Air turbo-refrigeration unit, method for operating same, and turbo-expander

Abstract

The invention relates to refrigeration technology and can be used in air conditioning systems, refrigerators, etc. An air turbo-refrigeration unit comprises a compressor disposed on the same shaft as a turbo-expander, an electric motor, a two-cavity heat exchanger, a recuperator, a water trap, and a refrigeration chamber with a cooler and a fan. The unit Is equipped with a two-cavity heat exchanger/cooler, and with a second water trap and a third water trap; the compressor is connected by its outlet to the first cavity of the heat exchanger, which is connected to the first cavity of the heat exchanger/cooler, and the first cavity of the heat exchanger/cooler is connected via the second water trap to the first cavity of the recuperator, which communicates with the inlet of the turbo-expander via the first water trap; the turbo-expander is connected by its outlet via the third water trap to the second cavity of the heat exchange r/cooler, which is communicated with the cooler and is communicated via the cooler with the second cavity of the recuperator, which is communicated with the compressor inlet. The invention makes it possible to prevent the formation of ice and frost on the inner cavities of the turbo-expander and of ducts, which, in turn, prevents shut-off of the air turbo-refrigeration unit and increases the refrigeration capacity of the unit.

1 . An air turbo-refrigerating plant which contains a compressor directly coupled to a centrifugal expander, electric motor with the shaft coupled to the shaft of a compressor and a centrifugal expander, a double-cavity heat exchanger, recuperator, moisture separator, refrigerating chamber with a chiller and a blower, with inlet and outlet of the second double-cavity heat exchanger opening to the atmosphere, where the inlet of the latter is via a blower, and the compressor's inlet opens via its valve member to the atmosphere, characterized in that the plant is equipped with a double-cavity heat-exchanging chiller, and the second and third moisture separators, with the compressor's outlet connected to the first cavity of the double-cavity heat exchanger, the said first cavity being connected to the first cavity of the double-cavity heat-exchanging chiller connected via the second moisture separator to the first cavity of the recuperator, with the said cavity connected via the first moisture separator to the inlet of the centrifugal expander, and the latter's outlet is connected via the third moisture separator to the second cavity of the double-cavity heat-exchanging chiller, the said second cavity connected to the chiller, and—through the latter chiller—to the second cavity of the recuperator, the said second cavity being connected to the compressor inlet. 
     
     
         2 . The plant which, according to  claim 1 , is characterized in that it is equipped with an air dryer package, the inlet of which opens to the atmosphere, and the outlet of which—via the second valve member—to the compressor inlet. 
     
     
         3 . The plant which, according to  claim 1  or  2 , is characterized in that the double-cavity heat exchanger is equipped with Peltier thermoelectric modules. 
     
     
         4 . The air turbo-refrigerating plant containing a compressor directly coupled to a centrifugal expander, a double-cavity heat exchanger, recuperator, moisture separator, refrigerating chamber with a chiller and a blower, where inlet and outlet of the second cavity of the double-cavity heat exchanger open to the atmosphere, and the outlet is via the blower, the above plant characterized in that the plant is equipped with a double-cavity heat-exchanging chiller, the second and third moisture separators, the second motor-driven compressor and the second double-cavity heat exchanger, with the compressor outlet connected to the first cavity of the double-cavity heat exchanger, the said first cavity being connected to the first cavity of the double-cavity heat-exchanging chiller, the said first cavity connected via the second moisture separator to the first recuperator cavity connected via the first moisture separator to the centrifugal expander's inlet, while the centrifugal expander's outlet is connected via the third moisture separator to the second cavity of the heat-exchanging chiller, the said second cavity being connected to the chiller and, via the chiller, to the second cavity of the recuperator, the latter second cavity connected to the inlet of the second compressor, while the latter opens with its inlet via the valve member to the atmosphere and with the outlet—via the first cavity of the second double-cavity heat exchanger connected to the compressor inlet, and the inlet and outlet of the second double-cavity heat exchanger open to the atmosphere, with the inlet being connected via the second blower. 
     
     
         5 . The plant, according to  claim 4 , being characterized in that it is equipped with the air dryer package, the latter opening via its inlet to the atmosphere, and connected via it outlet to the inlet of the second compressor. 
     
     
         6 . The plant, according to  claim 4 , being characterized in that it is equipped with the second electric motor, the shaft of which coupled to the shaft of the compressor and centrifugal expander. 
     
     
         7 . The plant, according to any of  claims 4 - 6 , being characterized in that the double-cavity heat exchanger is equipped with Peltier thermoelectric modules. 
     
     
         8 . The air turbo-refrigerating plant containing the directly coupled compressor and centrifugal expander, double-cavity heat exchanger, recuperator, moisture separator and refrigerating chamber with a chiller and a blower, with inlet and outlet of the second cavity of the double-cavity heat exchanger open to the atmosphere, while inlet is via the blower, being characterized that the plant is equipped with a double-cavity heat-exchanging chiller, second and third moisture separators, and the second and third compressors being directly coupled, electric motor, the shaft of which is coupled to the shaft of the second and third compressors, and with the second double-cavity heat exchanger, with the compressor inlet connected to the inlet of the second compressor which is connected with its outlet via the first cavity of the second double-cavity heat exchanger to inlet of the third compressor, the outlet of which is connected via the first cavity of the double-cavity heat exchanger to the first cavity of the heat-exchanging chiller, the said chiller's cavity connected via the second moisture separator to the first cavity of the recuperator connected via the first moisture separator to the outlet of the centrifugal expander, while the latter with its outlet is connected to the second cavity of the heat-exchanging chiller, the latter cavity connected to the chiller and, via the latter, to the second cavity of the recuperator, the latter cavity being connected to the compressor inlet, with the latter's inlet opening to the atmosphere via the valve member while the second cavity of the second double-cavity heat exchanger opens to the atmosphere on the side of both the inlet and outlet, and on the side of the inlet—via the second blower. 
     
     
         9 . A plant, according to  claim 8 , being characterized in that it is equipped with an air dryer package which opens via inlet to the atmosphere and is connected with its outlet via the second valve member to the compressor inlet. 
     
     
         10 . A plant, according to any of  claims 8  and  9 , being characterized in that the first and second double-cavity heat exchangers are equipped with Peltier thermoelectric modules. 
     
     
         11 . A plant, according to any of  claims 8  to  10 , being characterized in that it is equipped with the second electric motor, the shaft of which is coupled to the shaft of the compressor and centrifugal expander. 
     
     
         12 . The centrifugal expander containing directly coupled wheels of the centrifugal expander and the compressor mounted on same shaft installed in the shell between gas-dynamic bearings, being characterized in that an axial shaft stabilizer is installed in the shell opposite to the shaft end on the side of the compressor wheel clear of the last stationary magnet. 
     
     
         13 . The centrifugal expander, according to  claim 12 , being characterized in that in the axial shaft stabilizer a stationary electric magnet is installed. 
     
     
         14 . The centrifugal expander, according to  claim 13 , being characterized in that the electric magnet includes own magnetic field strength regulator. 
     
     
         15 . The centrifugal expander, according to  claim 12 , characterized in that in the axial shaft stabilizer a stationary permanent magnet is installed. 
     
     
         16 . The centrifugal expander, according to  claim 12 , characterized in that it additionally contains a permanent magnet installed on the shaft end opposite to the stationary magnet. 
     
     
         17 . The centrifugal expander, according to  claim 12 , characterized in that it is equipped with the second axial shaft stabilizer installed in the shell opposite to the shaft end on the side of the wheel of the centrifugal expander wheel clear of the second stationary magnet, with the second permanent magnet installed on the shaft end opposite to the second stationary magnet. 
     
     
         18 . The centrifugal expander, according to  claim 17 , characterized in that in the second axial shaft stabilizer a stationary n electric magnet is installed. 
     
     
         19 . The centrifugal expander, according to  claim 18 , characterized in that the electric magnet contains a magnetic field strength regulator. 
     
     
         20 . The centrifugal expander, according to  claim 17 , characterized in that in the second axial shaft stabilizer a stationary permanent magnet is installed. 
     
     
         21 . The principle of operation of the air turbo-refrigerating plant, according to any of  claims 1 - 3 , involving supply of compressed air with the compressor into the first cavity of the double-cavity heat exchanger in which compressed air is cooled with ambient air fed with the blower via the second cavity of the double-cavity heat exchanger, following which compressed air is cooled in the recuperator with cold air fed supplied from the cooler of the refrigerating chamber, after which compressed air is separated from moisture in the moisture separator and dried compressed air is fed into the centrifugal expander, where air, by way of expansion and transformation of its pressure energy into mechanical energy of rotation of wheels of the centrifugal expander and compressor is cooled and fed under reduced pressure into the cooler of the refrigerating chamber for removal of heat from, and cooling of, the chamber; from the cooler air is fed into the second cavity of the recuperator where compressed air is cooled, after which air is fed from the recuperator to the compressor inlet, characterized in that compressed air, before being fed in the first cavity of the recuperator, is cooled in the double-cavity heat exchanging chiller with air fed through it from the centrifugal expander and is separated from moisture in the second moisture separator, and air cooled in the centrifugal expander, before it is fed via the double-cavity heat-exchanging chiller into the cooler of the refrigerating chamber, is separated from moisture in the third moisture separator, with temperature in the refrigerating chamber and cooling capacity of the air turbo-refrigerating plant being regulated by changing rotation speed of the blower in the double-cavity heat exchanger. 
     
     
         22 . Principle of operation, according to  claim 21 , characterized in that temperature in the refrigerating chamber is additionally regulated by changing the rotation speed of the blower in the air cooler. 
     
     
         23 . The principle of operation, according to any of  claims 21  and  22 , characterized in that temperature in the refrigerating chamber is additionally regulated by cooling of compressed air in the double-cavity heat exchanger by installing of Peltier thermoelectric modules. 
     
     
         24 . The principle of operation, according to any of  claims 21  to  23 , characterized in that temperature in the refrigerating chamber is additionally regulated by cooling of compressed air in the double-cavity heat exchanger, by feeding water through the double-cavity heat exchanger. 
     
     
         25 . The principle of operation, according to any of  claims 21  to  24 , being characterized in that temperature in the refrigerating chamber is additionally regulated by changing rotation speed of the electric motor directly coupled to the compressor and centrifugal expander. 
     
     
         26 . The principle of operation, according to any of  claims 4  to  7 , involving supply of compressed air into the first chamber of the double-chamber heat exchanger in which compressed air is cooled with ambient air fed by the blower via the second chamber, after which compressed air is cooled in the recuperator with cold air from the cooler of the refrigerating chamber, following which compressed air is separated from moisture in the moisture separator and dried compressed air is fed into the centrifugal expander where air, by way of expansion and transformation of its pressure energy into mechanical energy of rotation of wheels of the centrifugal expander and compressor, and feed at reduced pressure into the cooler of the refrigerating chamber in order to remove heat from the said chamber and cool it; from the chiller air is fed into the second chamber of the recuperator where compressed air is cooled, characterized in that compressed air, before being fed into the first cavity of the recuperator, is cooled in the double-cavity heat-exchanging chiller with air fed through it from the centrifugal expander and is separated from moisture in the second moisture separator, air cooled in the centrifugal expander, before being fed via the double-cavity heat-exchanging chiller into the cooler of the refrigerating chamber, is separated from moisture in the third moisture separator, air from the second chamber of the recuperator air is fed into the inlet of the second compressor which compresses air and delivers it into the first chamber of the double-cavity heat exchanger, in the latter compressed air is cooled feeding ambient air via the second chamber of the second double-cavity heat exchanger with the second blower, while from the first chamber of the second double-cavity heat exchanger air is fed into the compressor, where temperature in the refrigerating chamber and cooling capacity of the air turbo-refrigerating plant is performed by regulation of rotation speed of the blower of the double-cavity heat exchanger. 7. The principle of operation according to  claim 26 , characterized in that additional regulation of temperature in the refrigerating chamber is performed by regulation of rotation speed of the blower of the second double-cavity heat exchanger. 
     
     
         28 . The principle of operation according to any of  claims 26  and  27  characterized in that additional regulation of temperature in the refrigerating chamber is performed by regulation of rotation speed of the electric motor of the second compressor. 
     
     
         29 . The principle of operation according to  claim 26  characterized in that additional regulation of temperature in the refrigerating chamber and cooling capacity of the refrigerating plant is performed simultaneously by changing the rotation speed of the electric motor of the second compressor and changing rotation speed of the blower in the second double-cavity heat exchanger and chiller blower. 
     
     
         30 . The principle of operation according to  claim 26 , characterized in that temperature in the refrigerating chamber is additionally regulated by cooling of the second double-cavity heat exchanger with Peltier thermoelectric modules. 
     
     
         31 . The principle of operation according to  claim 26 , characterized in that temperature in the refrigerating chamber is additionally regulated by additional simultaneous cooling of the first and the second double-cavity heat exchangers using Peltier thermoelectric modules. 
     
     
         32 . The principle of operation according to  claim 26 , characterized in that temperature in the refrigerating chamber is additionally regulated by additional cooling of the second double-cavity heat exchanger with water. 
     
     
         33 . The principle of operation according to  claim 26 , characterized in that temperature in the refrigerating chamber is additionally regulated by additional simultaneous cooling of the first and the second double-cavity heat exchangers with water. 
     
     
         34 . The principle of operation according to  claim 26 , characterized in that temperature in the refrigerating chamber is additionally regulated by changing rotation speed of the chiller blower. 
     
     
         35 . The principle of operation according to  claims 26 ,  32  to  34 , characterized in that temperature in the refrigerating chamber is additionally regulated by changing rotation speed of the second electric motor, the shaft of which is coupled to the shaft of the compressor and centrifugal expander. 
     
     
         36 . The principle of operation of the air turbo-refrigerating plant, according to  claim 8 , involving supply of compressed air into the first cavity of the double-cavity heat exchanger, in which compressed air is cooled with ambient air supplied with the blower via the second cavity of the double-cavity heat exchanger, following which compressed air is cooled in the recuperator with cold air fed from the cooler of the refrigerating chamber, following which compressed air is separated from moisture in the moisture separator and dried compressed air is fed in the centrifugal expander where it is cooled by way of expansion and transformation of its pressure energy into mechanical energy of rotation of wheel of the centrifugal expander and compressor and fed under reduced pressure into the cooler of the refrigerating chamber for heat removal from the latter and cooling, after which from the cooler air is fed into the second cavity of the recuperator where compressed air is cooled, characterized in that compressed air, before being fed into the first cavity of the recuperator, is cooled in the double-cavity heat-exchanging chiller with air fed via this chiller from the centrifugal expander and is separated from moisture in the second moisture separator, after which air cooled in the centrifugal expander, before being fed via the double-cavity heat-exchanging chiller into the cooler of the refrigerating chamber, is separated from moisture in the third moisture separator, from the second cavity of the recuperator air is fed into the inlet of the compressor which compresses air and feeds it into the second compressor, from which additionally compressed air is fed into the first cavity of the second double-cavity heat exchanger, while in the latter compressed air is cooled by feeding ambient air with the second blower via the second cavity of the second double-cavity heat exchanger, and from the first cavity of the second double-cavity heat exchanger air is fed into the third compressor, from which compressed air is fed into the first cavity of the double-cavity heat exchanger, while regulation of temperature in the refrigerating chamber and cooling capacity of the air turbo-refrigerating plant is performed by regulation of rotation speed of the blower of the double-cavity heat exchanger. 
     
     
         37 . The principle of operation according to  claim 36 , characterized in that temperature in the refrigerating chamber is additionally regulated by regulating rotation speed of the blower which feeds air into the refrigerating chamber through the cooler. 
     
     
         38 . The principle of operation according to any of  claims 36  and  37 , characterized in that temperature in the refrigerating chamber is additionally regulated by additional cooling of compressed air in the double-cavity heat exchanger by installing Peltier thermoelectric modules in that heat exchanger. 
     
     
         39 . The principle of operation according to any of  claims 36  and  37 , characterized in that temperature in the refrigerating chamber is additionally regulated by additional cooling of compressed air in the double-cavity heat exchanger with water fed through that heat exchanger. 
     
     
         40 . The principle of operation according to any of  claims 36  and  37 , characterized in that temperature in the refrigerating chamber and cooling capacity of the air turbo-refrigerating plant are regulated by changing rotation speed of the blower in the second double-cavity heat exchanger. 
     
     
         41 . The principle of operation according to any of  claims 36  and  37 , characterized in that additional regulation of temperature in the refrigerating chamber is performed by additional cooling of compressed air in the second double-cavity heat exchanger by installing Peltier thermoelectric modules in that heat exchanger. 
     
     
         42 . The principle of operation according to any of  claims 36  and  37 , characterized in that additional regulation of temperature in the refrigerating chamber is performed by additional cooling of compressed air in the second double-cavity heat exchanger with water fed through that heat exchanger. 
     
     
         43 . The principle of operation according to any of  claims 36  and  37 , characterized in that additional regulation of cooling capacity and temperature in the refrigerating chamber is performed by regulation of rotation speed of the electric motor, the shaft of which is coupled to the shaft of the second and third compressors. 
     
     
         44 . The principle of operation according to any of  claims 36  and  37 , characterized in that additional regulation of cooling capacity and temperature in the refrigerating chamber is performed by regulation of rotation speed of the second electric motor, the shaft of which is coupled to the shaft of the compressor and centrifugal expander.