EP0147770A2 - Thermische Induktionsmaschine - Google Patents

Thermische Induktionsmaschine Download PDF

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Publication number
EP0147770A2
EP0147770A2 EP84115702A EP84115702A EP0147770A2 EP 0147770 A2 EP0147770 A2 EP 0147770A2 EP 84115702 A EP84115702 A EP 84115702A EP 84115702 A EP84115702 A EP 84115702A EP 0147770 A2 EP0147770 A2 EP 0147770A2
Authority
EP
European Patent Office
Prior art keywords
column
heat
columns
condenser
boiler
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP84115702A
Other languages
English (en)
French (fr)
Other versions
EP0147770A3 (en
EP0147770B1 (de
Inventor
Jacques Sterlini
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alstom SA
Original Assignee
Alstom SA
Alsthom Atlantique SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alstom SA, Alsthom Atlantique SA filed Critical Alstom SA
Priority to AT84115702T priority Critical patent/ATE31806T1/de
Publication of EP0147770A2 publication Critical patent/EP0147770A2/de
Publication of EP0147770A3 publication Critical patent/EP0147770A3/fr
Application granted granted Critical
Publication of EP0147770B1 publication Critical patent/EP0147770B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/006—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the sorption type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/12—Sorption machines, plants or systems, operating continuously, e.g. absorption type with resorber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2315/00—Sorption refrigeration cycles or details thereof
    • F25B2315/002—Generator absorber heat exchanger [GAX]

Definitions

  • the present invention relates to a thermal induction machine for relating thermal resources to thermal uses, with a view to enhancing the thermal energy of the resources.
  • Another example is that of an enthalpy source at a low temperature level (factory thermal rejection, for example 45 ° water).
  • the enthalpy content of this source can be used, for space heating for example, by increasing its temperature up to 80 ° by means of a heat pump.
  • Absorption heat pumps use a static process, but their performance is inherently poor due to the structure of their thermal cycle.
  • An object of the invention is to provide a thermal machine using only quasi-reversible heat exchanges, so as to avoid degradation of the exergy content of the thermal resources used.
  • Another object of the invention is to produce a machine which either only comprises static means, therefore robust and not very subject to wear, or combine static and dynamic means, but with an energy efficiency much higher than that provided by systems which follow known thermal cycles.
  • An object of the invention is to provide a reversible thermal machine, that is to say capable of receiving thermal energy at a medium temperature level and recovering this energy by bringing it to high temperature, as well as receiving energy at low and high level and supply it at intermediate level.
  • Another object is to produce thermal devices whose manufacturing costs are significantly lower compared to thermal machines of the same power.
  • thermodynamic notions To fully understand the structure and operation of the thermal device of the invention, it is necessary to recall some thermodynamic notions and to give a certain number of definitions.
  • FIG. 1 schematically represents a distillation column 1 for the distillation of a mixture of two bodies A and B, A being the most volatile.
  • the column is associated with a boiler 2, and with a condenser 3.
  • the temperature axis T is directed towards the bottom of the figure.
  • the mixture A + B is introduced in the middle of the column at a temperature T 2 ; body B, with controlled purity, flows liquid at the bottom of the column at temperature T o ; one part goes to production P B , the other is evaporated in the boiler 2; the enthalpy content of the vapor thus produced is distributed along the column; when this vapor arrives at the head of the column at temperature T, it contains the body A of controlled purity; it is then condensed; part of A leads to production P A , the other (reflux) is returned to the column.
  • the arrow V represents the steam flow and the arrow L the steam flow in a section S (T) of the column at the temperature T.
  • the portions BC and CD are both arcs of very tense curves which can be assimilated to straight lines, representative of exchanges with external heat transfer circuits at constant specific heat.
  • the machine comprises a first and second columns continuously covering a temperature range TT 2 , without overlapping the respective temperature ranges of the columns, the end zones of the columns being all the heat exchange seat with the outside, the zones at temperatures T and T 2 exchanging in the same direction, the other end zones exchanging in the opposite direction.
  • the first and second columns cover a temperature range TT 2 g with a common temperature zone T 1 T2, the sources of heat, positive or negative, applied to a column between two given values of temperature inducing in the other column, between the same temperatures, a heat of opposite sign.
  • the machine by associating it with a working source (positive by a compressor, negative by a turbine), the machine is characterized in that at least one point of a column, located in a section end of a thermal transfer element constituting said column, is connected to a vapor drawing circuit which transports steam to the homologous point of the reverse column, said circuit comprising a member for carrying the pressure of the vapor of its value at the sampling point at its value at the point of reinjection into said reverse column, the machine comprising means for establishing a liquid flow rate between said sampling and steam reinjection points, so as to obtain equality of liquid flow rates in the peer sections of the associated columns.
  • the columns, the heat transfer circuits and the external sources exchange heat.
  • the right column C d (high pressure P, high temperature) is a distillation column whose high temperature region between T and T ' 0 is a boiler that receives a quantity of heat Q 0 from the outside (for example from a heat transfer medium M o ), and from which a liquid flow m 0 to T o is extracted.
  • the low-level region is a condenser which rejects heat Q 1 between T 1 and T 1 outside (for example to a heat carrier M 1 ) and from which a condensate flow rate m 1 to T 1 is extracted.
  • the left column is at lower pressure Pg and therefore at lower temperature; it receives in the opposite direction the adventitious flows from the right column in homologous sections where the same liquid concentration reigns at equilibrium. It has the same general operating characteristics as the first column, particularly with regard to exchanges with MDs.
  • Mass exchanges give rise to the arrival of a dm in a section with the same concentration, same temperature.
  • Cg will be the reverse column of C d if all the quantities of the "flow" type (flow rates, heat exchanges, etc.) are equal and of opposite sign in all homologous sections. Let us examine under which conditions Cg is effectively the reverse column of C d .
  • thermo induction machine The property that we have just described is considered essential, for this reason we call the machines which derive from this principle "thermal induction machine”.
  • Multi-stage devices are those where the two columns, continuing to operate in a similar manner to previously, can have a temperature interval in common (Figure 6).
  • m • 1 heats the column 0g1g which is associated with it; in the system S ', it is the column 1'2 which heats m • 1 .
  • Multistage machines are built using a construction game, the rules of which will be clarified by finishing the machine has begun.
  • the machine comprises a column Kd and a column Kg, operating with a mixture of R113 and R114.
  • FIG 12 established with the conventions established on page 9 from line 26.
  • Figure 13 explains this diagram by highlighting the components which carry out the heat exchanges. The temperature axis convention remains. We see that it is necessary to use four exchangers E 1 , E 2 , E 3 , E 4
  • Each exchanger is of the counter-current type and works with a constant temperature difference at each point.
  • P 1 , P 2 , P 3 pumps ensure the circulation of liquids.
  • Figure 14 shows, with its components on feet, the machine tritherme represented diagrammatically in FIGS. 12 and 13.
  • the conventions relating to the axes of temperature and gravity are abolished to make room for conventional conventions of representation.
  • the internal exchanges in this example, are three times higher than the power of use, but the exchanges with the columns are very low (of the order of 7%).
  • Figures 15 and 16 are two diagrams of an alternative embodiment of the machine.
  • FIG. 16 is a more detailed conventional representation, in which the exchange ⁇ Ts of the various exchangers are used.
  • the exchange ⁇ T in the exchanger Q e01 is equal to the temperature range of the boiler T 0 -T ' 0 .
  • the exchange ⁇ Ts for the entire high-level cycle are organized with the same water.
  • the situation of the exchangers is reversed, because the heating exchanger compartment is at a temperature lower than that of the heated compartment.
  • the powers exchanged are:
  • the explicit diagram shows three liquid-liquid exchangers of power: therefore a total of 195 kW, a value which has become low compared to 982 kW useful power.
  • the heat transfer circuit C c comprises a succession of horizontal coils such as 5, placed at different discrete levels.
  • the two-phase fluid circulates in tubes T provided with a lining or a spiral spring; the heat transfer fluid circulates between the tubes. A maximum exchange surface is thus obtained with a very low pressure drop.
  • a low temperature level such as a water table
  • the diagram in FIG. 21 represents a tritherm machine which receives thermal energy Q i1 , Q i2 at intermediate temperature T 1 , T ' 1 , T 1 , T'g o and supplies calories Q h at high temperature level T o , T ' 0 while rejecting energy Q b at low temperature level T 2 , T' 2 .
  • FIGS. 22A and 22B schematically represent for 22A, and more detailed for 22B, a multi-stage machine with two columns; it is a machine that uses a mixture of ammonia and water.
  • the common temperature range for the columns is 59 ° C - 238.25 ° C.
  • the right column G d is equipped with a boiler B 0 receiving heat (1925 kW) at a high temperature level, a boiler B1 receiving 2300 kW from the condenser C 1 in the left column, and a condenser C ' 1 yielding 2700 kW for use at intermediate thermal level;
  • the left column is equipped with a high level condenser C 1 yielding 2300 kW to boiler B 1 of the right column, a condenser C 2 yielding 2400 kW in use and a low level boiler receiving 3175 kW from a low-level resource.
  • the first machine receives the heat Q 1 and Q ' 1 at T 0 and T 2 respectively and supplies Q 1 + Q' 1 to T 1 .
  • the second machine receives Q • 1 at T 1 and Q " 1 to T 2 respectively and supplies Q • 1 + Q" 1 to T 3.
  • They can be constructed starting from trithermal diagrams; for example, start from FIG. 24, representing two heat transfer systems with two elements each, inducing each other one inside the other, one at high pressure P, the other at low pressure Pg.
  • FIG. 29 represents a heat pump where the compression takes place with the steam circulating between the columns at high level, which one has constructed starting from the diagram of FIG. 25.
  • Figure 30 is the reverse figure of 26; associated with a system like the one in figure 25, it allows to build a pump heat like that of Figure 31, where the effluents are transferred from one column to another at medium temperature level.
  • the heat pumps of Figures 28 and 29 have heat transfer circuits whose temperature differences A T are equal and in continuity with each other.
  • the machines which have just been described have the same reversibility character as the trithermal machines in detail close to wet or overheated compression (or expansion). If a mixture of type R112 + R113 is used as the working fluid, one can to a certain extent choose along the columns a vapor transfer point (at low, medium, or high level) so that the state steam on reinjection is roughly saturated. Furthermore, their operation has the same rigidity at nominal point; however, once we no longer allow our to exchange adventitious liquid flows between the columns, but also use vapor transport, we can build reversible machine configurations at nominal point, capable of combining any heat transfer circuits; Figure 35 gives an example.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Motor Or Generator Cooling System (AREA)
  • General Induction Heating (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Disintegrating Or Milling (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
EP84115702A 1983-12-22 1984-12-18 Thermische Induktionsmaschine Expired EP0147770B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84115702T ATE31806T1 (de) 1983-12-22 1984-12-18 Thermische induktionsmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8320573 1983-12-22
FR8320573A FR2557277B1 (fr) 1983-12-22 1983-12-22 Machine a induction thermique

Publications (3)

Publication Number Publication Date
EP0147770A2 true EP0147770A2 (de) 1985-07-10
EP0147770A3 EP0147770A3 (en) 1985-08-14
EP0147770B1 EP0147770B1 (de) 1988-01-07

Family

ID=9295447

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84115702A Expired EP0147770B1 (de) 1983-12-22 1984-12-18 Thermische Induktionsmaschine

Country Status (6)

Country Link
EP (1) EP0147770B1 (de)
JP (1) JPS60169067A (de)
AT (1) ATE31806T1 (de)
BR (1) BR8406673A (de)
DE (1) DE3468518D1 (de)
FR (1) FR2557277B1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990004145A1 (de) * 1988-10-04 1990-04-19 Gerd Wilhelm Verbundsysteme aus normaler und inverser rektifikation
FR2699262A1 (fr) * 1992-12-11 1994-06-17 Elf Aquitaine Dispositif à haute performance de production simultanée de chaleur et de froid utiles.
EP0836059A1 (de) * 1996-10-10 1998-04-15 Gaz De France Kältepumpe
WO1998026238A1 (fr) * 1996-12-13 1998-06-18 Gaz De France Dispositif a absorption de chaleur et/ou de froid multietagee

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2860987B1 (fr) * 2003-10-15 2006-02-24 Cheng Ming Chou Procede multi-etapes pour la distillation, le refroidissement et la congelation sous vide

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE278076C (de) * 1911-08-11
FR676668A (fr) * 1928-06-16 1930-02-26 Siemens Ag Machine à absorption
GB422150A (en) * 1932-12-21 1935-01-07 Siemens Ag Improvements relating to heat converters comprising absorption apparatus
US2182453A (en) * 1936-01-18 1939-12-05 William H Sellew Heat transfer process and apparatus
US2193535A (en) * 1938-07-08 1940-03-12 Maiuri Refrigeration Patents L Absorption refrigerating machine
DE1501144A1 (de) * 1966-10-29 1970-01-29 Steil Karl Heinz Verfahren zur Erzeugung von Kaelte
FR2441135A1 (fr) * 1978-11-10 1980-06-06 Armines Transformateur a absorption
DE2938565A1 (de) * 1979-09-24 1981-04-09 Linde Ag, 6200 Wiesbaden Verfahren zum anheben des temperaturniveaus von waerme mit hilfe einer absorptionswaermepumpe
EP0148756B1 (de) * 1980-08-11 1989-03-08 Etablissement Public dit: CENTRE NATIONAL DE LA RECHERCHE SCIENTIFIQUE (CNRS) System zum Aufwertem thermischer Energie mit niedrigem Niveau unter Ausnutzung der Verdampfung, und Mischung zweier strömender Medien mit gleichem Dampfdruck bei unterschiedlichen Temperaturen
US4442677A (en) * 1980-11-17 1984-04-17 The Franklin Institute Variable effect absorption machine and process
DE3100348A1 (de) * 1981-01-08 1982-08-05 Dieter Dr.-Ing. 5064 Rösrath Markfort "resorptions-anlage zur waermetransformtation"
ATE109880T1 (de) * 1981-03-24 1994-08-15 Alefeld Georg Mehrstufige einrichtung mit arbeitsfluid- und absorptionsmittel-kreisläufen, und verfahren zum betrieb einer solchen einrichtung.

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990004145A1 (de) * 1988-10-04 1990-04-19 Gerd Wilhelm Verbundsysteme aus normaler und inverser rektifikation
FR2699262A1 (fr) * 1992-12-11 1994-06-17 Elf Aquitaine Dispositif à haute performance de production simultanée de chaleur et de froid utiles.
WO1994014018A1 (fr) * 1992-12-11 1994-06-23 Pierre Le Goff Dispositif a haute performance de production simultanee de chaleur et de froid utiles
EP0836059A1 (de) * 1996-10-10 1998-04-15 Gaz De France Kältepumpe
FR2754594A1 (fr) * 1996-10-10 1998-04-17 Gaz De France Frigopompe
US5899092A (en) * 1996-10-10 1999-05-04 Gaz De France Chiller
WO1998026238A1 (fr) * 1996-12-13 1998-06-18 Gaz De France Dispositif a absorption de chaleur et/ou de froid multietagee
FR2757255A1 (fr) * 1996-12-13 1998-06-19 Gaz De France Dispositif a absorption de chaleur et/ou de froid multietagee

Also Published As

Publication number Publication date
BR8406673A (pt) 1985-10-22
DE3468518D1 (en) 1988-02-11
EP0147770A3 (en) 1985-08-14
FR2557277A1 (fr) 1985-06-28
JPS60169067A (ja) 1985-09-02
EP0147770B1 (de) 1988-01-07
ATE31806T1 (de) 1988-01-15
FR2557277B1 (fr) 1986-04-11

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