensed and liquefied and is recovered in the refrigerant recovery container 106 via the float valve chamber 71b.

Next, the cooling operation of the refrigerant adsorbent 60 will be described.
In order to desorb the adsorbed refrigerant, the temperature of the refrigerant adsorbent 60 is raised by the heater 58 as described above. In order to regain the refrigerant adsorption capacity, the temperature of the refrigerant adsorbent 60 is changed to the ambient environment of the refrigerant recovery device. It needs to be cooled down to about the temperature. For this reason, the following operation is required. In this cooling process, the control unit 84 issues a start command to the fan 62. Since the refrigerant adsorbing material 60 is housed inside the adsorbing tank 63, a forced air flow is generated in the vicinity of the adsorbing tank 63 by the fan 62 so that the temperature of the refrigerant adsorbing material 60 is quickly reduced. In order for the forced air flow to flow in the vicinity of the surface of the adsorption tank 63 effectively for cooling, for example, a duct 61 is preferably provided around the adsorption tank 63.
Also in this case, by using the refrigerant adsorbent filling container according to the present invention, it becomes possible to cool uniformly and quickly to the inside, so not only the time for stopping the refrigerant recovery operation can be minimized, The input energy required for cooling can be minimized, and the environmental load can be kept low.

  As described above, according to the present invention, the amount of refrigerant that leaks into the atmosphere accompanying the noncondensable gas discharged into the atmosphere from the refrigerant recovery device can be reduced to the limit using the refrigerant adsorbent, and the refrigerant adsorbent is Thus, it is possible to provide a refrigerant recovery apparatus that can be regenerated and reused promptly and before the sufficient refrigerant adsorption capacity is recovered, and that can regenerate the refrigerant adsorbent and recover the refrigerant.

The cross-sectional block diagram which shows an example of the refrigerant | coolant adsorbent filling container concerning this invention. The cross-sectional block diagram which shows another example of the refrigerant | coolant adsorbent filling container concerning this invention. The cross-sectional block diagram which shows another example of the refrigerant | coolant adsorbent filling container concerning this invention. The cross-sectional block diagram which shows another example of the refrigerant | coolant adsorbent filling container concerning this invention. The longitudinal cross-section block diagram which shows an example of the whole shape of the refrigerant | coolant adsorbent filling container concerning this invention. The schematic block diagram which shows an example of the turbo refrigerator which has the extraction collection | recovery apparatus using the refrigerant | coolant adsorbent filling container concerning this invention. The whole block diagram which shows an example of the extraction collection | recovery apparatus concerning this invention. The schematic block diagram which shows an example of the connection condition of the refrigerant | coolant collection | recovery apparatus concerning this invention, a compression type refrigerator, and a refrigerant | coolant collection container. The whole block diagram which shows an example of the refrigerant | coolant collection | recovery apparatus using the refrigerant | coolant adsorbent filling container concerning this invention.

  1: outer peripheral member, 2: internal fin (radial), 3: internal fin (inward), 4: internal fin (outward), 5: external fin, 6: adsorbent storage space, 7: flange portion, 8: Heater mounting hole, 9: Screw hole, 10: Center member, 11: Tank upper cover, 12: Tank lower cover, 13: Separator ((for example, wire mesh)), 14: Sealing material ((for example, O-ring)), 15 : Leg, 16: sensor mounting hole, 17: heater mounting hole, 18: refrigerant adsorbent filling container body, 19: inlet nozzle, 20: outlet nozzle, 31: purge condenser, 31a: condenser chamber, 31b: float valve chamber, 32: Cooling coil, 33: Float valve, 34: Differential pressure switch, 36: Extraction pump, 37: Connection arrangement, 38: Compressor (turbo refrigerator), 39: Orifice, 40: Control unit, 41: Condenser ( 42: evaporator (for turbo refrigerator), 43: refrigerant pump (for turbo refrigerator), 44: refrigerant filter (for turbo refrigerator), 45: orifice, 50: extraction recovery device, 51: Solenoid valve, 52: Solenoid valve, 53: Solenoid valve, 54: Connection piping, 55: Relief valve, 56: Relief valve, 57: Orifice, 58: Heater, 59: Thermostat, 60: Refrigerant adsorbent, 61: Duct, 62: fan motor, 63: adsorption tank (refrigerant adsorbent filling container), 65: non-condensable gas discharge port, 70: refrigerant recovery device, 71: small condenser, 71a: condenser chamber, 71b: float valve chamber, 72: cooling coil, 73: float valve, 74: pressure switch, 75: solenoid valve, 76: compressor or vacuum pump, 77: cooling water pump, 78: relief valve, 79: communication piping, 80 Connection piping, 81: communication piping, 82: communication piping, 83: communication piping, 84: control unit, 85: switching valve, 86: switching valve, 87: switching valve, 88: switching valve, 89: connection piping, 90: Orifice, 91: Solenoid valve, 92: Switching valve, 93: Non-condensable gas discharge port, 94: Connection pipe, 95: Connection pipe, 100: Compression refrigerator, 101: Condenser (of the refrigerator), 102: Evaporation (Refrigerator), 103: compressor (refrigerator), 104: cooling water pipe (refrigerator), 105: cooling water pipe (refrigerator), 106: refrigerant recovery container

Claims (7)

  A refrigerant adsorbent filling container comprising: a central member that forms a central portion; an outer peripheral member that forms an outer peripheral portion; and plate-like fins that interconnect the central member and the outer peripheral member. Has a refrigerant adsorbent storage space formed therein by the central member, the outer peripheral member, and the plate-like fins, and further has a gas inlet and outlet, and the inlet and outlet are the refrigerant adsorbent. Refrigerant adsorption characterized by being connected to each other by a gas passage also serving as a storage space, allowing gas to flow from the inlet toward the outlet, and heating and cooling the filling container from the outside of the outer peripheral member. Material filling container.   The refrigerant adsorbent filling container according to claim 1, wherein the outer peripheral member further includes a plate-like fin on the outside.   The refrigerant adsorbent-filled container according to claim 1 or 2, wherein at least two of the central member, the outer peripheral member, and the plate-like fin are integrally formed.   The center member and the outer peripheral member include plate-like fins extending from one side to the other side, and the fins are formed in parallel to any other fin. The refrigerant | coolant adsorbent filling container as described in 1, 2 or 3.   A non-condensable gas extracted together with the refrigerant gas from the turbo refrigerator is separated from the refrigerant gas and discharged into the atmosphere, and a refrigerant adsorbent filling container filled with a refrigerant adsorbent is provided. It is a bleed air collection | recovery apparatus, Comprising: The said refrigerant | coolant adsorbent filling container is the refrigerant | coolant adsorbent filling container as described in any one of Claims 1-4, The bleed air collection | recovery apparatus for turbo refrigerators characterized by the above-mentioned.   A turbo chiller provided with a bleed air recovery device, wherein the bleed air recovery device is the bleed air recovery device according to claim 5.   The refrigerant | coolant collection apparatus for adsorb | sucking and collect | recovering only refrigerant gas from the refrigerant gas containing non-condensable gas, and discharging | emitting non-condensable gas in air | atmosphere is the refrigerant | coolant described in any one of Claims 1-4 A refrigerant recovery apparatus, wherein an adsorbent filling container is filled with a refrigerant adsorbent.

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