BE476521A - - Google Patents

Description

       

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    "Improvements to refrigeration systems"
The present invention relates to a refrigeration system and more particularly to an absorption refrigeration system, suitable for use in air conditioning applications or in any application, in which a temperature above The freezing temperature of the water is desired, the invention also relating to control devices for controlling the operation of the system. It is understood that the present invention can also be employed in cases of low temperature refrigeration.

   In such cases, the system may be somewhat modified, in minor details, compared to the system used in air conditioning applications.

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   The main object of the present invention is an improved, economical absorption refrigeration system capable of more satisfactory efficiency and which
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 can be fa'tx'i <''. 11 1-:;:, 1: considered price; lL1ent lower had the systems proposed up to]? Î # z ± 3ClilÔo The invention also relates to a s7sr; c = ::; ¯ of Fif37i- ;; erat.LoL by atJ3Cd "j" 1 1 ij 3 'ù O iil pl? e ii é ">, l un tl fÎ $ - iq> C ùj -1 1 1- '(1.C; () - new trole, and 2 ^ i., r>. eC t: ¯O1'1 = 1c?, I.7E1 "W e ;, fW" it;

   .¯ t'c, - īux 'capacity, concentration and distribution of the. ^. solution, the temperature of the cooled water and the amount of refrigeration water directed through the elements of the system.



   Another object of the invention relates to a compact, economical absorption refrigeration system comprising a novel and efficient arrangement of the constituent elements of the system, which arrangement ensures increased efficiency of the system and reduces the space required by the system in service. .



   The invention also provides an absorption refrigeration system, comprising means for adjusting and adjusting system controls in response to the load imposed on the system.



   The subject of the invention is also an absorption refrigeration system, comprising safety devices against the non-functioning of system elements, the lack of electric current supplied to the system elements, the freezing of the solution. , freezing of chilled water, flooding of the generator, flooding of the system, and inability of the absorption medium to break up the solution.



   Another object of the invention consists of an absorption refrigeration system capable of providing conditioning agents or media of different temperatures.

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 annuities, wherein the temperatures of the agents or media so provided can be controlled independently of each other.



   The invention also relates to an absorption refrigeration system, comprising a control device, capable of allowing satisfactory operation of the system at higher concentrations of the solution in the generator.



   A further subject of the invention is an absorption refrigeration system, comprising a novel control device intended to regulate the circulation of refrigeration or condensation fluid through the tubes of the condenser and / or of the absorber.



   The invention also relates to an absorption refrigeration system suitable for air conditioning applications, in which the quantity of cooled water supplied to the air conditioning system and the quantity of cooled water returned to the air conditioning system. refrigeration system are balanced to prevent flooding of the refrigeration system evaporator.



   The invention provides an absorption refrigeration system comprising a casing, an absorber therein, an evaporator in the casing, a predetermined pressure being maintained in the casing, the system further comprising a second casing in the casing. which are a generator and a condenser.), a predetermined pressure different from that prevailing in the -crémière casing being maintained in the second casing, the casings being isolated from each other, and finally means for making circulate a solution between the envelopes.



   The present invention relates to an absorption refrigeration system comprising a casing

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 stretching horizontally and containing an absorber and an evaporator. A second horizontally extending envelope is disposed above the first envelope.
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  The second envelope contains a yenerator and a condenser placed above the generator. The absorber, the evaporator, the generator eb le> w <: o n d <n.s eL1 r are arranged in a closed circuit. Means are provided to extract a solupion from the '' -enerator c! ', To send).' R-e'ctc sol1 = ion to the absorber, as well as to circulate a solution from the aosorber to the generator. An a '' 'ent is sent to the evaporator, this refrigerant a, :: ent being cooled by projection in the evaporator. The
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 sprayed vapor, flow down into the absorber to be absorbed there by the solution.

   In I P: .- <Sn: 1.iaii #:> i>. , a substantially, identical quantity of value e:; t expelled because it boils, brought to the coi;: ie ;; seur, condensed and sent to the cooled water circuit. A trap is preferably provided to remove air or other non-condensable gases from the condenser.



   A control element or device is provided in the pipe connecting the absorber and the generator and serves to throttle the weak solution stream going
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 to the generator, This control element can be re- in response to the. te '.' tperat. '. ure of the cooled .refrigerant agent leaving 1.'é <ra>: iari <t, e; -ir., A control element or device is provided in the pipe;, lc vaoeur supplying 1-a steam to the tubes of the generator and the '.'; arranged, to control the quantity of steam pacsanb a t, # :. to # ..., -:;, the 'cubes, <iw ç <; 1;> 1 # rat> *: =:!, * o #; second, element.>, a <: c> i; <:.; .. É-Lz may have rej>; 1 <µ é; n response the 1 cure of the strong solution leaving the generator.

   Readjustment valves are provided for the vapor control element and can be used to adjust the said. element, in order to

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 reduce the concentration, for example, of the solution in the event of a partial charge. The quantity of refrigeration water passing through the tubes of the absorber and the condenser is regulated by a control element or device arranged in the condensate water pipe. This control element can be adjusted, if desired, in response to the temperature of the condensed vapor leaving the condenser and directed to the evaporator.



   The accompanying drawings illustrate a preferred embodiment of the invention:
In these drawings: FIG. 1 is a schematic view showing the flow of solution through the various elements of the refrigeration system; fig. 2 is a side elevational view of the absorption refrigeration device according to the invention; fig. 3 is an end view of the device shown in FIG. 2; fig. 4 is a section of the casing comprising the absorber and the evaporator; fig. 5 is, partially in section, an elevational view illustrating a suitable spray device for supplying the coolant to the evaporator. fig. 6 is a section taken along line 6-6 of FIG. 5;

     the. fig. 7 is, on a larger scale, a fragmentary section intended to illustrate the position of the nozzles in the spray device of FIG. 5; fig. 8 is a section through the nozzle shown in FIG. 7; fig. 9. is a plan view of the nozzle shown in figs. 7 and 8; fig. 10 'is a section of a modified spray device;

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 fig. 11 is a section swi. <; -. Ioe i 1 * line 11-J.l of fig. 10;
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 fig. 12 is a view in: ole12l of the device; the spraying of the absorber;

   fig. 13 is a side elevation view.;. = Spray device of FIG. 12; fig. 14 is an end view of the spray device of FIG. 12;
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 fig. 15 is an elevational view of a heat echa.ng; eur; fig. 16 is a section taken along line 16-16 of FIG. 15. FIG. 17 is a longitudinal section of the heat exchanger of FIG. 15; fig. 18 is an elevational view showing the manner in which the condenser reservoir is disposed in the casing; fig. 19 is a section taken along line 19-19 of FIG. 18; fig. 20 is a section taken along line 20-20 of FIG. 18;

   fig. 21 is an elevational view illustrating the way in which the bleeder pipe is supported in the absorber: FIG. 22 is a section showing the. how attached
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 a 1 (KE;: M: xm: x -! ';) a sure is for; born between the c1.:Í to the trap; collector the absorber and the: t, 'tJ: eX: t: C ill .; fig. 23 is a schematic view illustrating the
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 position and operation of the various control devices of the Jystér <ic;

   the ire 21w is uned. diagram illustrating the operation of the refrigeration system and how the cycle can be adjusted to allow operation at part load,

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 Fig. 25 is a schematic view illustrating a control device permitting operation at a higher concentration of the solution for partial loads. fig. 26 is a schematic view illustrating a modified control device; fig. 27 is a schematic view of an absorption refrigeration system comprising a modified control device; fig. 28 is, on a greatly enlarged scale, a fragmentary section showing a modified control device;

   and fig. 29 is a fragmentary schematic view of a modified absorption system, illustrating how two temperatures can be obtained.



   The apparatus, shown in the accompanying drawings comprises a frame consisting of a base 2 and supports 3, fixed to the base and intended to support drums or envelopes 4 and 5 extending horizontally. The casing 5 is preferably disposed above the casing 4. The casing 4 contains an absorber device 6 extending longitudinally and an evaporator device 7 also extending longitudinally and disposed above. above the absorber 6 in the upper part of the said envelope 4.



   The casing 5 contains a generator device 8 extending longitudinally and a condenser device 9 extending longitudinally and arranged above the generator 8 in the upper part of the casing 5.



  A weak solution is withdrawn from absorber 6 by pump 10, through line 11, and is sent to generator 8 through lines 12 and 13, through heat exchanger 14 and line 15. A solu -

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 strong tion is extracted 'from,: â'l'r'r'.iEL: r uar a cor'.duice 10 and brought, by a tro.?-Jlei device; or by tc- bordering 17, by a con41, toi:, <; 16, par .qLCiIRYLf; 6 ',: heat 14 and,? Ar a CpI7dül.tF 19,,' <an ejector.: 0, which sends the strong solution, through a pipe 21, to a spray device 22, This is to spray the solution onto the tubes 23 of the absorber 6. It should be noted that the line 19 is bent for a purpose, which will be described below.

   The thermal devices described above are in an exchange / mutual relationship thanks to the heat exchanger 14 described below.



  The solution overflow or overflow device 17 serves to prevent the solution in the generator 8 from rising above or falling below a predetermined level, as will be described. below.



   The term "weak solution" is used herein to define a solution containing a large amount of coolant such that this solution has poor absorption properties. The term "strong solution" denotes, on the other hand, a solution, which is relatively deficient in refrigerant and, therefore, a solution, which has increased properties of absorption of refrigerant.



   Various combinations of coolant and absorbent can be used in the present system.



  A solution consisting of lithium bromide and water is excellent. Other saline solutions can be used, if desired, in the system. When the system is operating at high temperature (above freezing temperature) a solution of lithium chloride and water or a solution of sodium hydroxide and water, for example, ¯, can be used. When the

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 system is used to achieve low temperatures, ammonia can, for example, be used as a refrigerant.



   A pump 24 brings cooling or condensation water through a pipe 25, to the tubes 23 forming the coil of the absorber 6. The condensation water, after passing through the tubes of the absorber, is directed , through conduits 26, to tubes 27 forming the coil of the condenser 9. This is, of course, a proposed arrangement, and it should be understood that the water can be passed in the reverse direction or in parallel pipes through the tubes 23 and 27 of the absorber and the condenser. Any suitable means can be provided to supply the condensation water. The condensed water leaves the tubes 27 of the condenser 9 through a pipe 28 and can be directed to a cooling tower or to an evacuation.



   The cooled water leaves the evaporator 7 via a pipe 29 and is circulated through the heat exchanger coil (not shown) of an air conditioning system, by means of a pump 30. L The refrigerant (/ cooled) water medium is returned from the air conditioning system, via a pipe 31, and is sprayed, by means of the spray device 32, into the evaporator 7. The pressure in the evaporator. shell 4 is such that the coolant sprayed into it is spray-cooled, the vapor moving downward to be absorbed by the solution in absorber 6, while the cooled solution is cooled in the evaporator 7 and can be removed therefrom, as described above, through line 29.



   A line 33 serves to send the condensate coming from the condenser 9 to the evaporator 7, the condensate passing through

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 1: through a pre-cooler device .- '4, rli.si'> os: 1 in -The pipe, 3 ;. The condensate precooler 34 consists of an assl,;: l; laf "(', lE, places pipes, r., I 1 <.: i: el we pass a; to: lî.l.eix or agent of 2 "thermal efr01nI1SSeī.r'.nt in exchange relation x., Dcx- with the vaneur. The condensate cooler 34 has. The shape of a loop, so as to achieve a seal safe liquid
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 between the envelopes: ', A \., 1 :,;. "ce ([; l,' f'.l'ulE: i,! ie f7 <'1111ï; f.tllr different pressures in the said envelopes, without steam escape.



     A suitable purging device 35 is provided to purge the condenser 9 and the absorber 6 of the air or of the other non-condensable gases which they contain. The purger 35 can operate intermittently or continuously, as desired.



   As shown in figs. 1 and 4, the casing 4 contains the absorber 6 and the evaporator 7. The evaporator 7 has horizontally extending side walls 36 and end walls (not shown), which side and end walls serve to form a box-shaped compartment 37, supported by the end walls 38 of the casing 4. Eliminators 39 are disposed in the vicinity of the top of the combartment 37 and extend longitudinally with respect to this compartment. The eliminators 39 serve, on the one hand, to prevent drops of water entrained by the sprayed vapor from being transferred to the absorber 6 and, on the other hand, to return these drops to the compartment 37.



   The spray device 32, disposed between the eliminators 39, receives the refrigerant (chilled water or the like) returning from the air conditioning coil and discharges it into the compartment 37. A portion 40 of the compartment 37 extends. down as shown in fig. 4, this arrangement allows

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 both the cooled water can be easily drained from compartment 37 via line 29, without it knowing the need to maintain a high water level in compartment 37.



   As shown in fig. 5, the spray collector device 32 consists of a / or main collector tube 41, which extends along the compartment 37. The /
41 is preferably provided with several fishtail nozzles 42 arranged on either side of the vertical plane passing through the axis of tube 41. Nozzles 42 occupy a position such that the jets are in a vertical plane. This particular arrangement provides an adequate water surface for evaporation and does not constrain the vapor moving upward. The arrangement of the jets results in reduced entrainment of liquid drops by the vapor.



   The part 41 preferably comprises an inner pipe 43 (see fig. 7) provided with openings 44. The pipe 43 is arranged in an outer pipe 45 carrying nozzles. fishtail 42. The nozzles are arranged. on either side of the vertical plane passing through the axis of the pipe
45 in the bottom of the pipe 45. The openings 44, formed in the pipe 43, can be arranged on either side of the vertical plane passing through the axis of this pipe. This arrangement makes it possible to reduce the approach speed of the collector water or other refrigerant entering the / 41 and ensures an adequate and equal distribution thereof among all the nozzles 42.



   If desired, the nozzles 42 can be arranged at a certain obliquity, so as to allow the jets coming from them to meet the walls.
36 of compartment 37. If desired, the nozzles can be adjusted so that the jets are

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 absorbed by the water in the bottom of compartment 37. In either case, the arrangement reduces the amount of entrained liquid and allows for spray cooling without interfering with the pre-sprayed vapor.



   In Figures 10 and 11, applicants set forth a modified form of spray arrangement, in which fishtail nozzles are eliminated.



  Instead of these nozzles, several openings 46 and 47 are made in the pipe 11,), the openings of each pair forming an acute angle with a perpendicular line drawn between them and extending from one 'The other. The spray device thus produced reduces the quantity of entrained liquid and enables spray cooling without the intervention of the sprayed vapor.



   The absorber (see fig. 4) comprises a coil da tubes or pipes 23, which is arranged between the walls of the casing 4, so as to allow the steam to pass between the tubes 23 towards the bottom. The tubes 23 of the absorber 6 are preferably placed in staggered rows, as illustrated in FIG. 4, in order to give rise to a uniform distribution of the vaporized liquid over the entire surface of the tubes. The tubes or pipes 23 are preferably arranged so as to form an isosceles triangle or. equilateral, with the major axis of the corresponding rhombus extending horizontally.

   An arrangement, such as that indicated above, allows each vertical row of tubes 23 to receive a substantial amount of vaporized liquid, which ensures uniform distribution and complete wetting of the surfaces of the tubes.



   The spraying device 22 used to spray the strong solution onto the tubes 23 of the absorber 6 is shown in FIGS. 12, 13 and 14. The spray collector device 22 comprises a / 48, by

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 which the strong solution is extracted from line 21.



   / or manifold From the main pipe / $ 4, the strong solution passes through one or more pipes 49 fitted with conical nozzles 50 making the desired angles with respect to a horizontal plane, so as to allow each nozzle to serve a larger surface of the coil . Each cone 50 evenly distributes the jet over a transverse surface of the tubes of the absorber. Such an arrangement of nozzles allows the solution to flow horizontally along the tubes 49 as well as between the tubes, which increases the rate of heat transfer and allows for uniform wetting of the absorber coil, while requiring less. of space between the spray device and the tubes.



   The vapor formed by the blast cooling of the refrigerant in the evaporator 7 moves in an upward motion into the evaporator 7, passes through the eliminators 39 and then goes downwards to the outside and around compartment 37, to be finally absorbed by the strong solution projected onto the tubes of the absorber. The strong solution sprayed onto the absorber tubes is cooled by the cooling water passing through the absorber tubes 23, so as to aid rapid absorption of the refrigerant.

   The tubes 23 are preferably arranged at a certain distance from the lowest point of the casing 4, in order to provide adequate space for the storage of liquid in the casing 4 in the event of an increase in volume of the casing. solution.



   As described above, the generator 8 and the condenser 9 are placed in the casing 5, which is fixed, by means of the frame of the assembly, in a position situated above the casing 4. Such an arrangement of the condenser and generator eliminates external steam connections and increases the efficiency of the system.

   The casing 5 is provided with a trough 51 extending longitudinally.

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 The weak solution passes through it. Openings 52 are made in the casing 5 at intervals such that the weak solution is evenly distributed over the entire length of the generator. This distribution of the weak solution throughout the generator improves the efficiency of the device, since the necessary reheating is eliminated.

   By distributing the weak solution in this way at several points along the horizontal generator, the preliminary heating period is reduced until it is less than that necessary, if all the weak solution is passed through one end of the penetrator and if it is allowed to flow alongside the generator, since it has an increase in heat transfer to the liquid as a result of the turbulence. The generator is heated so as to drive the coolant out of the weak solution by means of steam directed through the tubes 53 of the steam line 54, the steam being discharged from the tubes 53 through the steam line 55.



   The condenser 9 is arranged longitudinally with respect to the casing 5 above the generator 8. The condenser 9 is, preferably, freely mounted on supports, so as to obviate the disadvantages which could arise from a contraction and from unequal expansion of said supports. The condenser 9 consists of a tank or longitudinal compartment 56 in the form of a box containing a coil formed of tubes 27. Refrigeration water supplied from the line 26 passes through the tubes 27 and is discharged through the line 28.

   Eliminators57 are placed on both sides of the condenser 9 and serve to prevent the entrainment of drops of liquid, which could be transported by the steam moving in an upward movement, from the generator / towards. the condenser 9.

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   As described above, the condenser reservoir 56 is supported in such a way, in the independent casing 5, that it permits contraction and expansion !. The condenser reservoir 56, the baffles and the eliminators 57 form an independent assembly, which can be slid freely in the casing 5 to rest there on supports. As illustrated in figs. 18, 19 and 20, end plates 58 and 58 are welded to the ends of the casing 5. Each end plate has a shape such as to conform to the contour of the reservoir 56.



  About the middle of the length of the casing 6 is provided a support plate 59, which can be welded to the casing. The plate 59 is provided with an extension 60 the shape of which corresponds to that of the contour of the reservoir 56 and which is intended to serve as a support for the reservoir 56. The plate 59 is also provided with an extension 61, which constitutes, in fact, a sheet metal tube, arranged. to support at least some of the generator tubes. When the reservoir 51 is placed in the shell 5, the reservoir 56 is slid inside the shell and one of its ends rests against the end plate 58. The longitudinal and central portion of the reservoir 56 rests against and is supported by plate 59.

   The opposite end of the reservoir rests against and is supported by the second end plate 58 '. It should be noted that the reservoir 56 is not attached to its supports, but is held in place by them. As the end plates conform to the contour of the reservoir 56, such a method of assembly allows the reservoir 56 to contract and expand independently of the shell 5.



   When the generator is put into service, the weak solution is distributed in this generator into a plurality of

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 ity of points, as described above. Part of the refrigerant present in the weak solution is expelled by vaporization, goes to the top of the casing 5, that it passes through the eliminators 57, and is condensed in the condenser 9. After its reassage in the condenser 9 the aforementioned part of the refrigerating agent is brought through line 33 to the pre-cooler 34 and is finally returned to the evaporator 7.] This strong solution remaining in the generator 8 is extracted therefrom by line 16, as stated above.



   To help prevent the build-up of too high a liquid level in generator 8, a line 62 connects the generator to the overflow device 17.



  When the level of the liquid in the generator 8 increases a certain part of this liquid is drained through the line 62 to the overflow device 17, which returns the solution, through the line 18, etc., to the absorber. 6. The liquid level in the generator never drops below that of the overflow, since liquid is trapped in the generator.



   In order to achieve highly satisfactory operation, it is desirable that the capacity of the system be changed as soon as a change in load occurs. The temperature of the cooled water can be used to indicate a change in the load. A decrease in temperature of the load, from a determined point, indicates that the load imposed on the system has decreased.



  It should be understood that means other than the temperature of the cooled water may be used to indicate a change in the load. As the temperature of the cooled water leaving the evaporator decreases, the capacity of the system can be correspondingly decreased by restricting the volume of strong solution passing to the absorber.

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   For this purpose, (see figs. 1 and 23) a valve 65 is placed, preferably, in the line 12 between the pump 10 and the ejector 20. It should be understood that the valve 65 can be placed in other places. places, if desired. The valve is preferably disposed in the line 12 at a point between the pump 10 and the junction of the line 12 to the line 13. The valve 65 can be adjusted by means of a thermostatic control device 66. controlled by a probe 67 placed in the pipe 29 or in the vicinity thereof.

   When the temperature of the cooled water passing through the pipe
29 decreases, the fluid contained in the probe 67 contracts and actuates the thermostat 66, which tends to move the valve 65 to a closed position, thereby decreasing the quantity of weak solution which is sent to the generator 8 by c. pipes 12, 13 and 15.



  The movement of the valve 65 to a closed position decreases the amount of weak solution moving towards the ejector 20 and this in proportion to the decrease in temperature of the cooled water. The reduction in the amount of weak solution flowing to the ejector 20 reduces the rate of passage of said solution through the nozzle of said ejector and, therefore, a smaller amount of strong solution is entrained or induced. The throttling action of valve 65 therefore reduces the total amount of solution flowing to absorber 6. The capacity of absorber 6 is controlled by the diminished wetting action produced by the decrease in water content. total solution and by the reduction of strong solution according to the load imposed on the system.



   A valve 68 is provided in the steam line
54 to adjust the quantity of steam passing through the tubes 53 of the generator 8, depending on the load imposed on the system. The valve 68 is actuated by a device

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 thermostatic control éi9 controlled by a: sodium hydroxide 70 placed in the pipe 16 or in the vicinity thereof, connecting the generator 8 to the spout device 17. When the load decreases and the quantity of solution coming from the generator 8 decreases , the temperature of the strong solution in the pipe increases.

   Such an increase in temperature indicates that too much steam is being supplied to the generator: 3, which causes the solution to heat up and increase its concentration to an unnecessary degree, and indeed to an undesirable degree. The probe 70 which responds to the temperature of the solution in the line 16, actuates the thermostatic control device 69 so as to move the valve 68 to a closed position, which causes a decrease in the quantity of. steam passing through tubes 53 of generator 8 until it is in equilibrium with the new load.



   The quantity of refrigeration or conditioning water, which passes through the tubes 23 of the absorber 6 and the tubes 27 of the condenser 9, is controlled by means of a valve 71 placed in the pipe 28. The valve 71 ; is actuated by a thermostatic control device 72 controlled by a probe 73, placed in the condensate line 33 or in the vicinity thereof. If desired, the valve 71 can be disposed in lines 25 or 26. In fig. 23, this valve is arranged in the pipe 26. If cooling water is passed in parallel through the tubes 23 of the absorber 6 and the tubes 27 of the condenser 9, a similar valve can be provided in the pipes supplying condensate to the absorber tubes or to the pipe through which the water is withdrawn.



   The concentration of the strong solution leaving the

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 generator 8 depends on the temperature and the pressure in the casing 5. The pressure in the casing 5 can be maintained thanks to the condenser 9. The pressure in the casing 5 depends on the condensing temperature of the condenser 9. A decrease of the temperature of the steam condensate in line 33 indicates that too much condensation water can circulate in the tubes of the condenser 9. The probe 73 acts on the thermostatic control device to force the valve 71 to decrease the quantity of condensed water circulating in the tubes of absorber 6 and condenser 9. The condensing temperature can be controlled by adjusting the temperature of the refrigerating water within the desired limits.

   Thanks to the valves 68 and 71, the temperature and the pressure of the solution present in the casing 5 are controlled and, therefore, there is an indirect control of the concentration of the solution.



   While it is generally desirable to keep the concentration of the solution constant, regardless of the temperature and pressure conditions in the envelope 5, it may in some cases be desirable to decrease the concentration of the solution. partial load solution. For this purpose, a readjustment device is provided for changing the control point of thermostat 69. This readjustment device is not limited, in its use, to a decrease in the concentration of the solution to charge by. - tielle. Thus it can be employed, if desired, to maintain the concentration of the solution at any desired level or within any desired limits.

   The device illustrated in figs. 1 and 23 can, if desired, be replaced by another control device-. Intended to control the concentration.

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   tion of the solution. The control point or interval e
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 of the thermostat, 9 can ê'.ri: modified by lu r> rl;, 3s: O ;, 1 qa; ¯Lr in line 74 connected <1 to the air line '7), which ct -'-, o, -ine the valve. 5). The; -li: 5q: ossit'i 'die réa.juste'.rient thus provided is used to modify the:, control anoint.

   (read thermostat 69, when the air pressure in line 75 decreases and .: readjust the control point of thermostat 69 according to the desired temperature of the solution leaving the generator and the pressure in the chamber. veloppe 5, thus indirectly reducing the concentration of the solution to the desired degree. Instead of the air duct 74, an air duct 76 is provided, connected to the air duct 77, which actuates the valve 71 , to obtain the desired readjustment control.

   It is desirable to stop the machine when the solution pump 10 fails, for example, to prevent damage to the remaining elements of the system. As shown in fig.



  23, there is provided a pressure switch 78 responsive to the pressure created by the pump 10. When the pump 10 is turned on, the pressure on the pump discharge actuates the pressure switch, which in turn actuates the pressure switch. in turn, causes an automatic air shut-off alve 79, provided in the main air duct 80, to open, which allows air to be supplied to the various elements of the control system. , as indicated above. If during operation the pump 10 ceases to operate for either reason, the loss of discharge pressure activates the pressure switch 78, / in turn, brings about the automatic waltz. air interruption 79 to close.

   Closing valve 79 interrupts the supply of air to the various control devices, allowing them to return to the normal position to close.

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 valves 65, 68 and 67, which prevents the passage of solution through the system, the passage of steam through the generator tubes and the passage of condensate water through the absorber and condenser tubes as shown in fig. 23. A filter 81 and a pressure regulator 82 may be provided in the main air line 80. These elements are well known and need not be described in detail.



   As shown in fig. 23, the various thermostatic controls 66, 69 and 72 are connected to the main air line 80 and can be actuated in response to a predetermined air pressure prevailing in that line. The various probe control devices 67, 70 and 73 serve to control the operation of said thermostats and to regulate the operation of the valves 65, 68 and $ 1 in response to the various conditions which arise during the operation of the system. In addition, various functional and safety control devices can, of course, be provided, as will be shown below, to achieve the most efficient and effective operation of the present system.



   The refrigeration cycle of the absorption system and how it is affected by the various control devices is shown in diagrammatic form in fig. 24. This figure shows the refrigeration system at full load, together with the temperatures of the cooled water supplied to and leaving the evaporator, the steam supplied to the generator and the refrigeration water entering the evaporator. absorber and leaving the condenser.



   With reference to fig. 24, it should be noted that the ordinates indicate the concentrations of the solution in percent by weight of lithium bromide,

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 which is the preferred absorbent agent. The abscissa indicates the vapor pressure of the water in the solution in -The current lines refer to the constant temperatures of the solution, which correspond to the pressure and the concentration at any point in the diagram under saturated conditions.



  Any point on the horizontally projected diagram of the zero concentration line indicates the temperature of the water in equilibrium with the solution at that point.



   Under the full load conditions for which the system is intended, it should be noted that the temperature of the steam supplied to the generators is approximately 270 degrees, the temperature of the condensing water entering. in the absorber is 80 degrees F, with which the temperature of the condensed water leaving the condenser was raised 8.90 degrees F. In other words, the temperature of the condensed water was raised by its passage through the absorber and the con- dancer. The temperature of the cooled water entering the evaporator is about 55 degrees F., this water being spray-cooled to a temperature of about 45 degrees F.

   (temperature of the cooled water leaving the evaporator). The Freeze Line Fr serves as a general indication of the temperature and concentration at which the absorbent begins to crystallize and precipitate from solution. The refrigeration cycle is shown in solid lines.

   Point A is considered, for purposes of illustration, to be the start of the cycle and indicates the point at which the mixture of weak solution and strong solution is formed in the elector. The solid line A-B indicates the passage of the solution from the ejector 20 to the heat exchanger

 <Desc / Clms Page number 23>

   14, passing through absorber 6. The dashed line B-A is used to show the weak solution, at lower temperature, returning to point A and mixing with the strong solution at that point. At point B (where the weak solution enters the heat exchanger) it should be noted that the temperature of the solution is. approximately 95 degrees F. and the pressure has been reduced.



   The ordinate B-C illustrates the passage of weak solution through the heat exchanger. The temperature of the weak solution increases as it passes through the heat exchanger. The continuation C-D of the ordinate B-C serves to illustrate the increase in temperature during the pre-heating period in the generator (the increase in temperature required to bring the solution to its boiling point in the generator). The abscissa DE illustrates the evaporation of the solution in the generator, at a constant pressure, which evaporation is accompanied by an increase in temperature and concentration of the solution.

   The order EF illustrates the passage of strong solution through the heat exchanger.;: Showing the decrease '. Of temperature and pressure caused by its dte- thermal relationship' changes' with the weak solution (indicated by the ordinate BC). The line FA (in broken lines) indicates the passage of strong solution from the exchanger to the ejector (point A), which is mixed with the weak solution of the absorber, as indicated by the dashed line BA.



   As described above, the diagram illustrates the refrigeration cycle under defined conditions (operation at full load). If, for example, the load imposed on the system decreases, the temperatures of the condensed water and the steam remaining constant,

 <Desc / Clms Page number 24>

 the cycle shown by the solid lines will change by a basket corresponding to the change in load. Such a decrease in load is indicated by the dashed lines on the right side of the diagram.



   When the load imposed on the system has decreased, the probe 67, which reflects this change in load, actuates the thermostatic control device 66, which has the effect of moving the valve 65 to a closed position, so that there is a decrease. low solution flow to the generator and similarly decreased flow of mixed solution to the absorber. Since the flow of steam through the generator is sufficient to maintain a desired temperature of the outgoing strong solution, at olein load, the temperature and concentration of the refrigeration solution is increased.

   Such an increase in temperature is reflected by the probe 70, which actuates the thermostatic control device 69, so as to move the valve 68 to a closed position, which decreases the quantity of steam supplied to the generator as well as the pressure. maintained in the casing 5, so that there is a further increase in the concentration of the solution leaving the generator. These temperature and pressure changes were illustrated by dashed lines / dashes E-Ex and Ex-Ey. In reality, the lines connecting points E and Ey could just as well be indicated by a single line, since the effects illustrated by these lines are, in fact, the result of two different forces.

   The line has been illustrated by two components to show more clearly that a number of factors are affected by the decrease in. load applied to the system.

 <Desc / Clms Page number 25>

 



   The ordinate Ey-Fy illustrates the passage of strong solution, at partial load, through the heat exchanger. It should be noted that such a line not only comes dangerously close to the freezing line, but can actually cross it. Thus, a very dangerous and very unsatisfactory operating condition is created by the tested part load operation. It is essential that such a line, indicating the passage of strong solution through the heat exchanger, be moved to the left rather than to the right of the diagram, in order to move the point away.
F or its corresponding points on the freeze line.



   The aforementioned readjustment device can be used for this purpose. When the load decreases, the probe 67 activates the thermostat 66, so that there is a decrease in the air pressure prevailing in the duct 75, which has the effect of moving the valve 65 to a position closed. The decrease in the air pressure in line 75 is reflected by line 74 in thermostat 69. Decreasing the air pressure adjusts the control point of thermostat 69, so as to lower the temperature of the solution, to which it is sensitive. This decrease in solution temperature would be reflected on the diagram by moving the line, indicating the strong solution passage through the heat exchanger, to the left, away from the freeze line.



  The readjustment device sets or adjusts the thermostat 69, so as to actuate the valve 68, for partial loads, at temperatures different from the temperature to which it is sensitive, when full load conditions prevail.

 <Desc / Clms Page number 26>

 



  The readjustment device can. to be used
 EMI26.1
 "90ur adjust the thermostat> to i ', in order to think the increase in tBE (17" iai, lil e of the solution leaving the generator, the decrease in pressure in envelope 5, factors (he both would serve to increase the concentration of the solution leaving the generator, the aforementioned adjustment citing, in addition,

   such that it gives another safety or over-safety factor capable of ensuring safe operation under partial load conditions. Such an adjustment changes the temperature to which the thermostat 69 is sensitive.



  Obviously, when referring to the diagram shown in fig. 24, that a change in temperature will compensate for the change in pressure at part load. Consequently, under partial load, after readjustment of the control device 69, point E of the cycle becomes point E ', which indicates the pressure and temperature of the solution leaving the generator.



   If the refrigeration water temperatures are kept constant and the same amount of refrigeration water is passed through the absorber tubes, the limits of the. cycle are, under these conditions, enlarged to an unnecessary degree, so that the refrigeration capacity is increased at a time when it should be decreased.

   In addition, widening the cycle limits is undesirable, since it can cause abrupt and irregular variation of the control devices. This condition is indicated by the dashed lines.
 EMI26.2
 terrompus shown to the left of the diagram shown in fig. 2L, connecting the points ûT, i; J :, D1 and D '
Under the conditions described above, the temperature of the steam condensate leaving the condenser will decrease. The decrease in condensate temperature

 <Desc / Clms Page number 27>

 reflected by probe 73 will cause thermostat 72 to be actuated, so as to move valve 71 to a closed position, reducing the flow of condensed water through the absorber and condenser tubes.



   The change in temperature is shown by the dashed line. It should be noted that the temperature of the condensed water entering the absorber remains at 80 degrees F, while the temperature of the condensing water leaving the condenser has been raised to 100 degrees F.



   The decrease in the quantity of condensed water supplied to the absorber and to the condenser consequently shifts points B and Dx to the right towards points B 'and D', "tightening" in effect the limits of the condenser. cycle, to allow more efficient and satisfactory operation at part load.



   The partial load refrigeration cycle is illustrated by the phantom lines, connecting points A ', B', C ', D', E ', and F'. These points correspond, in general, to points A, B, C, D, E and F illustrating the operation of the system at full load. Note that the cycles shown have a similar outline, but the cycle illustrating the operation of the system at part load is even further away from the freeze line Fr (the hazardous condition).



   The various control devices, which automatically come into action to effect the changes specified above in the refrigeration cycle, give immediate and exact control of the operation of the system from a total load, for example 150 tons. refrigeration, up to partial loads, in particular of the order of 10 tonnes.

 <Desc / Clms Page number 28>

 
 EMI28.1
 



  The control devices j => e = 1;. <And. V; nt economical operation at any partial load within .1: "11-G6S specified more rlaL * 1Jj.cn than 1; CLiB.i" IEI111Tte 1: iJnir.-? S. la: ¯L?;. 24 illustrates the refrigeration cycle at a given partial temperature, it must evre F27t!; It U that the control Jisç> Jsit; 1 ": s control works .- 'ta;> 10;: ia: =, 1- quetnent 4îoLt1 adjust or correct the cycle to any cue.¯the condition df '; ch8X "e partial da:) :::; .1 <::: Lil: lites described above.



  The device of or. de cir ± borrdcr: 18ct 17 helps to control the distribution of the solution in this system, since it ensures at all times that a minimum quantity of solution is maintained in the generator.



  The efficiency of the ejector 20 is controlled, to some extent, by the column of strong solution held in line 18 and by the pressure maintained in casing 5.



   As described above, the pressure prevailing in the casing 5 can be regulated by reducing the flow of condensation water passing through the condenser 9. The concentration of the solution in the generator 8 is
 EMI28.2
 maintained approximately at the desired level, by the automatic control of the temperature and the pressure maintained in the enclosure 5.

   The concentration of the solution in the absorber 6 can be changed or influenced by reducing the flow of cooling water through the tubes of the absorber. readjusting the steam control device decreases the temperature of the solution leaving the generator and, together with the control of the refrigeration water to be supplied to the machine, indirectly controls the flow of the solution. Tightening the concentration limits of the part-load solution, as described above, prevents

 <Desc / Clms Page number 29>

 decreasing the temperature of the cooled water will move valve 65 too far to a closed position.



   In order to allow satisfactory operation of the system at higher concentrations of solution in the generator, part of the heat exchanger 14 can be bypassed. Fig. 25 schematically illustrates a suitable device for partially bypassing the heat exchanger. A pipe 85 is provided connecting the pipe 12 to a desired loop 86 of the heat exchanger 14. A manually operable valve 87 is disposed in the pipe 85. A similar valve 88 may be disposed in line 12, as shown. When it is desired to avoid or exclude a certain part of the heat exchanger surface, waltz 87 can be opened and valve 88 "choked" or closed to allow weak solution to pass through line 85 to the exchanger. of heat, without going through all of it.



  The solution leaving the heat exchanger at a higher temperature, which will allow operation at a higher concentration / of the solution leaving the generator, without danger of approaching the freezer line, as shown schematically in FIG. 26, a pipe 89 bypassing the condenser 9 may be provided to allow a portion of the condensation water passing through the pipe 26 of the absorber 6 to avoid the condenser 9. A valve 90 may be provided. disposed in the deregulation 89, to regulate the quantity of refrigeration water passing through the condenser 9 and the bypass 89.

   The flow of refrigeration water through the condenser and absorber can

 <Desc / Clms Page number 30>

 be modified to achieve the desired operation of the condenser and absorber.



   The trap 35, shown in fig. 1, serves to remove the non-condensable gases from the absorber and the condenser. This trap 35 comprises a casing or housing 91 containing a condensing coil 92 'through which the condensate water is passed, ion. A steam line 93 is connected to the housing 91, as in FIG. 1, and an ejector is placed in line 93.



  A nurgor pipe 95 extends longitudinally in the absorber 6 and has openings for sucking in the air or non-condensable gases collecting in the absorber 6. The pipe 95 is connected, by a pipe 96, to the air. The ejector 94 - a ball valve 97 is provided in the line 96, to prevent liquid from being drawn into the trap when it is in operation.



  Passage of vapor through ejector 94 entrains air and other non-condensable gases from absorber 6 through line 96, when waltz 97 is open. Steam and entrained gases are carried in housing 91, where a large part of the steam condenses as a result of its cooling by the water flowing through coil 92. Housing 91 is also connected to condenser 9. through line 98. The pressure in housing 91 is less than the pressure in housing 5. Consequently, air and other non-condensable gases flow to housing 91 through line 98. A valve 99 is disposed in the pipe 98, so as to allow the latter to close when desired.

   Likewise, suitable valves (not shown) may be disposed in the steam line 93 and in the water line 100 described below.

 <Desc / Clms Page number 31>

 



   An auxiliary water-pipe 101 is provided, in which is placed a water ejector 102 connected to the housing 91 by a pipe 103. The passage of water through the ejector 102 entrains the liquids and gases in the housing 91, thus ensuring their removal from the system. The steam and water used to operate the trap may be obtained from the same supply sources as those used to supply the steam generator and the absorber and condenser with refrigeration or condensation water.



  The described trap can operate intermittently or continuously, as desired.



   It should be noted that the housing or condenser 91 of the trap 35 is disposed some distance from the absorber 6. Such an arrangement of the trap 35 is of particular value when, as occurs in certain circumstances, the level of the liquid. in the absorber 6 rises above that of the bleeder pipe 95. The ejector 94 is so arranged that, under these conditions, it cannot raise the liquid to a sufficient height to remove a part of the solution from the system, but is adequate to remove air and other non-condensable gases from absorber 6, when the level of liquid in the absorber is such as to allow these gases to be removed by the absorber 6. 'intermediate the trap pipe 95.



   Figs. 21 and 22 illustrate how the bleeder pipe is disposed in and secured in absorber 6 so as to prevent any leakage from the absorber to the ambient atmosphere. The purger pipe 95 extends along the absorber 6 and is supported at one end of the absorber by means of a pad

 <Desc / Clms Page number 32>

   104 welded to the casing 4. The end of the pipe 95 rests on the bushing 104 and is supported by it but not attached to it. At the opposite end, the trap pipe 95 passes through the wall 105 of the casing 4 and through the wall 106 of the water tube 107. An opening is made in the wall 105 and is threaded to receive a socket 108. welded to pipe 95.

   When the bleeder pipe is assembled into the structure, the socket is coated with a suitable sealant and is screwed into the threaded opening made in the wall 105, this socket thus serving to close and seal the openings in the wall. absorber and main tube / or collector pal / 107. In the wall 106 of the tube 107 is formed an opening, through which the tube 95 passes. At least part of the wall of said opening is threaded to receive a plug 109. A packing ring 110 is arranged. around the pipe 95 in the aforementioned opening and is compressed in place by means of the stopper, so that a perfectly tight seal is obtained between the pipe and the ambient atmosphere, which prevents water leakage during machine operation.



   It should be noted (refer to fig. 1) that the pipe 19 has a part arranged in the form of a loop 19 '. The ejector 20 is disposed in a plane located below the plane in which the heat exchanger 14 extends. The loop 19 'serves to prevent the heat exchanger 14 from drying out during the operation of the machine, even if the liquid level in the line 18 decreases excessively. The loop 19 'serves to ensure, at all times, the presence of an adequate quantity of strong solution in the heat exchanger 14 for heat exchange purposes.

 <Desc / Clms Page number 33>

 
The heat exchanger 14 is shown in figs.



  15, 16 and 17 'The heat exchanger 14 has several pipes 111 connected to each other and intended for the passage of strong solution. Several smaller pipes 112 gathered in a bundle, for the passage of weak solution from the absorber 6 to the generator 8, are arranged in each of said pipes 111. The pipes 112 are kept spaced apart from each other by means of to wires arranged at intervals along these pipes. We see in Figures 16 and 17 that son'113 are arranged around. inner pipe 112. Several pipes 112 are disposed around the inner pipe 112 and spaced threads 114 serve to keep these pipes spaced from the inner pipe 112. Several pipes 112 are disposed around the preceding layer of pipes and spaced threads 115 serve to keep these pipes spaced from the inner pipe 112. Several pipes 112 are disposed around the preceding layer of pipes and spaced threads 115 serve to keep them. maintain said pipes in the desired position.

   The threadlike supports thus provided allow the spacing of the pipes 112 from each other, which ensures an adequate heat exchange relationship between the strong solution passing through the pipes 111 and the weak solution passing through the pipes 112 The strong solution enters the heat exchanger 14, at point 116 connected to the pipe 18 and leaves it at the point 117 connected to the pipe 19. The weak solution enters the heat exchanger 14 through the pipe 13. and exits via line 15.



   In order for the machine to be able to remain in service for a long time, it is desirable that the parts of the device which come into contact with the brine solution be made of or coated with materials which prevent corrosion. If the elements in contact with the solution do not resist it, we will realize

 <Desc / Clms Page number 34>

 that excessive loss of egg time results after long continuous operation 1 from the need to replace parts frequently. Consequently, in the proposed system, the elements, which are in contact with the colution, are formed (the material preventing corrosion.

   Thus, the drums or casings can have their interior surfaces covered with stainless steel. The absorber tubes can be of copper-nickel alloy, whereas the condenser tubes can be formed of a suitable copper alloy, such as "Everdur". The evaporator and condenser tanks can be made of copper alloys such as "Everdur" or bronze.



  Eliminators can be formed from stainless steel or nickel-copper. Other elements of the system which are in contact with the brine solution can also be formed from stainless steel or copper-nickel.



   Under certain conditions, additional water may be introduced into the system during an overnight shutdown in order to dilute the solution. A suitable pipe 118 is illustrated in FIG. 1 for this purpose. A valve 119 is disposed in the pipe 118 to control the flow of water in this pipe. Assuming it is necessary to shut down the system, eg overnight, steam may be interrupted as is the example, steam may be / while the evaporator continues to operate. Some water is absorbed by the solution, but in some cases not enough may be absorbed. Valve 119 can be opened to add a desired amount of water to the solution in the absorber.



   Fig. 27 illustrates a control mechanism for adjusting the level of refrigerant maintained in the system evaporator.

 <Desc / Clms Page number 35>

 



   The system thus illustrated in FIG. 27 is substantially the same as the system illustrated in FIG. 1, except that it includes, in addition, the control mechanism to adjust the level of refrigerant maintained in the evaporator. tor. To maintain a desired level of cooled water in the evaporator 7, a float valve 120 is provided. This float valve 120 comprises a float 121 connected to a lever 122 carrying a stop 123.



  An air line 124 connects a valve 125, disposed in the return line 31, to the float valve 120.



  Valve 125 is connected to the system main air line. Valve 125 is normally in the open position. Under these conditions, the lightning can escape from the pipe 124. An increase in the water level in the valve 120 causes the float 121 to rise, which causes the actuation of the lever 122, so that the stop 123 is brought against. an orifice formed in the pipe 124, which prevents air from escaping from this pipe 124 and establishes a pressure therein tending to urge the valve 125 towards a closed position. A balancing line 126 connects the valve 120 to the casing 4, so as to allow the same pressure, as that which exists in the casing 4, to be maintained in the valve 120.

   Valve 125 regulates the amount of cooled water entering the system after it has passed through the air conditioning equipment. A line 127 connects the valve 120 to the line 29, thus allowing the water level in the valve 120 to be maintained at the same height as the water level in the evaporator 7.



   If desired, a shut-off valve 128 can be provided in the return line 31, to prevent the return of cooled water to evaporator 7. Valves

 <Desc / Clms Page number 36>

 
 EMI36.1
 129 and ¯3.i ctïonrues s .-, a il -G e 'l- c ,,, ie ii t o1J e.lectr.c; ùe, .le-¯t can be e folded, if 1 vii the '.'. sire, when the system is off for the l: Ll.i, or; "'or des 2, - :,) licéttiol1S similar.



  The iiai, 2S illustrates a coded control di800si01-f to connect the rh:.:;.;: Of refrigerant passing through the tubes of the condenser and / or the absorber. The control device illustrated in Fig. 28 may be employed in conjunction with the system against Fig. 1 in place of the control device 73. A housing 131 is provided.
 EMI36.2
 mounted next to e: lVeJ.o1'j) e 5, de; 7ré "'é: .enc <in the conduide connecting the device 35 to the condenser 9. The box 131 is connected to the casing 5 by a driving 132.

   The steam, generated in the casing 5 by the generator 3, goes through line 132 to the casing 131 and condenses there. Inside the housing 131 is a probe 133 connected to the thermostatic controller 72. A wick 134 surrounds the probe 133.



  The vapor arriving in the envelope 131 condenses there, so that a reserve of liquid 135 is maintained in the bottom of the envelope 131. The level of the reserve of liquid 135 is maintained at a desired degree. sufficient to moisten the wick 134. Within the casing or housing 131 extends an extension 136 of a duct 137, connecting the casing 131 to the trap 35, which allows the maintenance of a desired amount of liquid in the casing and also serves to purge the casing of non-condensable gases, coming from casing 5, which may collect there.



   A suitable fluid is provided in the probe 133, a pipe 138 connecting this probe to the bellows (not shown)
 EMI36.3
 of the tilermostatic control device 71. The probe 133 reflects the saturation temperature prevailing in the envelope 131. As the envelope 131 is connected to the envelope.

 <Desc / Clms Page number 37>

 loppe 5, the saturation temperature thus reflected corresponds to the pressure maintained in the envelope 5. A change in the saturation temperature, as reflected by the probe 133, corresponds to a change in the pressure prevailing in the envelope 5.

   Such a change reflected by the probe 133 activates the thermostatic control device 72, so as to tend to move the valve 71 to a closed or open position, which reduces or increases the flow of condensed or refrigeration water passing through them. absorber and / or condenser tubes in the arrangement shown.



   Fig. 29 illustrates a variant of the system making it possible to obtain two temperatures with a single absorption refrigeration machine of the type described.



  A medium or conditioning agent is circulated by a pump 139 in a pipe 140 leading to a coil 141 arranged in the evaporator 7. The refrigerant cooled by projection in the evaporator 7 is in an exchange relationship. heat with the coil 141 and serves to cool the conditioning agent which passes through it. A pipe 142 connects the coil 141 to several heat exchangers 143, arranged in areas to be conditioned.

   These secondary heat exchangers 143 may include part of an air conditioning system, as described in U.S. Patent No. 2,363,29, issued November 21, 1944 to Carrier, in which the air from the zone to be conditioned is introduced into an induction device disposed in said zone, by the discharge of air conditioned initially at high speed in said device. The introduced air passes through a secondary heat exchanger 143 and is cooled to a desired temperature,

 <Desc / Clms Page number 38>

   in accordance with the requirements of the particular area to be packaged.
 EMI38.1
 Agent l'.E Ct711C?:. I; ¯Oi: 'tl :: ileT't'L, é1-r, Ôs 1,;.;, Sé:

  j = <. in the secondary heat exchanger 143, is returned by
 EMI38.2
 a pipe 144 towards the number 139 and 'breaks again by .. the coil ..i.l one it is again cooled.



  It will be seen that in 'most cases it is desirable' 11; e 11 é :: r: rnt # frl, n; erant r <: 11 - <> 1.d.i. rJ2:) ant because the heat exchanger of heat 1, rÜiÜl '(; 1 du; 3 / s! Ame, to conc.lition: the air intake is a temperature different from that of 11 é. \'; ent of condi tioDllc, 1Emt passing through the secondary heat exchanger 143. The refrigerant is cooled by projection in the evaporator 7 to a desired temperature and, coming into a calorific exchange relation with the coil 141, cools the conditioning agent therein until substantially the same temperature is reached A three-branched mixing valve 146 is provided in line 142 for controlling the flow of conditioning agent therein.

   The valve 146 is controlled by a thermostat 147, which is controlled by a probe 148 disposed in or in contact with the line 142, a bypass 149 connects the line 144 to the valve 146. Assuming that. it is desired to maintain the conditioner. - Sent to the secondary heat exchanger 143 at a temperature of 50 degrees F, the probe 148, in response to the temperature of the conditioner in line 142, activates thermostat 147, so as to control valve 149,

     by thus controlling the amount of conditioning agent passing through coil 141 and bypass 11 In other words, part of the conditioning agent returning from secondary heat exchangers 143 is cooled, while a second part does not change temperature,

 <Desc / Clms Page number 39>

 the two conditioning agent streams being controlled so as to reach the desired final temperature of the conditioning agent to be supplied to the secondary heat exchangers.

   If desired, a throttle valve, shown in dotted lines, can be provided in bypass 149 as a replacement for valve 146.
In order to control the amount of conditioning agent passing through each secondary heat exchanger 143, an appropriate bypass. 150 is planned. This branch 150 extends from line 142 to line 144.



  A valve 151 is disposed in bypass 150 and is adjusted according to the temperature of the zone to be conditioned, so as to determine the amount of cooled conditioning agent passing through each heat exchanger 143, according to the requirements of each zone. individual.



   The present invention provides an absorption cooling system of increased efficiency and lower cost than any system of this type known heretofore. The system is light in weight, which reduces the cost of transportation and allows for easier and faster assembly of the system for use. It does not contain any main moving parts, which greatly increases its useful life. It does not vibrate in operation and eliminates the dangers due to the extremely high pressures maintained in conventional absorption systems.



   The controls of the present invention allow the operation of the absorption refrigeration system from a full load to a very low partial load. Under these various operating conditions, the control devices operate precisely and smoothly, the operation of the

 <Desc / Clms Page number 40>

 system being automatically modified according to the load imposed on the system.
 EMI40.1
 



  The control device serves a rc;, vle: the capacity of the system, the concentration of the solution, the temperature of the cooled water leaving the system, the flow of condensed water in the tubes of the absorber and condenser, the value flows through the generator tubes, and provides various effective controls to increase the economical and efficient operation of the system. If desired, the system of the present invention
 EMI40.2
 tion can be used to provide a concluding a; "': ent è: different places' 1 ', 1: = ¯17¯Sai,: L î't':, '; 1':" é: - annuities uemperatures.

   The equipment required for this purpose does not greatly increase the cost of the machine and can easily be incorporated / system.
 EMI40.3
 



  Fi..8Vl :, iIDICiÚ'IJ1; [).



  --------------- 1. Uar absorption refrigeration system comprising an envelope, an absorber placed in the said envelope, an evaporator also placed in the aforementioned envelope, a predetermined pressure being maintained in this envelope, a second envelope containing a generator and a condenser, a predetermined pressure different from the pressure prevailing in the first envelope being maintained in the second envelope, these envelopes being isolated from one another , and
 EMI40.4
 means being nrtvus 1) Our circulate 1-1. solution between the envelopes.

** ATTENTION ** end of DESC field can contain start of CLMS **.


    

Claims (1)

2. Absorption refrigeration system comprising a casing containing an absorber and an evaporator, the evaporator serving to cool by pojeation a refrigerant, the projected value passing through the absorber to be absorbed there by the solution, <Desc / Clms Page number 41> a second casing adjacent to the first casing and containing a generator and a condenser, the generator serving to vaporize the refrigerant, which has condensed in the condenser, a pump for removing the weak solution from the 'absorber and to send the weak solution to the generator, and / an ejector, the pump serving to pass part of the weak solution into the ejector, the discharge of weak solution into the ejector, serving to drive the strong solution from the generator and to supply the mixture to the absorber. 3. Absorption refrigeration system comprising an absorber, an evaporator, a generator and a condenser, means for circulating the solution from the absorber to the generator and from the generator to the absorber, control means for the ability to control the amount of solution circulating in the system and means for controlling the operation of the monitoring device in response to a change in the load imposed on the system. 4. Absorption refrigeration system according to claim 3, wherein the evaporator and absorber are disposed in a casing, the evaporator being disposed above the absorber, and having pulverizing elements for pulverization. - put a refrigerant in the evaporator in order to cool it by spraying, the sprayed vapor being brought to the absorber passing through the periphery of the evaporator, so that the latter is isolated from the atmosphere ambient, the cooled refrigerant being withdrawn from the evaporator and brought into calorific exchange relation with the fluid to be cooled, atomizing elements being provided in the casing for atomizing the solution into the absorber. <Desc / Clms Page number 42> 5. Absorption refrigeration system according to claim 4, in which the generator and the condenser are disposed in an enclosure, the condenser being disposed above the generator, the generator therein. heating the solution to vaporize the vaporized refrigerant rising to the condenser and being condensed there, the strong solution being supplied to the absorber and means being provided for sending the condensate to the evaporator. 6. Absorption refrigeration system according to either of claims 1, 2 and 5, in which the casings extend horizontally, the casing containing the generator and the condenser being disposed above the casing. casing containing the evaporator and the condenser. 7. Absorption refrigeration system according to any one of the preceding claims, in which a heat exchanger device is employed to place the strong and weak solutions in a heat exchanging relationship with each other. the other. 8, A refrigeration system according to claim 7, wherein the heat exchanger comprises a bundle of pipes through one of the solutions, spaced members disposed around the central pipe of the bundle of pipes disposed around. of the central pipe, at a certain distance from each other and separated from the central pipe by the aforementioned elements, second elements arranged at intervals around said layer, a second layer of pipes arranged around the previous layer a certain distance from each other and spaced from the first layer by the second elements, outer / outer elements arranged around the second layer, and an outer pipe surrounding the beam and tra- <Desc / Clms Page number 43> poured by the solution, the outer pipe being kept spaced from the aforementioned bundle, by the external elements arranged around said bundle. 9. Absorption refrigeration system according to either of the preceding claims, in which a trough is provided for receiving the weak solution to be distributed in the generator, the weak solution passing through the trough and being distributed at from there; through a series of openings, evenly along the length of the generator. 10. Absorption refrigeration system according to any one of the preceding claims, in which spray elements distribute the solution in the evaporator, said spray elements being constituted by an inner pipe arranged to receive the solution. refrigerant and having openings, through which the refrigerant passes into an outer pipe surrounding the inner pipe and of which is the longitudinal axis / disposed in a plane above the plane of the inner pipe, so as to provide a space for the accumulation of the refrigerant in the outer pipe and fishtail nozzles connected to the second pipe for discharging the refrigerant in a series of substantially uniform flat jets, the openings in the inner pipe being placed at a sufficient distance above the fishtail nozzles to allow the coolant to accumulate in the lower part of the second pipe in the vicinity of the fishtail nozzles, whereby the turbulence of the coolant stream in the second pipe and its discharge rate from the fishtail nozzles are reduced. 11. Next absorption refrigeration system <Desc / Clms Page number 44> any of claims 1 to 9 inclusive, in which spray elements distribute the solution in the evaporator, the spray elements comprising an inner pipe arranged to receive coolant and provided with openings through which the refrigerant agent passes through an outer pipe surrounding the inner pipe and having. its longitudinal axis disposed in a plane located above the plane of the inner pipe, so as to provide space for the accumulation of refrigerant in the outer pipe, a series of spaced openings in the outer pipe arranged / paired to discharge the refrigerant in a substantially uniform flat pattern, the openings of each pair extending through the wall of the outer pipe towards each other and forming an acute angle with a perpendicular line drawn between them, the openings in the inner pipe being arranged at a sufficient distance. health above the openings in the outer pipe than to allow the refrigerant to accumulate in the lower part of the outer pipe in the vicinity of said openings, whereby the turbulence of the coolant stream in the outer pipe and its rate of discharge from the openings therein are reduced. 12. Absorption refrigeration system according to either of the preceding claims, in which a bleeding device is provided for extracting the non-condensable gases from the condenser and from the absorber, the bleeding device comprising a casing or casing. containing a refrigeration coil, a vapor line connected to the aforementioned casing and containing an ejector connected to the absorber, exits therefrom that the chamber, high speed vapor in the ejector entrains the gases from the absorber- <Desc / Clms Page number 45> beur, the housing being connected to the condenser, the pressure prevailing in the condenser being greater than, the pressure prevailing in the housing, whereby non-condensable gases are forced into the casing, and a water ejector connected to the casing or casing, passage of water at high speed through the water ejector entraining the material contained in the housing and discharging it out of the system. 13. Absorption refrigeration system according to one or other of the preceding claims, in which the absorber comprises several staggered tubes, at least some of these tubes being arranged so as to form a triangle, at least two of which are sides. are equal, the longest axis of a corresponding rhombus extending horizontally, and in which the atomizing elements, intended to distribute the solution on the tubes of the absorber, comprise conical nozzles, each nozzle uniformly distributing the solution. solution on a transverse area of the tubes, which allows the production of a horizontal and vertical stream of solution on the tubes. 14. An absorption refrigeration system as claimed in any of claims 7 to 13 inclusive, wherein a loop is provided in a pipe connecting the heat exchanger and the ejector, which loop serves to maintain. an adequate amount of strong solution in the exchanger for heat exchange purposes. 15. Absorption refrigeration system according to either of claims 1, 2 and 5 to 14, furthermore, in which the condenser reservoir is supported in the casing so as to allow its expansion and its expansion. contraction independently of the envelope by terminal elements attached to the envelope, which elements have a shape such that they conform to the con- <Desc / Clms Page number 46> round the tank and are fixed to the casing. 1o. An absorption refrigeration system as claimed in any one of the preceding claims, in which a drain pipe extends through the absorber, a threaded opening being provided in the wall of the casing to receive a. threaded plug, fixed to the drain pipe and intended to hold it in place, and in which an opening, through which the drain pipe passes, is made in the wall of a cau tube, -a / ¯ Being arranged in the opening and a cap / provided to compress the packing against a shoulder provided in the opening made in the wall of the aforementioned water tube to prevent leaks through said opening. 17. Absorption refrigeration system according to any one of the preceding claims, in which the capacity control device comprises a control element, such as a valve, for regulating the quantity of circulating solution. in the system. the. An absorption refrigeration system according to claim 17, wherein an element responsive to heat and to a change in the load imposed on the system controls the operation of the control element, the restriction of the control element decreasing. the. quantity of weak solution supplied to the generator and proportionally reducing the quantity of strong solution supplied to the absorber. 19. An absorption refrigeration system according to claim 17 or 18, wherein a heating agent or medium is supplied to the generator to vaporize at least a portion of the refrigerant from the gas. solution in the generator, a second control element, such as a valve, regulates the amount of heating medium supplied to the generator, and an element sensitive to heat and a change in temperature <Desc / Clms Page number 47> of the strong solution leaving the generator controls the operation of the control element. 20. An absorption refrigeration system as claimed in either of claims 17, 18 and 19, wherein the supply of refrigeration water to the absorber and / or condensed water to the condenser is controlled by a third control element, such as a valve, and in which means are provided for controlling the operation of the third control element. 21. An absorption refrigeration system according to claim 20, wherein said means is sensitive to the temperature of the condensate leaving the condenser, for controlling the third control element. 22. Absorption refrigeration system according to claim 20, in which the aforesaid control means comprise / an element intended to reflect the saturation temperature corresponding to the pressure prevailing in the casing of the condenser, so that, thanks to a variation From the reflected saturation temperature, the third control element is operated to change the flow of coolant through the condenser. 23. An absorption refrigeration system according to any one of claims 19 to 22. inclusive, wherein means are provided for adjusting the control point of the heat sensitive element controlling the operation of the second. control element, controlling the supply of heating medium to the generator. 24. A refrigeration system according to any one of the preceding claims, comprising means for preventing the formation of crystals in the <Desc / Clms Page number 48> solution when the system is operating at partial load. 25. An absorption refrigeration system according to any one of claims 17 to 24 inclusive, in which the various control elements are actuated by air pressure and in which means are provided responsive to the pressure created. by the pump EMI48.1 of solution to cut off the supply of air to the control elements, so that a deficiency or failure of the pump has the effect of automatically activating the control elements in order to cut off the operation of the system. 26. An absorption refrigeration system according to claim 25, wherein a pressure switch is disposed adjacent the discharge of the solution pump and is connected to a shut-off valve disposed in the main air line. the pressure created by the stern operating the switch so as to open the valve to supply air to the control elements; and a deficiency or failure of the pump operating the switch. so as to close the valve to cut off the air supply to the control elements. 27. An absorption refrigeration system according to any of claims 17 to 26 inclusive, wherein a bypass for condensed water is provided around the condenser and a control element is provided. to adjust the quantity of condensed water directed through the bypass. 28. An absorption refrigeration system as claimed in any one of claims 17 to 27 inclusive, wherein means responsive to the load imposed on the system are provided for readjusting the control element controlling the flow of heating agent. fage in the generator, in order to vary the <Desc / Clms Page number 49> tration of the solution passing through the system. 29. An absorption refrigeration system as claimed in any one of claims 77 28 inclusive including means for rendering a portion of the heat exchanger inefficient so as to allow the system to be operated at a higher concentration. high of the solution leaving the generator. 30. Absorption refrigeration system according to claim 29, wherein the aforesaid means comprise a bypass around a part of the heat exchanger, a control valve in said bypass and a second control valve in the supply line. the weak solution to the heat exchanger, opening the first valve and closing the second valve having the effect of opening the bypass and rendering part of the heat exchanger inefficient. 31. Absorption refrigeration system according to any one of the preceding claims, in which a control element is arranged in the pipe supplying refrigerant to the evaporator and in which means are provided for controlling the refrigerant. operation of the control element in response to a change in the level of refrigerant in the evaporator. 32. An absorption refrigeration system as claimed in claim 31, wherein the control element is responsive to the air pressure supplied thereto and wherein said control means vary the air pressure acting upon it. the element so as to move the element to an open or closed position. 33. Absorption refrigeration system according to either of claims 31 and 33, wherein a float valve is connected to the control member by an air line, the float valve being connected. <Desc / Clms Page number 50> to the casing of the evaporator so that the pressure prevailing in the chamber of the float valve corresponds substantially to the pressure prevailing in the casing, and in which an element is provided in the chamber dc. the valve to vary the air pressure in said pipe, in response to a change in the level of refrigerant in the evaporator. 34. Absorption refrigeration system according to any one of the preceding claims, wherein an athermal exchange element, such as a coil, is arranged in the evaporator to place the curling agent. in heat exchange relation with the cooled refrigerant, we are provided to circulate the cooled cooling agent in heat exchange relationship with a medium to be cooled and means are provided to circulate the cooled conditioning agent to a temperature different from the temperature of the refrigerant re - cooling in a secondary heat exchanger, in heat exchange relation with a second medium to be cooled. 35. The absorption refrigeration system of claim 34, wherein means, the bypass, are provided for bypassing the conditioning agent from the element. heat exchange and a valve is provided to adjust the proportion of conditioning agent passing through the heat exchange element. 36. An absorption refrigeration system according to claim 35, wherein a heat sensitive member is provided to control the valve in response to the temperature of the conditioning medium flowing to the heat exchanger. secondary. 37. Absorption adjustment system, substantially as described and illustrated with reference to the accompanying drawings.