High-temperature heat pump plant, reversibly usable in alternative operational mode as a co-tri-generation plant

Abstract

The present invention relates to the field of energy conversion plants and, in particular, concerns a same plant configuration that can be reversibly used according to two alternative operational modes, wherein each operating unit work in both said operational modes. The first operational mode involves operating as a co-tri-generation plant for supplying the end-user with electrical/mechanical power and simultaneously with heating power and/or refrigeration power through the conversion of thermal power supplied by any heat source (renewable or non-renewable). The second operational mode involves operating as a high-temperature heat pump without the mechanical and/or electrical power supplied by an external source for supplying the end-user with high-temperature heating power through the conversion of the low to medium-temperature thermal power supplied by the aforementioned heat source.

1 . An energy conversion plant making use of a single working fluid apt to absorb a thermal power transferred by a heat source, the plant comprising:
 i) Isenthalpic flow rate regulation means(S) apt to divide the overall flow rate of said working fluid circulating in the plant into a first and a second share of the working fluid;   ii) Downstream of said isenthalpic flow rate regulation means(S), a first circuit (C 1 ) apt for the circulation of at least said first share of the working fluid, said first circuit comprising:
 first adiabatic two-phase compression means (TC 1,M ) apt to increase the pressure and consequently the temperature of said working fluid, powered by a fraction of the overall electrical or mechanical power generated by said plant; 
 first isobaric heat exchange means (HE 1,N ); 
 first adiabatic two-phase expansion means (TE 1,O ) apt to generate said electrical power or mechanical power due to the decrease in the pressure and consequently the temperature of said working fluid; 
 first isobaric thermal regeneration means (TR 1,P ) functionally associated with said first adiabatic two-phase compression means (TC 1,M ) and said first adiabatic two-phase expansion means (TE 1,O ), apt to promote a transfer of thermal power between the working fluid circulating downstream of at least one stage of said first adiabatic two-phase expansion means (TE 1,O ) and the same working fluid circulating downstream of at least one stage of said first adiabatic two-phase compression means (TC 1,M ); 
   iii) Downstream of said isenthalpic flow rate regulation means (S), a second circuit (C 2 ) apt for the circulation of said second share of the working fluid, said second circuit comprising:
 second isobaric heat exchange means (HE 2 ); 
 second adiabatic two-phase expansion means (TE 2,O* ) apt to generate said electrical power or mechanical power due to the decrease in the pressure and consequently the temperature of said working fluid; 
 third isobaric heat exchange means (HE 3,N ); 
 second adiabatic two-phase compression means (TC 2,M* ) apt to increase the pressure and consequently the temperature of said working fluid, powered by a fraction of the overall electrical or mechanical power generated by said plant; 
 wherein said first and second circuits (C 1 , C 2 ) are in communication with each other so as to be apt to combine said first share of the working fluid of said first circuit (C 1 ) downstream of said first adiabatic two-phase expansion means (TE 1,O ) and said second share of the working fluid of said second circuit (C 2 ) downstream of said second adiabatic two-phase compression means (TC 2,M* ); 
   iv) A third circuit (C 3 ) downstream of said second adiabatic two-phase compression means (TC 2,M* ) for the circulation of the overall flow rate of said working fluid (i.e., consisting of said first and second share of the working fluid) towards said isenthalpic flow rate regulation means (S), further comprising, upstream of the latter, fourth isobaric heat exchange means (HE 4 );   v) Control means configured to distribute the working fluid between said first and second circuit and to perform the switching of said first and second circuit according to a first operational mode of the plant as a high-temperature heat pump for supplying the end-user with heating power at different temperature values, wherein:
 the overall mechanical or electrical power produced by said first adiabatic two-phase expansion means (TE 1,O ) and said second adiabatic two-phase expansion means (TE 2,O* ) is equal to or greater than the overall mechanical or electrical power required by said first adiabatic two-phase compression means (TC 1,M ) and said second adiabatic two-phase compression means (TC 2,M* ), wherein in said first operational mode of the plant as a high-temperature heat pump; 
 said second isobaric heat exchange means (HE 2 ) and said fourth isobaric heat exchange means (HE 4 ) are configured to operate, according to said first operational mode of the plant as a high-temperature heat pump, as means for the isobaric vapor generation of said working fluid, being fed by said medium-low temperature thermal power provided from said heat source; 
 said first isobaric heat exchange means (HE 1,N ) are configured to operate, according to said first operational mode of the plant as a high-temperature heat pump, at least as means for isobaric condensation apt to condense said working fluid, resulting in the supply of heating power to said end-user at different temperature values; 
 said third isobaric heat exchange means (HE 3,N* ) are configured to operate, according to said first operational mode of the plant as a high-temperature heat pump, at least as means for isobaric heat transfer (thermal dissipation) from the working fluid to the external environment; 
 said first and second adiabatic two-phase compression means (TC 1,M , TC 2,M* ) are configured to increase the pressure and consequently the temperature of the working fluid by converting mechanical/electrical power supplied to said same first and second adiabatic two-phase compression means, operating according to said first operational mode of the plant as a high-temperature heat pump, wherein the two-phase working fluid has a variable quality within a wide range: i) up to values near one in the inlet sections of said first adiabatic two-phase compression means (TC 1,M ), wherein in this limiting condition said two-phase working fluid predominantly consists of the vapor phase; ii) up to values near zero in the inlet sections of said second adiabatic two-phase compression means (TC 2,M* ), wherein in this limiting condition said two-phase working fluid predominantly consists of the liquid phase; 
 said first and second adiabatic two-phase expansion means (TE 1,O , TE 2,O* ) are configured to decrease the pressure and consequently the temperature of the working fluid, resulting in the production of mechanical/electrical power, operating according to said first operational mode of the plant as a high-temperature heat pump, wherein the two-phase working fluid has a variable quality within a wide range: i) up to values near zero in the inlet sections of said first adiabatic two-phase expansion means (TE 1,O ); ii) up to values near one in the inlet sections of said second adiabatic two-phase expansion means (TE 2,O* ). 
   
     
     
         2 . The plant according to  claim 1 , wherein said control means are configured to distribute the working fluid between said first and second circuit and furthermore to execute the switching of said first and second circuit, according to a second operational mode of the plant as a co-tri-generation plant, for supplying the end-user with electrical or mechanical power, heating power or cooling power at different temperature values, wherein:
 said second isobaric heat exchange means (HE 2 ) and said fourth isobaric heat exchange means (HE 4 ) are configured to operate, according to said second operational mode of the plant as a co-tri-generation plant, at least as isobaric condensation means apt to condense said working fluid with consequent thermal dissipation to the external environment or supply to said end-user of heating power;   said first isobaric heat exchange means (HE 1,N ) are configured to operate, according to said second operational mode of the plant as a co-tri-generation plant, at least as isobaric condensation means apt to condense said working fluid with consequent supply to said end-user of heating power at different temperature values, except for the first isobaric heat exchange means associated with the maximum pressure (and consequently the maximum temperature) of the working fluid of said plant, in which said first isobaric heat exchange means associated with the maximum pressure are configured to operate, according to said second operational mode of the plant as a co-tri-generation plant, at least as means for isobaric vapor generation of said working fluid, being fed by high-temperature thermal power provided from the heat source;   -said third isobaric heat exchange means (HE 3,N* ) are configured to operate, according to said second operational mode of the plant as a co-tri-generation plant, at least as isobaric evaporation means apt to evaporate said working fluid with consequent supply of cooling power to the end-user.   
     
     
         3 . The plant according to any one of  claims 1 , wherein said control means are configured to distribute the working fluid between said first and second circuit and furthermore to execute the switching of said first and second circuit, according to said second operational mode of the plant as a co-tri-generation plant, wherein:
 said first and second adiabatic two-phase compression means (TC 1,M , TC 2,M* ) are configured to determine the increase of the pressure and consequently the temperature of the working fluid by converting of mechanical/electrical power supplied to said first and second adiabatic two-phase compression means, operating according to said second operational mode of the plant as a co-tri-generation plant, wherein the two-phase working fluid has a variable quality in a wide range: i) up to values close to zero in the inlet sections of said first adiabatic two-phase compression means (TC 1,M ); ii) up to values close to one in the inlet sections of said second adiabatic two-phase compression means (TC 2,M* );   said first and second adiabatic two-phase expansion means (TE 1,O , TE 2,O* ) are configured to determine the decrease of the pressure and consequently the temperature of the working fluid with consequent production of mechanical/electrical power, operating according to said second operational mode of the plant as a co-tri-generation plant, wherein the two-phase working fluid has a variable quality in a wide range: i) up to values close to one in the inlet sections of said first adiabatic two-phase expansion means (TE 1,O ); ii) up to values close to zero in the inlet sections of said second adiabatic two-phase expansion means (TE 2,O* )   
     
     
         4 . The plant according to  claim 1 , further comprising first spillover working fluid flow rate means (B 1,Q ) functionally associated with said first adiabatic two-phase compression means (TC 1,M ) and said first adiabatic two-phase expansion means (TE 1,O ), configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the circulation of a portion of the working fluid flow rate (B 1,Q ) between said first adiabatic two-phase compression means (TC 1,M ) and said first adiabatic two-phase expansion means (TE 1,O ) through interposed first connection means or through said first isobaric heat exchange means (HE 1,N ), wherein said first isobaric heat exchange means (HE 1,N ) are further configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
     
     
         5 . The plant according to  claim 1 , comprising first spillover working fluid flow rate means (B 1,Q ):
 functionally associated with said first adiabatic two-phase expansion means (TE 1,O ) and configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the circulation of a portion of the working fluid flow rate between said first adiabatic two-phase expansion means (TE 1,O ) through interposed said first isobaric heat exchange means (HE 1,N ), and optionally to determine the circulation of the working fluid flow rate exiting from said first adiabatic two-phase expansion means (TE 1,O ) towards said first adiabatic two-phase compression means (TC 1,M ) through interposed first connection means or through said interposed first isobaric heat exchange means (HE 1,N ), wherein said first isobaric heat exchange means (HE 1,N ) are further configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the heat transfer from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said first adiabatic two-phase compression means (TC 1,M ) and configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the circulation of a portion of the working fluid flow rate between said first adiabatic two-phase compression means (TC 1,M ) through said interposed first isobaric heat exchange means (HE 1,N ), and optionally to determine the circulation of the working fluid flow rate exiting from said first adiabatic two-phase compression means (TC 1,M ) towards said first adiabatic two-phase expansion means (TE 1,O ) through interposed first connection means or through said interposed first isobaric heat exchange means (HE 1,N ), wherein said first isobaric heat exchange means (HE 1,N ) are further configured to perform, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-tri-generation plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
 
     
     
         6 . The plant according to  claim 4 , in which said first spillover working fluid flow rate means (B 1,Q ) are furthermore:
 functionally associated with said first adiabatic two-phase expansion means (TE 1,O ) and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said first adiabatic two-phase expansion means (TE 1,O ) through interposed said first isobaric heat exchange means (HE 1,N ), and optionally to determine the circulation of the working fluid flow rate exiting from said first adiabatic two-phase expansion means (TE 1,O ) towards said first adiabatic two-phase compression means (TC 1,M ) through interposed first connection means or through said interposed first isobaric heat exchange means (HE 1,N ), wherein said first isobaric heat exchange means (HE 1,N ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said first adiabatic two-phase compression means (TC 1,M ) and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said first adiabatic two-phase compression means (TC 1,M ) through said interposed first isobaric heat exchange means (HE 1,N ), and optionally to determine the circulation of the working fluid flow rate exiting from said first adiabatic two-phase compression means (TC 1,M ) towards said first adiabatic two-phase expansion means (TE 1,O ) through interposed first connection means or through said interposed first isobaric heat exchange means (HE 1,N ), wherein said first isobaric heat exchange means (HE 1,N ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
 
     
     
         7 . The plant according to  claim 1 , comprising second spillover working fluid flow rate means (B 2,Q* ), functionally associated with said second adiabatic two-phase compression means (TC 2,M* ) and said second adiabatic two-phase expansion means (TE 2,O* ), and configured to execute, according to the first operational mode of the plant as a high-temperature heat pump and alternatively according to the second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said second adiabatic two-phase compression means (TC 2,M* ) and said second adiabatic two-phase expansion means (TE 2,O* ) through interposed second connection means or through said third isobaric heat exchange means (HE 3,N* ), wherein said third isobaric heat exchange means (HE 3,N* ) are also configured to execute, according to the first operational mode of the plant as a high-temperature heat pump and alternatively according to the second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
     
     
         8 . The plant according to  claim 1 , comprising second spillover working fluid flow rate means (B 2,Q* ):
 functionally associated with said second adiabatic two-phase expansion means (TE 2,O* ), and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said second adiabatic two-phase expansion means (TE 2,O* ) through said interposed third isobaric heat exchange means (HE 3,N* ), and optionally to determine the circulation of the working fluid flow rate exiting from said second adiabatic two-phase expansion means (TE 2,O* ) to said second adiabatic two-phase compression means (TC 2,M* ) through interposed second connection means or through said interposed third isobaric heat exchange means (HE 3,N* ), wherein said third isobaric heat exchange means (HE 3,N* ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said second adiabatic two-phase compression means (TC 2,M* ), and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said second adiabatic two-phase compression means (TC 2,M* ) through said interposed third isobaric heat exchange means (HE 3,N* ), and optionally to determine the circulation of the working fluid flow rate exiting from said second adiabatic two-phase compression means (TC 2,M* ) to said second adiabatic two-phase expansion means (TE 2,O* ) through interposed second connection means or through said interposed third isobaric heat exchange means (HE 3,N* ), wherein said third isobaric heat exchange means (HE 3,N* ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
 
     
     
         9 . The plant according to  claim 8 , wherein said second spillover working fluid flow rate means (B 2,Q* ) are further:
 functionally associated with said second adiabatic two-phase expansion means (TE 2,O* ), and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said second adiabatic two-phase expansion means (TE 2,O* ) through said interposed third isobaric heat exchange means (HE 3,N* ), and optionally to determine the circulation of the working fluid flow rate exiting from said second adiabatic two-phase expansion means (TE 2,O* ) towards said second adiabatic two-phase compression means (TC 2,M* ) through interposed second connection means or through said interposed third isobaric heat exchange means (HE 3,N* ), wherein said third isobaric heat exchange means (HE 3,N* ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said second adiabatic two-phase compression means (TC 2,M* ), and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the circulation of a portion of the working fluid flow rate between said second adiabatic two-phase compression means (TC 2,M* ) through said interposed third isobaric heat exchange means (HE 3,N* ), and optionally to determine the circulation of the working fluid flow rate exiting from said second adiabatic two-phase compression means (TC 2,M* ) towards said second adiabatic two-phase expansion means (TE 2,O* ) through interposed second connection means or through said interposed third isobaric heat exchange means (HE 3,N* ), wherein said third isobaric heat exchange means (HE 3,N* ) are further configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer from or to the working fluid at respective distinct temperature values. 
 
     
     
         10 . The plant according to  claim 1 , wherein said second circuit comprises second isobaric thermal regeneration means (TR 2,P* ) functionally associated with said second adiabatic two-phase compression means (TC 2,M* ) and said second adiabatic two-phase expansion means (TE 2,O* ), and configured to execute, according to said first operational mode of the plant as a high-temperature heat pump, and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the heat transfer between the working fluid circulating downstream of at least one stage of said second adiabatic two-phase expansion means (TE 2,O* ) and the same working fluid circulating downstream of at least one stage of said second adiabatic two-phase compression means (TC 2,M* ). 
     
     
         11 . The plant according to  claim 1 , wherein said control means comprise:
 first deviation means (DM 1,K ) configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the deviation of said working fluid in said first circuit (C 1 ), bypassing said respective first isobaric heat exchange means (HE 1,N ) except for said first isobaric heat exchange means associated with the maximum pressure (and consequently the maximum temperature) of the working fluid in said plant; and   second deviation means (DM 2,K* ) configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the deviation of said working fluid in said second circuit (C 2 ), bypassing said respective third isobaric heat exchange means (HE 3,N* ) except for said third isobaric heat exchange means associated with the minimum pressure (and consequently the minimum temperature) of the working fluid in said plant; and   third deviation means (DM 3 ) configured to execute, according to said first operational mode of the plant as a high-temperature heat pump and alternatively according to said second operational mode of the plant as a co-trigeneration plant, the deviation of said working fluid between said first circuit (C 1 ) downstream of said first adiabatic two-phase expansion means (TE 1,O ) and said third circuit (C 3 ) upstream of said fourth isobaric heat exchange means (HE 4 ), bypassing said second circuit (C 2 ).   
     
     
         12 . A method for energy conversion by making use of a single working fluid in a thermodynamic cycle apt to absorb a thermal power transferred by a heat source, the method comprising:
 i) dividing the overall flow rate of said working fluid circulating in the thermodynamic cycle into a first and a second share through isenthalpic regulation (S);   ii) circulating at least said first share of the working fluid downstream of said isenthalpic regulation (S) in a first sequence of thermodynamic transformations in said first circuit (C 1 ) which includes:
 first adiabatic two-phase compression transformations (TC 1,M ) apt to increase the pressure and consequently the temperature of said working fluid, operated by making use of a fraction of the overall electrical or mechanical power generated by said thermodynamic cycle; 
 first isobaric heat exchange transformations (HE 1,N ); 
 first adiabatic two-phase expansion transformations (TE 1,O ) apt to generate said electrical power or mechanical power due to the decrease in the pressure and consequently the temperature of said working fluid; 
 first isobaric thermal regeneration transformations (TR 1,P ) functionally associated with at least one stage of said first adiabatic two-phase compression transformations (TC 1,M ) and at least one stage of said first adiabatic two-phase expansion transformations (TE 1,O ), apt to promote the heat transfer between the working fluid circulating downstream of at least one stage of said first adiabatic two-phase expansion transformations (TE 1,O ) and the same working fluid circulating downstream of at least one stage of said first adiabatic two-phase compression transformations (TC 1,M ); 
   iii) circulating at least said second share of the working fluid downstream of said isenthalpic regulation (S) in a second sequence of thermodynamic transformations in said second circuit (C 2 ) which includes:
 second isobaric heat exchange transformations (HE 2 ); 
 second adiabatic two-phase expansion transformations (TE 2,O* ) apt to generate said electrical power or mechanical power due to the decrease in the pressure and consequently the temperature of said working fluid; 
 third isobaric heat exchange transformations (HE 3,N ); 
 second adiabatic two-phase compression transformations (TC 2,M* ) apt to increase the pressure and consequently the temperature of said working fluid, operated by making use of a fraction of the overall electrical or mechanical power generated by said thermodynamic cycle; 
 wherein said first share of the working fluid in said first sequence of thermodynamic transformations of said first circuit (C 1 ) downstream of said first adiabatic two-phase expansion transformations (TE 1,O ) and said second share of the working fluid in said second sequence of thermodynamic transformations of said second circuit (C 2 ) downstream of said second adiabatic two-phase compression transformations (TC 2,M* ) are combined with each other. 
   iv) circulating the overall flow rate of said working fluid, obtained due to the mixing of said first and second shares of the working fluid, in a third circuit (C 3 ), located downstream of said second adiabatic two-phase compression transformations (TC 2,M* ), towards said isenthalpic regulation (S), further comprising, upstream of said isenthalpic regulation (S), fourth isobaric heat exchange transformations (HE 4 );   v) control transformations apt to distribute the working fluid between said first and second sequence of thermodynamic transformations in said first and second circuits, respectively, and switching said first and second sequence of thermodynamic transformations according to a first operational mode of the method associated with a high-temperature heat pump thermodynamic cycle for supplying the user with heating power at different temperature values, in which:
 the overall mechanical or electrical power produced by said first adiabatic two-phase expansion transformations (TE 1,O ) and said second adiabatic two-phase expansion transformations (TE 2,O* ) is equal to or greater than the overall mechanical or electrical power required by said first adiabatic two-phase compression transformations (TC 1,M ) and said second adiabatic two-phase compression transformations (TC 2,M* ), in which in said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle: 
 said second isobaric heat exchange transformations (HE 2 ) and said fourth isobaric heat exchange transformations (HE 4 ) generate isobarically, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle, vapor of said working fluid being fed by said medium-low temperature thermal power supplied by said heat source; 
 said first isobaric heat exchange transformations (HE 1,N ) condense isobarically, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle, said working fluid with the consequent supply to said end-user of heating power at different temperature values; 
 said third isobaric heat exchange transformations (HE 3,N* ) isobarically transfer (dissipate) thermal power from the working fluid to the external environment, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle; 
 said first and second adiabatic two-phase compression transformations (TC 1,M , TC 2,M* ) increase the pressure and consequently the temperature of the working fluid by converting mechanical/electrical power supplied to said first and second adiabatic two-phase compression transformations, operating according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle in which the two-phase working fluid has a variable quality over a wide range: i) up to values close to one in the inlet sections of said first adiabatic two-phase compression transformations (TC 1,M ), wherein in this limiting condition said two-phase working fluid consists almost exclusively of the vapor phase; ii) up to values close to zero in the inlet sections of said second adiabatic two-phase compression transformations (TC 2,M* ), wherein in this limiting condition said two-phase working fluid consists almost exclusively of the liquid phase; 
 said first and second adiabatic two-phase expansion transformations (TE 1,O , TE 2,O* ) decrease the pressure and consequently the temperature of the working fluid with the consequent production of mechanical/electrical power, operating according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle in which the two-phase working fluid has a variable quality over a wide range: i) up to values close to zero in the inlet sections of said first adiabatic two-phase expansion transformations (TE 1,O ); ii) up to values close to one in the inlet sections of said second adiabatic two-phase expansion transformations (TE 2,O* ). 
   
     
     
         13 . The method according to  claim 12 , wherein said control transformations distribute the working fluid into said first and second sequence of thermodynamic transformations in said first and second circuit, and further switch said first and second sequence of thermodynamic transformations in said first and second circuit into a second operational mode of the method associated with a co-tri-generation thermodynamic cycle for supplying the end-user with electrical or mechanical power, heating power, or cooling power at different temperature values, wherein:
 said second isobaric heat exchange transformations (HE 2 ) and said fourth isobaric heat exchange transformations (HE 4 ) condense, according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid with the consequent dissipation of thermal power to the external environment or supply of heating power to said end-user; 
 said first isobaric heat exchange transformations (HE 1,N ) condense, according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid with the consequent supply of heating power at different temperature values to said end-user, except for the first isobaric heat exchange transformations associated with the maximum pressure (and consequently the maximum temperature) of the working fluid in said thermodynamic cycle, wherein said first isobaric heat exchange transformations associated with the maximum pressure isobarically generate vapor of said working fluid, being fed by high-temperature thermal power supplied by the heat source, according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle; 
 said third isobaric heat exchange transformations (HE 3,N* ) evaporate isobarically, according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid with the consequent supply of cooling power to the end-user. 
 
     
     
         14 . Method according to any one of  claims 12 , wherein said control transformations distribute the working fluid between said first and second sequence of thermodynamic transformations in said first and second circuit, and further switch said first and second sequence of thermodynamic transformations in said first and second circuit in said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, in which:
 said first and second isobaric two-phase compression transformations (TC 1,M , TC 2,M* ) increase the pressure and consequently the temperature of the working fluid through the conversion of mechanical/electrical power supplied to said first and second isobaric two-phase compression transformations, operating according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, in which the two-phase working fluid has a variable quality in a wide range: i) up to values close to zero in the inlet sections of said first isobaric two-phase compression transformations (TC 1,M ); ii) up to values close to one in the inlet sections of said second isobaric two-phase compression transformations (TC 2,M* );   said first and second isobaric two-phase expansion transformations (TE 1,O , TE 2,O* ) decrease the pressure and consequently the temperature of the working fluid, resulting in the production of mechanical/electrical power, operating according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, in which the two-phase working fluid has a variable quality in a wide range: i) up to values close to one in the inlet sections of said first isobaric two-phase expansion transformations (TE 1,O ); ii) up to values close to zero in the inlet sections of said second isobaric two-phase expansion transformations (TE 2,O* ).   
     
     
         15 . The method according to  claim 12 , further comprising first working fluid flow spillover transformations (B 1,Q ), functionally associated with said first isobaric two-phase compression transformations (TC 1,M ) and said first isobaric two-phase expansion transformations (TE 1,O ), and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow (B 1,Q ) between said first isobaric two-phase compression transformations (TC 1,M ) and said first isobaric two-phase expansion transformations (TE 1,O ) through interposed first connection transformations or through said interposed first isobaric heat exchange transformations (HE 1,N ), wherein said first isobaric heat exchange transformations (HE 1,N ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
     
     
         16 . The method according to  claim 12 , comprising first working fluid flow spillover transformations (B 1,Q ):
 functionally associated with said first isobaric two-phase expansion transformations (TE 1,O ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said first isobaric two-phase expansion transformations (TE 1,O ) through said interposed first isobaric heat exchange transformations (HE 1,N ), and possibly circulating the working fluid flow exiting from said first isobaric two-phase expansion transformations (TE 1,O ) towards said first isobaric two-phase compression transformations (TC 1,M ) through interposed first connection transformations or through said first interposed isobaric heat exchange transformations (HE 1,N ), wherein said first isobaric heat exchange transformations (HE 1,N ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said first isobaric two-phase compression transformations (TC 1,M ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said first isobaric two-phase compression transformations (TC 1,M ) through interposed first isobaric heat exchange transformations (HE 1,N ), and possibly circulating the working fluid flow exiting from said first isobaric two-phase compression transformations (TC 1,M ) towards said first isobaric two-phase expansion transformations (TE 1,O ) through interposed first connection transformations or through said first isobaric heat exchange transformations (HE 1,N ), wherein said first isobaric heat exchange transformations (HE 1,N ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
 
     
     
         17 . The method according to  claim 15 , wherein said first working fluid flow spillover transformations (B 1,Q ) are also:
 functionally associated with said first isobaric two-phase expansion transformations (TE 1,O ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said first isobaric two-phase expansion transformations (TE 1,O ) through said interposed first isobaric heat exchange transformations (HE 1,N ), and possibly circulate the working fluid flow exiting from said first isobaric two-phase expansion transformations (TE 1,O ) towards said first isobaric two-phase compression transformations (TC 1,M ) through interposed first connection transformations or through said interposed first isobaric heat exchange transformations (HE 1,N ), wherein said first isobaric heat exchange transformations (HE 1,N ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values;   
       or vice versa
 functionally associated with said first isobaric two-phase compression transformations (TC 1,M ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said first isobaric two-phase compression transformations (TC 1,M ) through interposed first isobaric heat exchange transformations (HE 1,N ), and possibly circulate the working fluid flow exiting from said first isobaric two-phase compression transformations (TC 1,M ) towards said first isobaric two-phase expansion transformations (TE 1,O ) through interposed first connection transformations or through said first isobaric heat exchange transformations (HE 1,N ), wherein said first isobaric heat exchange transformations (HE 1,N ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
 
     
     
         18 . The method according to  claim 12 , comprising second working fluid flow spillover transformations (B 2,Q* ) functionally associated with said second isobaric two-phase compression transformations (TC 2,M* ) and said second isobaric two-phase expansion transformations (TE 2,Q* ), and transfer, according to said first operating mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said second isobaric two-phase compression transformations (TC 2,M* ) and said second isobaric two-phase expansion transformations (TE 2,Q* ) through interposed second connection transformations or through said third isobaric heat exchange transformations (HE 3,N* ), wherein said third heat exchange transformations (HE 3,N* ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
     
     
         19 . The method according to  claim 12 , comprising second working fluid flow spillover transformations (B 2,Q* ):
 functionally associated with said second isobaric two-phase expansion transformations (TE 2,O* ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said second isobaric two-phase expansion transformations (TE 2,O* ) through interposed third isobaric heat exchange transformations (HE 3,N* ), and optionally circulating the working fluid flow exiting from said second isobaric two-phase expansion transformations (TE 2,O* ) to said second isobaric two-phase compression transformations (TC 2,M* ) through intermediate second linking transformations or through said third isobaric heat exchange transformations (HE 3,N* ), wherein said third isobaric heat exchange transformations (HE 3,N* ) further transfer, in accordance with said first operating mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively in accordance with said second operating mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power to or from the working fluid at respective distinct temperature values.   
       or vice versa
 functionally associated with said second isobaric two-phase compression transformations (TC 2,M* ) and transferring, in accordance with said first operating mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively in accordance with said second operating mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said second isobaric two-phase compression transformations (TC 2,M* ) through intermediate third isobaric heat exchange transformations (HE 3,N* ), and optionally circulate the working fluid flow exiting from said second isobaric two-phase compression transformations (TC 2,M* ) towards said second isobaric two-phase expansion transformations (TE 2,O* ) through interposed second connection transformations or through said third isobaric heat exchange transformations (HE 3,N* ), wherein said third isobaric heat exchange transformations (HE 3,N* ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
 
     
     
         20 . The method according to  claim 19 , wherein said second working fluid flow spillover transformations (B 2,Q* ) are further:
 functionally associated with said second isobaric two-phase expansion transformations (TE 2,O* ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said second isobaric two-phase expansion transformations (TE 2,O* ) through interposed third isobaric heat exchange transformations (HE 3,N* ), and optionally circulate the working fluid flow exiting from said second isobaric two-phase expansion transformations (TE 2,O* ) to said second isobaric two-phase compression transformations (TC 2,M* ) through interposed second connection transformations or through said third isobaric heat exchange transformations (HE 3,N* ), wherein said third isobaric heat exchange transformations (HE 3,N* ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values.   
       or vice versa
 functionally associated with said second isobaric two-phase compression transformations (TC 2,M* ) and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, a portion of the working fluid flow between said second isobaric two-phase compression transformations (TC 2,M* ) through interposed third isobaric heat exchange transformations (HE 3,N* ), and optionally circulate the working fluid flow exiting from said second isobaric two-phase compression transformations (TC 2,M* ) to said second isobaric two-phase expansion transformations (TE 2,O* ) through interposed second connection transformations or through said third isobaric heat exchange transformations (HE 3,N* ), wherein said third isobaric heat exchange transformations (HE 3,N* ) further transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power from or to the working fluid at respective distinct temperature values. 
 
     
     
         21 . The method according to  claim 12 , wherein said second sequence of thermodynamic transformations in said second circuit (C 2 ) comprises second isobaric thermal regeneration transformations (TR 2,P* ) functionally associated with said second isobaric two-phase compression transformations (TC 2,M* ) and said second isobaric two-phase expansion transformations (TE 2,O* ), and transfer, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, thermal power between the working fluid circulating downstream of at least one stage of said second isobaric two-phase expansion transformations (TE 2,O* ) and the same working fluid circulating downstream of at least one stage of said second isobaric two-phase compression transformations (TC 2,M* ). 
     
     
         22 . The method according to  claim 12 , wherein said control transformations comprise:
 first deviation transformations (DM 1,K ) deviate, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle, and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid in said first sequence of thermodynamic transformations in said first circuit (C 1 ), bypassing said respective first isobaric heat exchange transformations (HE 1,N ) except for said first isobaric heat exchange transformations associated with the maximum pressure (and consequently the maximum temperature) of the working fluid in said thermodynamic cycle; and   second deviation transformations (DM 2,K* ) deviate, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle, and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid in said second sequence of thermodynamic transformations in said second circuit (C 2 ), bypassing said respective third isobaric heat exchange transformations (HE 3,N* ) except for said third isobaric heat exchange transformations associated with the minimum pressure (and consequently the minimum temperature) of the working fluid in said thermodynamic cycle; and   third deviation transformations (DM 3 ) deviate, according to said first operational mode of the method associated with said high-temperature heat pump thermodynamic cycle, and alternatively according to said second operational mode of the method associated with said co-tri-generation thermodynamic cycle, said working fluid between said first sequence of thermodynamic transformations in said first circuit (C 1 ) downstream of said first isobaric two-phase expansion transformations (TE 1,O ) and said third sequence of thermodynamic transformations in said third circuit (C 3 ) upstream of said fourth isobaric heat exchange transformations (HE 4 ), bypassing said second sequence of thermodynamic transformations in said second circuit (C 2 ).