FR2557277A1 - THERMAL INDUCTION MACHINE - Google Patents

Abstract

The machine for the more effective utilisation of heat uses a working substance which is a mixture of two pure substances with different boiling points. The machine has two columns (Cd,Cg) operating at different pressures. In the first column a quantity of heat (Qo) is supplied to the base of the column. This heat causes one of the components of the working substance to evaporate and flow to the upper part of the second similar column (Cg) which operates in a reverse manner. Quantities of heat are transferred between the two columns at different heights above the base of each column.

Description

Thermal induction machine

  The present invention relates to a heat induction machine

  to link thermal resources and uses

  thermal energy, with a view to developing the thermal energy of

  these. We know the need to save energy. One way to do this is to use the existing enthalpic resources and to

  change from their current temperature to a temperature of

  tion, retaining their exergetic content. As an example of an enthalpy resource with a high temperature level, water vapor at 5000 ° C from a thermal power station can be mentioned. The current way to conserve the exergy of this resource is to use a turbine that will produce transformable mechanical energy

in electrical energy.

  It can be seen that implementation requires significant investments

  tives. Another example is that of a low-level enthalpic source of

  temperature (factory heat rejection, eg water at 45).

  The enthalpy content of this source can be used for space heating, for example, by increasing its temperature up to

  by means of a heat pump.

  Conventional heat pumps with compressed working fluid

  have a poor performance coefficient.

  It requires dynamic elements (compressors) subject to

wear and maintenance.

  Absorption heat pumps use a static process, but their efficiency is inherently poor because of the structure of

their thermal cycle.

  An object of the invention is to provide a thermal machine involving only quasi-reversible heat exchange, so as to avoid the degradation of the exergy content of the thermal resources used. Another object of the invention is to provide a machine which has only static means, therefore robust and not subject to wear, or combines static means and dynamic means, but with an energy efficiency much higher than that provided by the systems

  which follow the known thermal cycles.

  An object of the invention is to provide a reversing thermal machine.

  that is, capable of receiving thermal energy at an average temperature level and valuing that energy by raising it to high temperature, as well as receiving energy at low and high

  level and provide it at intermediate level.

  Another goal is to produce thermal devices whose manufacturing costs are significantly lower compared to

  thermal machines of the same power.

  To understand the structure and functioning of the

  thermal system of the invention, it is necessary to recall a few

  thermodynamic notions and give a number of definitions.

  The initial idea that led to the device of the invention is

  that it is possible to achieve static thermal transfers of about

  if-reversible. This notion of static heat transfer

  quasi-reversible originates from the study of distillation.

  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 a condenser 3.

  The temperature axis T is directed towards the bottom of the figure.

  The mixture A + B is introduced at the middle of the column at a temperature of

  T2; the body B, with controlled purity, flows at the bottom of the column at temperature T; one part goes to the production PB '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 top of the column at temperature T1, it contains the body A with controlled purity; it is then condensed; one part of A bears to the production PA 'the other (reflux) is returned to the column. The arrow V represents the vapor flow and the arrow L the vapor flow in a section S (T) of the column at temperature T. The physical operations put into play on the Merkel diagram are usually followed; this diagram (FIG. 2) comprises for each pressure: - 3 - equilibrium spindles, liquid concentration x (T) and y (T) body vapor A. enthalpy h (liquid) and H (vapor) of the mixture depending on the concentrations. The correspondences between these quantities on the diagram are

shown in Figure 2.

  It is easy to be convinced that the distillation thus carried out can not be reversible: by writing between two sections of the column the three conservation equations (flow A, flow A + B, enthalpy)

  realizes that they can not be verified at the same time

  is lying; as a result, in conventional distillation with heat columns

  the liquid and vapor phases in contact necessarily evolve

out of balance.

  The Applicant has observed that to have thermodynamic equilibrium

  (ie the values of the concentrations of the liquid x and

  vapor corresponding to equilibrium at the prevailing temperature pressures.

  In all respects, heat must be supplied or removed in each column section. French Patent No. 80 17313 gives a

  example of the means that can be implemented to achieve a distill-

reversible lation.

  The reversible distillation carried out in this way is

  thus, in each particular case, by a heat distribution T Q (t): q d T as typically represented 0To

in Figure 3.

  Q (T) comprises several parts, and in particular: the part BC (depletion E) which translates an endothermic activity of the column

  - CD (rectification R) which is exothermic.

  The portions BC and CD are both arcs of very tight curves which can be assimilated to straight lines, representative

  of exchanges with external heat-transfer circuits with specific heat

constant.

  The reasoning that has just been made with respect to a column at -'4-

  distiller is valid for all types of heat exchangers, in particular

  bind for a thermal system consisting for example of a packed column or trays equipped throughout its height with heat exchanger traversed by external heat-sensitive circuits supplying or extracting from said column linearized heat distribution ensuring its operation reversible. A column section equipped with a constant flow external heat transport circuit may be

  considered as an interchange comprising a first compartment, dipha-

  it is constituted by the column itself, the second compartment being traversed by the external coolant. Such an exchanger is

  referred to as the heat transfer element.

  It will be noted that through such an exchanger the flow of energy of the en-

  effluent appears to remain constant as a function of temperature,

second order close.

  By thermal activity, the amount of heat received or supplied in each heat transfer element will be referred to as thermal activity to ensure the reversibility of the thermodynamic phenomena for each temperature level T. A heat transfer element is defined by: the nature of the mixture diphasic used

  - the flows of liquid and vapor working eluide of the first

  - the operating pressure of the exchanger - the temperature values between which the fluid is

item.

  We deduce the calorific powers applied to the element

  (calorific resources = heat supplied to the system, positive;

  calorific = heat provided by the system, negative) and

  as a result, the nature of the coolant.

  For each given heat transfer element (called "direct"),

  given pressure it is possible to match a heat transfer element

  "reverse", at another pressure, in which: - the nature of the two-phase mixture is the same as that of the coolant - we find in the direct element and the inverse element, the sections

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  homologues, the same liquid and vapor flow rates at the same concentrations of the constituents of the working fluid, but moving in the opposite direction in

temperature function.

  the sources have the same absolute value for a direct element and an inverse element, but the signs are opposite. The subject of the invention is a heat transfer device for linking thermal resources and thermal uses, in order to value the energy of the resources without reducing their exergy content, said device operating very closely with the reversibility with a working fluid of at least

  two pure bodies which are miscible and put into play in two-phase

  in that it comprises: a first direct set of heat transfer elements placed in series on the liquid and vapor flows of the working fluid, said first set comprising a first two-phase exchange column operating at a first pressure value; a second set of heat transfer elements, said second set being inverse of the first and containing the same number of elements and in particular a second column with two-phase exchange, the second column working at a second pressure value lower than the first one; value, weed flows being established between the two sets across the homologous elements, all parts of the device having a temperature between any two values exchanging heat with each other, the weed rates and their direction being adjusted so that the two columns receive in all respects

  exchange rate the quantities of heat corresponding to their activity

thermal energy.

  In a particular embodiment, the machine comprises a

  first and second columns continuously covering a temperature range

  to T2, 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 with temperatures To and T2 exchanging in the same direction, the others end zones exchanging

reverse.

  In an industrial embodiment corresponding to a single-stage trithermal heat pump, the machine is characterized in that the first and second columns comprise at their hottest end respectively a first boiler and a second boiler and their

  the coldest end respectively a first and a second condensa-

  boilers receiving heat from outside resources.

  device and condensers supplying heat to a user

  the weed rates including:

  a first pair connecting the conjugated ends of the first

  their and the second condenser and exchanging heat in a first countercurrent exchanger,

  a second pair connecting the conjugate ends of the second

  their and the first condenser and exchanging heat in a second countercurrent exchanger, - a third pair substantially connecting the middle of the first

  column to the second condenser and exchanging heat in a third

  th countercurrent exchanger, and a fourth pair substantially connecting the middle of the second column to the first condenser and exchanging heat in a

  fourth countercurrent exchanger.

  In an industrial embodiment corresponding to an energy recovery machine available at medium temperature level, the first direct column comprises at its hottest end a first condenser supplying energy to one use, the second reverse column comprising at its coldest end a second condenser providing energy for use, the two columns each comprising at their common temperature a boiler receiving heat from external resources, the adventitious flows comprising:

  a first pair connecting the conjugate ends of the first

  their and the second condenser and exchanging heat in a first countercurrent exchanger,

  a second pair connecting the conjugate ends of the second

  their and the first condenser and exchanging heat in a second countercurrent exchanger, - a third pair substantially connecting the middle of the first -7 -

  column to the second condenser and exchanging heat in a third

  th countercurrent exchanger, and a fourth pair substantially connecting the middle of the second

  column to the first condenser and exchanging heat in a quad

  third counterflow heat exchanger. In another embodiment corresponding to a multi-stage machine, the first and second columns cover a temperature domain TO T2g with a common temperature zone T1 T2, the heat sources, positive or negative, applied to a column between two given values. inducing temperature in the other column,

  between the same temperatures, a heat of opposite sign.

  In another embodiment of the machine, by associating 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 transfer element

  constituent of said column, is connected to a sampling circuit

  vapor which transports steam to the homologous point of the

  reverse column, said circuit comprising a member for carrying the pressure

  the value of the vapor at the point of sampling at its value at the point of reinjection into the said reverse column, the machine comprising

  means for establishing a liquid flow between said sampling points

  vapor reinforcement, so as to obtain the equality of

  liquid flows in the homologous sections of the associated columns.

  The invention will be well understood from the description given below

  various embodiments of the invention, with reference to the accompanying drawing in which: Figure 1 schematically shows a conventional distillation column. Figure 2 shows a Merkel diagram for a mixture

binary.

  Figure 3 illustrates the heat exchanges occurring in a

  distillation column performing a quasi-reversible process.

  Figure 4 is a block diagram of a transfer device

single-stage thermal.

  Figure 5 is a Merckel diagram relating to the provision of

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Figure 4.

  Figures 6 to 10 are schematic diagrams explaining the

  operation of a multi-induction thermal transfer device

  floor. FIG. 11 is a Merckel diagram of a transmission device

  induction heat, multi-stage.

  Figure 12 schematically shows an induction machine

  single-stage thermal device in a first embodiment.

  Figure 13 is a more detailed diagram of the machine of the

figure 12.

  Figure 14 is an even more detailed representation of the

machine of Figures 12 and 13.

  Figures 15 and 16 are two diagrams of an induction machine

  single-stage thermal device according to a second embodiment.

  Figures 17 and 18 are two diagrams of an induction machine

  single-stage thermal device according to a third embodiment.

  Figures 19 and 20 show two diagrams of exchangers used

  in the machines of the invention.

  Figure 21 schematically shows a trithermal machine receiving heat at high and low temperature levels and providing

  heat to an intermediate level.

  Figures 22A and 22B schematically show a single-stage machine. FIG. 23C represents a multi-stage machine obtained by the

  combination of two single-stage machines represented in the

23A and 23B.

  Figures 24 to 26 are explanatory diagrams for the preparation of

  a machine for external work.

  Figure 27 is a diagram of a thermal induction machine

providing work.

  Figure 28 is a diagram of an induction heat pump

  thermal device according to a first embodiment.

  Figure 29 is a diagram of an induction heat pump

thermal according to a variant.

  Figure 30 is the opposite diagram to that of Figure 25.

  Figure 31 is a diagram of an induction heat pump

  according to a third embodiment.

  Figures 32 to 34 illustrate the construction of a heat pump.

  their thermal induction according to a fourth embodiment.

  Figure 35 schematically shows a heat pump according to

a fifth embodiment.

  Figure 36 shows schematically an induction machine tMher-

  external workstation with four columns.

  Figure 37 shows the machine of Figure 36 reduced to three

colonnex.

  Figures 3a and 39 reorient respective variants of

fSgc0res 36 e, 37.

  Fig. 40 is a diagame of the iso-integration of the carrier, the carrier in operation and the temperature of the carrier. 41. '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '*' 4 ee ee; ee? Espeegiveento i; Ss fiu, te.s; 3.9. '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' '' - ' qemóca a dieposi if according to the figm'.e is rprsenplSxt. ######################################################## the version edite moo6t.ageo The disposi-tif e% eo: nstitu 'by t: calion of de.ux elone, 2, co-ntact two-phase (for example flat% -ux or gan: 5 wise, on, It involves a fluid of trill according to the above-mentioned conditions, the working fluid is mixed with at least two pure iseibite bodies. J. Ie.prosC by dornnant only examples of nmlanges biEaia res .. The figre fI must be read with conventions ei-aproximable valid $ except éntntaire, for all the traine-les the, .eiques which will be

expe icted in this ijimoire.

  - The temperature axis T is directed to the bottom of the drawing.

  In the columns, the liquid and vapor flows are designated L and V. The values of the weed rates are denoted by the letter m with indices.

  - If an axis perpendicular to the temperature axis is drawn, the temperature

  is the same for all the points cut by this axis whether it is the points of the column, heat transfer circuits or

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external sources.

  To achieve this condition columns, circuits calopor

  and external sources (resources: positively counted and

  uses: negatively counted) exchange heat.

  Returning to FIG. 4, it is noted that the right column Cd (high pressure P, high temperature) is a distillation column whose high temperature region between To and T'o is a boiler which receives a quantity of heat Qo from the outside (for example of a coolant

  Mo), from which a liquid flow mo is extracted at To.

  The low-level region is a condenser that discharges a heat Q1 between T1 and T1, for example towards a coolant M1, and

  from which a flow of condensate m1 is extracted at T1.

  This column has throughout its temperature range

  t T T a basic flow distribution dm withdrawal or ol1 injection of the working fluid (weed rates) which exchange their

  sensible heat with the column; by construction the flow rates

  These are adjusted so that the exchanges with the column correspond in every respect to the supply of a quantity of heat equal to the thermal activity of the column. The determination of the dm is done as follows:

  The caleul takes place step by step towards decreasing temperatures.

  starting from T. Let us suppose that at a stage of computation we have reached o at T ', we therefore know L' V 'and all the dm calculated between To and T', write the equations for the step of elementary computation T 'T (two

  flow conservation equations, conservation of enthalpy).

  LI - V '+ Idmi = L - V + dmi + dm (T) x' L '-y' V '+, xi dmi = x L - y V + xi dmi + n dm h' L '- H' V '+ E hi mi = h L - HV + hi dmi + h dm + dq, The liquid and the vapor being hypothetically in equilibrium at T and T', the thermodynamic quantities (x, y, h, H) are known , dq is the external heat input and is a datum; so we have three linear equations with L, V, dm as unknown, so we can solve from near

  close to To at T1; the column thus obtained is strictly reversible.

  It should be noted that the practice of calculation indicates that the sections of type To or T'1 which are at the boundary between an exchange zone and an adiabatic zone receive adventitious flows of finite value. The left column Cg (boiler between Tg0 and T'go, condenser between T'g1 and Tg1, coolant flow Mgo, Mg1) is the reverse column of the column of

  right. This inverse term is explained later. It is noted that the provisions

  taken for the right-hand column give it a

  fully reversible operation.

  The left column is at lower pressure Pg and therefore at

  lower temperature; it receives in the opposite direction the flow rates

  of the right-hand column in homologous sections where the

  same liquid concentration at equilibrium. It has the same characteristics

  general operating characteristics that the first column, in particular

  with regard to trade with DMs.

  Mass exchanges result in the arrival of a DM in a section

  at the same concentration, same temperature.

  15. Heat exchanges are at constant temperature. In the single-stage machine we are currently examining, the pressure Pg is set such that Tgo = T1. Thus, the set of two columns continuously covers the temperature domain To Tg1; we find a

  single column at each temperature.

  Cg will be the inverse column of Cd if all the quantities of the "flux" type (flows, heat exchanges, etc ...) are equal and of sign

  contrary in all homologous sections. Let's look at what conditions

  Cg is actually reverse column of Cd.

  For this purpose, write the equations for the slice T'g Tg homo-

  logue of T 'T (1) The g - V'g + Vg + indmgi + dmg (Tg) (2) x'g The g - y'g V'g + xgi dmgi = xg Lg - yg Vg + xgi dmgi + xg dmg (Tg) (3) h'g The g - H'g V'g hgi dmgi = hg Lg - Hg Vg hgigi dmgi + hg dmg (Tg) + dqg is the external heat input Cg will be inverse of C if if any section with temperature Tg is inverse of its homologue with temperature T. Suppose that the section T'g is inverse of T ': The g = L', V'g = V ', dmgi = dmi

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  the section Tg will be inverse of the section T if the solutions Lg, Vg, dm (tg) of the system (1) + (2) + (3) are such that Lg = L,

Vg = V, dm (Tg) = dm (T).

  For this to be so it is necessary: 5. Conditions 1 yg: y Hg = H + A hg = H +, being an arbitrary quantity Condition 2 dqg = dq The conditions 1 mean that the Merckel diagrams established for

  the pressures Pg and P are deduced from each other by a translation.

  This property is not far from being realized in practice for the

  most mixing diagrams, although it is not strictly

  is lying; it is in a way a "property at the limit" analogous to the concept of perfect gas; we will say that in this case the diagram of

  Merckel is ideal (from our point of view).

  Finally we see that the association of two columns as described above can not give rise to a strictly

  reversible only in an ideal Merckel diagram.

  Condition 2 can be interpreted as follows: If a column of heat is brought to a given distribution, the appearance of a "heat demand" in the reverse column is called up in inverse distribution, which we will call "induced heat". ". Thus, in FIG. 4, the heat input Q along the To To domain by a coolant M induces a heat of the same value Qg = Qo between Tg0 and Tg'o, which must be taken at the level of use. ; in the same way the contribution Qg1 between T'g1 and Tg1 induces the heat Q1 = Qg1 between T'1 and T1 which one must also evacuate. Note that one could as well consider Q0o, as induced by Qgo, and that it is therefore indeed a question of

  coupling between heat transfer fluids M and Mgo.

  The property just described is considered to be

  for this reason we call machines that derive from this

  principle "thermal induction machine".

  Some properties of these systems can still be distinguished: - 13- 1 / We have Q1 Qo. = hi (T1) mi of o Q 1 Qo Qo = Qg Q1 Qgl Q + Qg COA = i - Qo (COA = coefficient of amplitude = heat with the use of heat at the source of heat) 2 / The position of the use in relation to the sources comes from the construction (figure 5) on the Merekel diagram * it is riCide eF

  only this position is likely to ensure a steady flow of

  Hble; it must therefore be considered as a kind of the no-isai point; the study of functions outside the nominal capacity will have no sound and no

about real machines.

  The multimedia devices are those where the two colors are

  In such cases, it is possible to use the same method as Ur.

  interval of tenpCrature in copmun (figure 6).

  When starting to run a system step by step from To, we have to decide from a different procedure

from that described previously.

  Let us situate ourselves at the stage of computation at a temperature T situated in an area common to both columns. Assume that all adventitious rates up to T have already been calculated for the right column; the left column is already provided up to T'g. To caleuler the T T'l we must now write: 2 flow equations for the left column (unknowns Lg, Vg) 2 flow equations for the right column (unknown L, Vq dm (T "1 enthalpy equation for the entire system between T and

* T ', that is to say the two eolumns and the set of weed rates.

  Let 5 linear equations, 5 unknowns, so we can gradually

  find the solution (flow structure L, V, Lg, Vg, dm).

  In this way we lose sight of how the exchanges between column and beams of DM are performed. We are now looking to

illuminate this last point. To achieve this we will try to identify in the system

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  multistage of Figure 6, the single-stage systems constituting

  tutifs. For this purpose, there is established in the system a cutoff according to FIG. 7, which interrupts the continuity of the flow rates L1, V1, L1g, V1g, and the two systems S and S 'thus constituted at 1, 1' are installed at the limits of

  lg, 1'g, condensers and evaporators, and the liquid flow rates are closed again.

  ml, m'1 between homologous columns (Figure 8). By hypothesis 1, 1 ', 1g, 1'g are very small temperature differences; the exchangers located on either side of the break (condensers and evaporators 1, 1 ', 1g, 1'g) have reverse operations. If we close the cut again we find figure 6. If we maintain it, we see S and S 'work in the same way (structure of the flow rates L, V, Lg, Vg, dm, identical to

  emergence near flows m1, m'1).

  From the point of view of the exchanges of heat with the columns, the flow rates m1 and m, are equivalent to: m1m = m1 '- m1 = LV (figure 9) Mi i 1 ii In the system S, m1 warms the column Oglg which him is

  associated; in the system S ', it is the column 1'2 which heats m ;.

  If we go back to the primitive system by gluing the cut all

  the elements of our constructions disappear; the fact remains that

  fictitiousness of the previous m flows were indicative of an assignment

  column 12 to the Oglg column, equivalent to the circula-

  closed circuit coolant m = L1 - V1 (see Figure 9).

  The reasoning just taken is independent of anything else that may happen in the system, including: Column 01 is certainly equipped with a heat source; we will therefore necessarily find on the Oglg column the induced heat distribution. One will have the choice between: 30. To supply it directly to a use, to give it to the column in opposite vis-à-vis between the same temperatures; in this case this heat distribution will be induced again

  on the left column and so on.

  Multi-stage machines are built using a construction game which we will specify the rules by finishing the machine we

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has begun.

  Starting from the starting section 01, (FIG. 10), many things have already been determined, and in particular:

the opposite section Oglg.

  5. The direct section vis-à-vis 12. They are built on the Merckel diagram as steps between the x (T) curves

  corresponding to the pressures P and Pg (Figure 11).

  Always following this staircase construction you can

  represent the heat distribution Q according to 00 'by a sequence of in-

  ductions and exchanges vis-à-vis until finally she sort

  from the left column (for example in lg 1'g).

  Similarly Q2 introduced in 3g 3'g will emerge from C in 22 '; the system is quadritherme; to make it trithermatic it is necessary to foresee the steps of staircase so that Qo0 and Q2 leave the system in the field of

  temperature prescribed for use.

  Until now, only theoretical machines have been described.

  Various embodiments of real machines will now be described. The actual machines differ from the theoretical machines by the following two points: - Merckel diagrams of fluids used in real machines are not perfect diagrams

  - the number of weed flows is over.

  It has been calculated, using numerical programs, real trithermal machines in which the liquid and the vapor evolve slightly out of equilibrium to allow the enthalpic balances

to be satisfied.

  This results in a slight difference in the actual COA compared to the COA theo-

  (in the example below 1.91 instead of 1.95).

  A real machine, in its conventional mode of representation

  it is shown in FIG. 12 and in more detail in FIG. 13, while FIG. 14 shows it in a configuration of FIG.

real construction.

  Figure 12 The machine comprises a column Kd and a column Kg, operating with

a mixture of R113 and R114.

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  The column Kd receives heat Qo0 between the temperatures To and T'o and

  provides heat Q'1 between the temperatures T'i and T1.

  Column Kg furnishes heat Q "1 between Tgo (= T'1) and T'go (= T1) and receives heat Q2 between temperatures T'g1 and Tg1. There are five weed rates: a first flow rate Mo , from Kd to To, Kg to Tg, exchanging heat at constant T with a second rate m 'from Kg to T'go at Kd to T'oi O a third rate m1 from Kd to T1 (= Tgo) to Kg at Tg1 exchanging heat with a fourth flow rate m'1 Kg T'g1, a fifth flow mm Kg to Kd exchanging heat with Kg Tgm Tg1 and Kd Tgo

  (= T1) at Tg, Tgm and Tg being substantially the intermediate temperatures

columns Kg and Kd.

  Figure 13 Figure 12 established with the conventions established on page 9 from line 26. Figure 13 explains this diagram by highlighting the components that perform the heat exchange. The Reliative Convention

  at the temperature axis remains. We see that it is necessary to use

  read four exchangers E1, E2, E3, E4 The ratings indicate that: - the mo flow is doubled in m and m

  the flow m is doubled in m and mm then m1 and mm.

M m m m 1

  the flow m1 is doubled in m1 and m1.

  with m = ml where m = m1 * m ** = m1 ** m 1 = m '

  Each exchanger is of the countercurrent type and works

  constant temperature difference in each point.

  P1, P2, P3 pumps ensure the circulation of liquids.

  Figure 14 Figure 14 shows, with its components on feet, the machine

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  trithermally shown schematically in Figures 12 and 13. The conventions relating to the axes of temperature and gravity are

  abolished to make room for conventional conventions of representation.

  The column portions exchanging heat with the outside have been isolated, namely:

  a BD boiler and a Cd condenser for the Kd column

  a boiler Bg and a condenser Cg for the column Kg.

  Column Kd is at high pressure (5 bars) while Column Kg

is at atmospheric pressure.

  The numerical indications beside the boilers and condensers correspond to the heat exchange with the outside expressed in kilowatts. The black arrows indicate the liquid flow rates in liters per second.

  The dashed arrows represent the steam flows.

  The operating temperatures are as follows: T'0 at the boiler inlet Bd = 85.830C TO at the boiler outlet Bd = 86.330C T'1 at the condenser inlet Cd = 60.89 C T1 at the outlet of the condenser Cd = 60, 39 C Tgo = T1 at the boiler inlet Bg = 60.390C T'go at the boiler outlet B = 59.89 C T'g1 at the condenser inlet C = 34.94 C Tgl = T2 at the condenser outlet Cg = 34.540C

  It is observed that the temperature differences at the ends of the

  heat exchange with the outside (boilers, condensers) is of the order of 0.5 degrees. We use conventional boilers and condensers. The internal exchanges of the machine, involving the working fluid, are as follows: Exchanger E1: 215 kW Exchanger E2 20 kW Exchanger E3: 0.7 kW Exchanger E4: 2.04 kW Column Kd 2.84 kW

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  Column Kg 2.57 kW Use (condenser Kd and Kg): 72 kW Internal exchanges, in this example, are three times higher than the power of use, but the exchanges with the

  columns are very weak (about 7%).

  It can be seen that trithermal induction machines are technologically constituted by the assembly of several types of subassemblies of conventional condensing boilers and condensers - countercurrent liquid-liquid heat exchangers - circulates the liquid working fluid of accessories such as pumps and liquid lamination - devices consisting of contact columns equipped with

  exchangers. These devices are in fact constituted by the Juxtapo-

  Series on the liquid and vapor of the working fluid of

  thermal transfer which we have described at the beginning of this memoir in its principles. We will describe these elements further under

  the aspect of their technological embodiment.

  Figures 15 and 16 are two diagrams of a variant embodiment of

machine.

  In these two figures, the conventions relating to the single axis of the temperatures directed downwards and to the axis of gravity are repeated. Figure 15 shows that: - The differences in the temperatures of the boilers and condensers is about C, - the same number and the same arrangement for the weed rates have been kept.

  Figure 16 is a more detailed conventional representation

  in which the exchange of the various exchangers is involved. There are boilers, condensers and heat exchangers

  Figure 14, but with the following notations: E01, E12, Eml, Elm.

  In addition, there is added to the machine: - a low power Eup exchanger - 9 -

  - A flash F at the entrance of the boiler Bg.

  Indeed, in the high temperature portion of the cycle, the exchange AT in the exchanger Qeo1 is equal to the temperature range of the To-To boiler. In the same way, the exchange tTs for the entire high-level cycle are organized from the same waters. At low temperature, the exchanger situation is reversed because the heat exchanger compartment is at a lower temperature than the heat exchanger compartment.

warmed compartment.

  This situation is corrected by using an additional exchanger

  silent (low power) and making a small flash of 5 C from

  working fluid that enters the boiler Bg.

  The powers exchanged are: - in the heat exchanger E01: 266 kW - in the heat exchanger E12: 43.6 kW - in the heat exchanger E 1: 25.6 kW - in the heat exchanger Em: 20 kW - in the heat exchanger exchanger E: 14 kW - in column Kd 82 kW - in column Kd: 73 kW - in column Kg: 73k - in use (Cd + Cg): 449 + 476 kW = 925 kW Internal exchanges by exchangers liquid-liquid represent about 40% of the useful power; the exchanges in the columns

  represent about 17% of the useful power.

  These two examples indicate how and with which order of magnitude the temperature interval of the external sources act on the internal exchanges: As one approaches the isothermal exchanges (T small), the internal liquid-liquid exchanges become very important compared to the thermal power of the system at the same time as the exchanges with the

  two-phase columns become evanescent.

  For A T = 5, the internal liquid-liquid exchanges are

  However, the exchanges with the columns are not yet prohibitive and seem feasible with existing technological means. Figures 17 and 18 illustrate another example of a machine in

- 20 -

  which heat sources exchange with the outside with a large temperature difference (of the order of 11 C). Note that there are only four weed rates; the one called mm in

  the previous examples became useless.

  5. that the two columns Kd and Kg include important parts to

  co-current, such as the system seen on foot would include 4 columns.

  The explicit diagram shows three liquid-liquid heat exchangers: Eo, 1 = 93.96 kW E1,1 = 6.13 kW E11, g '= 28.8 kW, therefore a total of 195 kW, a low value compared to the power

useful 982 kW.

  Let's look at two-phase column exchanges along the dif-

  Transfer elements: o00 'with working fluid 75,2 kW with external coolant 496 kW 571,2 kW 0'1' with working fluid 2,28 kW il 'with working fluid 50,74 kW with the heat transfer fluid 496 kW 549 kW og og 'with the working fluid 96,3 kW with the coolant 486 kW 582.3 kW o'g the g with the working fluid 12 kW with the coolant 21 kW the g lg with the working fluid 481 kW 514 kW Finally 2281 kw are exchanged directly with the diphasic column

  of which 1971 with the external coolants, 310 with the fluid of

vail.

- 21 -

  Note the following conclusions:

  Temperature intervals of exchange with external sources

  machines give some of the characteristics of certain

  contrasted: - machines exchanging with isothermal sources at relatively conventional boilers and condensers also include:

  significant liquid-liquid exchanges.

  To exchanges in small columns.

  - machines exchanging with sensible heat transfer fluids

  including heat transfer-column quite preponderant.

  To these two types of machine, it will be necessary to provide solutions

  different technologies for interchange between column and heat

  tors. For machines exchanging with isothermal sources a

  column made according to the diagram of Figure 19 can be used.

  It includes a classic G filling (Raschig rings by

  example); the heat transport circuit C comprises a succession of serpents

c

  horizontal lines such as 5, placed at different discrete levels.

  For machines exchanging with sensitive sources, which require a higher exchange rate, one will preferably use a

  exchanger as that of Figure 20.

  The two-phase fluid flows in tubes T equipped with a lining

  wise or spiral spring; the heat transfer fluid circulates between the tubes. This gives a maximum of exchange surface with a loss of

very low charge.

  The three exemplary embodiments which have been given with reference to FIGS. 12 to 14, 15 and 16, 17 and 18 respectively relate to single-stage machines in which energy is supplied at a high temperature level. a low level 3G temperature source (such as groundwater) and energy is obtained at

intermediate temperature.

  The diagram of FIG. 21 represents a trithermal machine that receives thermal energy Qil 'Qi2 at intermediate temperature T1, T'1, T, T1' go and supplies high temperature calorie Qh at To, T 'while rejecting energy Qb at low temperature level T2, T'2o T 'while rejecting energy Qb at low temperature level T2 T' o 2'2

- 22 -

  This results from the perfect reversibility of the machine and the thermal induction properties that exist in both directions of possible operation. Figs. 22A and 22B show schematically for 22A, and more detailed for 22B a multi-stage two-column machine; it is a machine that uses a mixture of ammonia and water. The

  common temperature range of the columns is 59 C - 238.25 C.

  The right column Gd is equipped with a boiler Bo receiving the

  heat (1925 kW) at high temperature, a boiler B1 receives

  2300 kW of the C1 condenser in the left column, and a condenser

  It yields 2700 kW when used at. intermediate thermal level

  diary; the left column is equipped with a high-level C1 condenser yielding 2300 kW to the boiler B1 of the right column, a condenser C2 yielding 2400 kW in use and a boiler B3 to low

  level receiving 3175 kW of a low level resource.

  In the more detailed diagram of Figure 22B, we see the flows

  weeds exchanged in exchangers E and E1.

  Note the presence of an EBC exchanger that boils the working fluid of the right column and condenses the fluid of

work from the left column.

  Fig. 23C is another embodiment of a multi-machine

  stage obtained by superposition of single-stage machines 23A and 23B: one 23A having a pressure column P, temperatures TO to T1 and a pressure column Pg and temperatures T1 to T2 - the other 23B having a pressure column Pg and temperatures T1 T3 and a pressure column P'g and temperatures T3 to T4. In practice, T4 is very close to T2 and, in any case, we can choose T3 so that

T4 is equal to T2.

  The first machine receives heat Q1 and Q'1 at To and T2

  respectively and provides Q1 + Q'1 to T1.

  The second machine receives Q at T1 and Q1 at T2 respectively, and

provides Q1 + Q "1 to T3.

  Nothing prohibits the inclusion in a single column of both

  columns of the two machines running between T1 and T3.

  We obtain the machine of FIG. 23C which receives Q1 at TO,

- 23 -

  Q'I1 + Qu1 to T2 and provides 0 to T1 and Q1 + Q "1 to T3.

  This was simply a multi-stage machine.

  It is possible to realize on the basis of the same principles described

  previously, thermal induction machines with external work.

  They are machines with two sources; the work can be provided by a turbine (energy production), or absorbed by a compressor (heat pump) according to the direction of the exchanges with the sources with high and

low level.

  They can be built from trithermal patterns; for example, from Figure 24, representing two transfer systems

  two elements each, mutually inducing one into the other

  be one at high pressure P, the other at low pressure Pg.

  Thermal exchanges between columns and external sources, as well as weed rates, were included. Let us practice a break between the two elements of each system as indicated by the mixed line. The systems of FIGS. 25 and 26 are obtained, with at bottom of FIG. 25 and at the top of FIG. 26 the flows V, Vg and L, Lg of vapor and

of fluid from the working fluid.

Consider the only figure 26.

  If the steam circuit V is closed by a turbine Tu which relaxes the gas from P to Pg and provides work, and if the liquid flows are connected by a Li bond exchanging heat q with the adventitious flow mi,

  to warm the flow L, a machine is obtained (FIG.

  outside work (w = q) by restoring heat to low

temperature level.

  FIG. 28 is the inverse machine of the machine of FIG. 27, receiving low-level heat Qo, receiving work W by a compressor Co and supplying heat Q'o = Qo + W at a high level

temperature.

It's a heat pump.

  FIG. 29 represents a heat pump where the compression is carried out with the steam flowing between the high-level columns, which

  it is built starting from the diagram of figure 25.

  Figure 30 is the inverse figure of 26; associated with a system like that of Figure 25, it allows to build a pump to

- 24 -

  as in Figure 31, where the effluents are transferred

  from one column to another at average temperature level.

  We can therefore build thermal induction heat pumps

  with compression at low, medium, or high temperature level.

  The general nature of the processes used with reference to the

  24 to 32 shows that not only can

  them, but also get work from sensible heat sources.

  The heat pumps of FIGS. 28 and 29 have heat circuits

  carriers whose temperature differences at T are equal and in the

continuity of one another.

  It is possible to separate coolants by

  ples from to T. Consider Figure 32 schematically representing a quadritherme machine and make a cut along the line in dashed line. The upper part is retained (Figure 33); the steam circuit is closed by a compressor Co and the liquid circuit by a

  Li binding exchanging with the adventitious flow ml (Figure 34).

  There was thus obtained a heat pump where the coolants are separated from A T. It could in principle be separated by 2, 3, ..., n times at T; but in fact this is unrealistic because the internal exchanges of the system quickly become prohibitive. A more economical process will be found later on.

  exchange surfaces to achieve the same result (but in contrast

pressurized).

  The machines just described have the same character of rever-

  that trithermal machines are close to damp or overheated compression (or expansion). If a mixture of the R112 + R113 type is used as the working fluid, a steam transfer point (low, medium, or high level) can be used to a certain extent along the columns to make the from steam to reinjection is almost saturating. Moreover, their operation at the same rigidity character at the nominal point; however, once we are allowed not only to exchange liquid weed flow rates between the columns, but we also use steam transport, we can build machine configurations that are reversible at the nominal point,

- 25 -

  capable of associating any heat transfer circuit; Figure 35

give an example.

  The thermal induction machines for outdoor work that we have

  examined so far only have two columns.

  The machines we have studied so far have only two columns; we can consider morphologies that include one

higher number.

  Fig. 36 shows such an embodiment; we recognize on the right of this figure a machine identical to that of figure 28,

  operating between P and P1; they transfer Q 'to the colon

  o Nes Cgo and C1 to a machine of the same type operating between P1 and P2; Cgo and C1 operating at the same pressure P1 and between the same temperatures T1 and T2 can be superimposed (Figure 37): the set Cgo, C1, M'o

  gives way to the column C 'whose operation results from the super-

i5

  position of the direct and reverse columns CO and C1 respectively of

  thermal sensitivity Q and Q'o; the thermal activity of C 'is therefore QO - Q'0 =; so it's a weak activity and it's a small

auxiliary column.

  Another example figures 38 and 39; same provisions as

  ously; moreover the coolant m0 warms C1; column C'1 (fig.

  re 39) is the seat of the thermal activity 2Qo-Q'o = QO + ql.

  It is convenient to represent multi-stage machines on diagrams in which the pressure, temperature down (as usual) is plotted on the abscissa; isocentrations x = constant are such

as shown in Figure 40.

  The arrangements of Figure 39 can be generalized to a 4-stage (Figure 41) or six-stage machine (Figure 42). The drawings depicted the pressure and temperature axes. The cycle is a cycle without flash of energy production from heat resources

  sensitive (eg geothermal).

S57277

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Claims (5)

  1 / Thermal induction machine for connecting resources   thermal sources and thermal uses (Qo0, Q1i Q'1i Q2),   in order to valorise the energy of the resources, said device   very close to the reversibility with a working fluid consisting of at least two miscible pure bodies and involved in two-phase form, characterized in that it comprises: a first direct set of heat transfer elements set in series on the liquid flow and steam of the working fluid, said   first set comprising a first column (Kd) with a dipha   sique operating at a first pressure value, - a second set of heat transfer elements, said second set being inverse of the first and containing the same number of elements and in particular a second column (Kg) with two-phase contact, the second column working at a second pressure value lower than the first value, heat-transfer rates (m, m'o, m1, m'1)   being established between the two sets across the homogeneous elements   logues, all parts of the device having a temperature between any two values (columns, weed rates) exchanging heat between them, weed rates and their meaning being adjusted so that the two columns receive in all points during exchanges   the quantities of heat corresponding to their thermal activity.   2 / Machine according to claim 1, characterized in that the first   re (Kd) and second (Kg) columns continuously cover an area of   temperature (To T2), without overlapping the temperature ranges   columns, since the end zones of the columns are all   the seat of heat exchange with the outside, the zones with the temperatures   extremes (To, T2) exchanging in the same direction, the other zones   end exchange in the opposite direction.   3 / Machine according to claim 2 characterized in that the first   re (Kd) direct column comprises at its hottest end a first   first boiler (Bd) supplied with heat by a first resource and a second boiler (Bg), that the second reverse column comprises (Kg) at its coldest end a second boiler (Bg) fed by a - 27 -   second resource, the two columns each with their own tempera-   a common condenser (Cd, Cg), these providing heat for a second use, the weed rates comprising:   a first pair connecting the conjugate ends of the first   their and the second condenser and exchanging heat in a first exchanger (El) against the current,   a second pair connecting the conjugate ends of the second   their and the first condenser and exchanging heat in a second exchanger (E2) against the current, - a third pair substantially connecting the middle of the first   column to the second condenser and exchanging heat in a third   second heat exchanger (E3) against the current, and a fourth pair substantially connecting the middle of the second   column to the first condenser and exchanging heat in a quad   third heat exchanger (E4) against the current ..   4 / Machine according to claim 2, characterized in that the first direct column (Kd) comprises at its hottest end a first condenser (Cd) providing energy for use, the second reverse column (Kg) comprising its coldest end a second condenser (Cg) providing energy to use, the two columns each comprising at their common temperature a boiler (Bd,   Bg) receiving heat from outside resources, flow rates including:   a first pair connecting the conjugate ends of the first   their and the second condenser and exchanging heat in a first exchanger (El) against the current,   a second pair connecting the conjugate ends of the second   their and the first condenser and exchanging heat in a second exchanger (E2) against the current, - a third pair substantially connecting the middle of the first   column to the second condenser and exchanging heat in a third   th countercurrent exchange (E3), and a fourth pair substantially connecting the middle of the second column to the first condenser and exchanging heat in a - 28 -   fourth exchanger (E4) against the current.   Machine according to claim 1, characterized in that the first   (Kd) and second column (Kg) cover a range of temperatures.   ture (To, T2g) with a common temperature zone (T1 T2), the heat sources, positive or negative, applied to a column between two given temperature values inducing in the other column, between the   same temperatures, a heat of opposite sign.   6 / Machine according to claim 1, characterized in that at least one point of a column, located in an end section of an element of   constituent heat transfer of said column, is connected to a cir-   vapor sampling furnace which carries steam at the homologous point of the reverse column, said circuit comprising a member (Tu, Co) for bringing the vapor pressure from its value at the sampling point to its value at the point of reinjection into said column, the machine comprising means (Li) for establishing a liquid flow rate between said sampling points and steam reinjection points, so as to obtain the equality of the liquid flow rates in the homologous sections of the associated columns.