Environmental Air Conditioning and Heating Plant

Abstract

A reverse cycle steam compression thermal machine is described, concerning a main circuit (100) connected to an auxiliary circuit (200), comprising an economizer (3), the main circuit (100) comprising a first high pressure exchanger (2) and an evaporator (5), the auxiliary circuit (200) comprising a second high pressure exchanger (7a) and a second expander (8); the economizer (3) includes a first hot branch (1c), a first cold branch (1f), a second hot branch (2c) and a second cold branch (2f).

1 . A reverse cycle steam compression thermal machine, comprising a main circuit ( 100 ) connected to an auxiliary circuit ( 200 ), comprising an economizer ( 3 ) in common with the main circuit and the auxiliary circuit, the main circuit ( 100 ) comprising a first high pressure exchanger ( 2 ) downstream of and in fluid communication with a first compressor ( 1 ), an evaporator ( 5 ) upstream of the first compressor ( 1 ) and downstream of and in fluid communication with a first expander ( 4 ), the auxiliary circuit ( 200 ) comprising a second high pressure exchanger ( 7   a ) downstream of and in fluid communication with a second compressor ( 6 ) and in parallel with a third high pressure exchanger ( 7   b ) placed near the evaporator ( 5 ), a second expander ( 8 ) downstream of and in fluid communication with the second high pressure exchanger ( 7   a ), the auxiliary circuit ( 200 ) suitable for sub-cooling the main circuit ( 100 ) in the case in which the high pressure exchanger ( 2 ) is a condenser, or for de-superheating the main circuit if the high pressure exchanger ( 2 ) is a gas chiller, said thermal machine characterized in that said economizer ( 3 ) in common is configured as a heat exchanger with a first hot branch ( 1   c ) connected downstream of the first high pressure exchanger ( 2 ), a first cold branch ( 1   f ) connected downstream of the economizer ( 3 ) in common and upstream of the first expander ( 4 ), a second hot branch ( 2   c ) connected downstream of the economizer ( 3 ) in common and upstream of the second compressor ( 6 ), a second cold branch ( 2   f ) connected downstream of the second expander ( 8 ) and upstream of the economizer ( 3 ) in common. 
     
     
         2 . The thermal machine according to  claim 1 , characterized in that the economizer ( 3 ) in common allows an internal heat exchange of a first refrigerant fluid (m 1 ) of the main circuit ( 100 ) with a second refrigerant fluid (m 2 ) of the circuit auxiliary ( 200 ), the entire flow rate of the first refrigerant fluid (m 1 ) sent to the economizer ( 3 ) in common to deliver thermal power to the auxiliary circuit ( 200 ) by sub-cooling a saturated liquid that circulates in the first hot branch ( 1   c ) when the high pressure exchanger ( 2 ) is a condenser, or, through a more severe de-superheating of a fluid circulating in the first hot branch ( 1   c ) compared to the initial de-superheating when the high pressure exchanger ( 2 ) is a gas chiller, and through the entire flow rate of the refrigerant fluid (m 2 ) sent to the economizer ( 3 ) in common to receive thermal power from the main circuit fluid ( 100 ) through a complete evaporation of the biphasic mixture up to the condition of saturated or superheated steam which circulates in the second hot branch ( 2   c ). 
     
     
         3 . The thermal machine according to  claim 2 , characterized in that the entire flow rate of refrigerant fluid (m 1 ) compressed by the first compressor ( 1 ) and subsequently cooled by means of the first high pressure exchanger ( 2 ) allows increasing the vapor pressure at a level such that the corresponding saturation temperature is higher than the ambient temperature at which the first high pressure exchanger ( 2 ) works, at the operating pressure of the evaporator ( 5 ) the corresponding saturation temperature is lower than the ambient temperature at which the evaporator ( 5 ) works, the vapor compressed by the compressor ( 1 ) introduced into the high pressure exchanger ( 2 ) exchanging thermal power with the environment to allow the cooling of the refrigerant fluid (m 1 ), to saturated liquid if the high pressure exchanger ( 2 ) is a condenser, or, a de-superheated gas if the high pressure exchanger ( 2 ) is a gas cooler. 
     
     
         4 . The thermal machine according to  claim 2 , characterized in that the entire flow rate of refrigerant fluid (m 1 ) sent to the first expander ( 4 ) to reduce the pressure and fed into the evaporator ( 5 ) allows the complete evaporation of the biphasic mixture with saturated or superheated steam, the entire flow of fluid compressed completely to the pressure of the first high pressure exchanger ( 2 ), allowing a new cycle to be started. 
     
     
         5 . The thermal machine according to  claim 2 , characterized in that the entire flow rate of refrigerant fluid (m 2 ) compressed by the second compressor ( 6 ) is subsequently cooled by means of the second high pressure exchanger ( 7   a ), said second compressor ( 6 ) allows increasing the vapor pressure to a level corresponding to the saturation temperature higher than the ambient temperature in which the second high pressure exchanger ( 7   a ) works, the refrigerant fluid (m 2 ) reaching a condition of saturated or subcooled liquid in the event that said second high pressure exchanger ( 7   a ) is a condenser, or, of de-superheated gas if said second high pressure exchanger ( 7   a ) is a gas chiller, the entire flow of saturated or de-superheated, subcooled refrigerant fluid (m 2 ) sent to the second expander ( 8 ). 
     
     
         6 . The thermal machine according to  claim 2 , characterized in that the entire flow rate of refrigerant fluid (m 2 ) compressed by the second compressor ( 6 ) is subsequently cooled by means of the third high pressure exchanger ( 7   b ) to carry out the defrost cycle ( 11 ) of said evaporator ( 5 ) in case of need, said compressor ( 6 ) allows increasing the vapor pressure to a level corresponding to the saturation temperature higher than the ambient temperature in which the second high pressure exchanger ( 7   b ) works, the refrigerant fluid (m 2 ) reaching a condition of saturated or subcooled liquid if said second high pressure exchanger ( 7   b ) is a condenser, or of de-superheated gas if said second high pressure exchanger ( 7   b ) is a gas chiller, the entire flow rate of saturated, subcooled or de-superheated refrigerant fluid (m 2 ), sent to the second expander ( 8 ). 
     
     
         7 . The thermal machine according to  claim 1 , characterized in that at least said first expander ( 4 ) and/or said second expander ( 8 ) assumes the configuration of a lamination valve. 
     
     
         8 . The thermal machine according to  claim 1 , characterized in that at least said first expander ( 4 ) and/or said second expander ( 8 ) assumes the configuration of a turbine connected to at least one alternator/compressor. 
     
     
         9 . The thermal machine according to  claim 8 , characterized in that the turbine can be that of a turbocharger/turbo-alternator to power a compressor connected in series or in parallel, any electronic device, a combustion engine, an air conditioning or heating system.