US2054158A - Process of and apparatus for air - Google Patents

Description

PROCESS OF AND APPARATUS FOR AIR CONDITIONING Filed Jan. 11, 1932 2 Sheets-Sheet 1 INVEN TOR.

A TTORNEYS Sept. 15, 1936.

PROCESS. OF AND APPARATUS FOR AIR CONDITIONING Filed Jan. 11, 1932 2 Sheefcs-Sheet 2 INVENTOR.

BY Mi #W swa A TTORNE Y.

J. N. HADJISKY 2,054,158

Patented Sept. 15, 1936 UNITED STATES PROCESS OF AND APPARATUS FOR AIR CONDITIONING Joseph N. Hadjisky, Birmingham, Mich.

Application January 11, 1932, Serial No. 585,918

29 Claims.

This invention relates to air conditioning apparatus, and more particularly to an improved process for controlling the temperature and humidity of the air within a given space, by providing positive means for circulating such air, and

means appurtenant the circulating apparatus for conditioning the air so circulated. Various systems and constructions have been employed in the past for accomplishing this purpose, which systems, however, have had many inherent limitations, and have been so cumbersome and complicated as to prohibit their use in private homes, and to confine their use to auditoriums, large buildings, theaters, etc.

15 The system perhaps most commonly used incorporates positive air circulating means in connection with which a given portion of the air desired to be conditioned is treated in a single chamber, in whichit is both cooled and dehumidi- 20 fied.

is of course dependent upon accurate control of the temperature of the cooling medium, (usually cold water spray or combined spray and refrigeration). The only other system in common use 25 for accomplishing similar results provides a separate dehydrating chamber, in which is placed a moisture absorptive substance (frequently silica gel or the like) for removing moisture from the air, while the cooling is entirely performed in a separate and usually second chamber incorporating refrigeration or cooled water coils, cold water spray or the like. This arrangement is necessarily even more elaborate than the system first mentioned, as two complete and separate de- 5 humidifying systems must be provided, together with means for driving the moisture from one while the other is working. Moreover, both these arrangements not only necessitate use of apparatus occupying more space than is available in the 40 ordinary home, but the close regulation of the temperature of the cooling medium, etc., necessary to be maintained, obliges the attendance of an engineer practically constantly, further adding to the expense and impracticality of installations of such types in places where economy or space must be considered.

My improved process contemplates use of separate chambers for cooling and dehumidifying, the functions of which are interlocked and over- 50 lapping in operation, although they are controlled by independent humidity and temperature-responsive regulating means, or their equivalents. Both the temperature and humidity of the conditioned air discharged by such apparatus, when In such a system the conditioning process.

operated in accordance with the principles of my improved process, are relatively independent of variations of temperature of the cooling media in each chamber. The last statement requires the further explanatory observation that I preferably employ cooling coils for dehumidifying as well as 5 cooling. This latter feature assists in enabling incorporation of the process in apparatus of novel simplicity and compactness.

In order to illustrate the principles of my invention I have shown two constructions in which 10 the same are incorporated, but in which for purposes of clarity I have conformed, insofar as possible, to standard practice in the construction of air conditioning apparatus, varying therefrom only to the extent required to incorporate the principles of my invention. The invention, however, insofar as the process is concerned will be seen to be entirely independent of the apparatus used.

From the foregoing brief rsum of the problems and conditions existing in the field here involved, it is believed that the primary objects and advantages of my invention may easily be gathered.

They may briefly be stated to be the provision of a new system of air conditioning utilizing apparatus much simpler both in construction and operation than it has hitherto been possible to use.

A further object of my invention is the creation of a novel degree of flexibility of operation in the conditioning process by controlling the degree of dehumidification and also the cooling process by varying the percentage of air treated in each chamber, independently of temperature variations of the cooling agent. Such arrangement allowing the temperature of the cooling and dehumidifying agents to vary through a considerable range, creates important and valuable advantages which will become more apparent as the description progresses. The ability to control separately and independently the temperature and the humidity of the zone served irrespective of temperature fluctuations of the cooling agent, enables achievement of flexibility heretofore altogether impossible.

A further object of my invention is the provision of a system, so simple. that it may be incorporated in practical apparatus of very small size and low price, for home use or other uses where attendance of an operating engineer is not desirable.

A further object of my invention is the provision of such an improved'process, utilizable in conjunction with a supply of cooling water which may be at a temperature only slightly below that desired for the conditioned air, thus frequently enabling use of a city or deep well water supply,

for example, without necessitating artificial cooling thereof.

Other objects and advantages will be apparent from the following description, wherein reference is made to the accompanying drawings illustrating preferred embodiments of my invention, and wherein similar reference numerals designate similar parts throughout the several views.

In the drawings:

Figure 1 is an isometric view of the exterior of one form of suitable apparatus embodying the principles of my invention;

Figure 2 is a vertical sectional view thereof taken substantially on the line 22 of Figure 1 and looking in the direction of the arrows;

Figure 3 is a vertical sectional view taken substantially at right angles to Figure 2 and on the line 33 thereof, looking in the direction of the arrows;

Figure 4 is a plan view in partly horizontal section taken substantially on the plane 44 of Figure 5 and looking in the direction of the arrows, showing a somewhat modified form of my invention, and

Figure 5 is a vertical sectional view thereof taken substantially on the line 55 of Figure 4, and looking in the direction of the arrows.

In carrying out my improved process I provide separate chambers for cooling and dehumidifying, in each of which a cooling agent is employed. In most air conditioning systems, as above stated, a single chamber is used for both cooling and dehumidifying. Since dehumidification of such air as is usually desired to be conditioned cannot ordinarily be efiected at any but relatively very low temperatures, usually requiring, if temperature difference is to be employed for dehumidification, a temperature of about to 60 F. in the dehumidifying chamber, it follows that if this same chamber is used for cooling as well, a wastage of refrigerating facilities results, from the necessity of reducing the entire chamber to the extremely low temperature required to accomplish dehumidification, whereas the cooling could just as well be done at a temperature difference of only a few degrees. By separating the cooling and dehumidifying processes to as great an extent as is possible, while yet using cooling media for both purposes, and by a novel system of control, I attain the above outlined results.

First considering the specific apparatus shown in Figures 1, 2 and 3, after a description of which the process itself may be more readily understood: Reference character I designates the casing of one form of illustrative apparatus, which may, as shown, be embodied in a single housing. Air inlets 22' are provided in and adjacent the bottom portions of its walls, one of which may, if desired be for re-circulated and the other for fresh air. As shown in Figure 2, the entering air is divided into three portions by partitions 55' which divide the interior of the housing directly above the inlet chamber 3 into three sections, 6, 'I and 8.

The first of these (6) is a by-pass passage, through which air may be allowed to flow, untreated, directly to the circulating fans, by which it is forced from the outlet. The by-pass is so arranged as to always allow the flowing therethrough f a quantity of air sufiicient to provide a controlling balance which in regulated cooperation with the humidified and cooled air, the quantity of which is subject to continuous control,

chamberis smaller than the cooling chamber,

and the air travel through it normally less, a relatively small refrigerating unit answers, although the coil 9 is best maintained at a relatively low temperature. While the coil 9 serves to somewhat lower the temperature of the air flowing through the compartment 8, its principal function is that of dehumidifying such air. Air passing through this compartment is further dried by the water droplet arrester II, comprising a series of spaced'substantially par llel crenelated vanes through which the air must pass and upon which any globules of moisture it may contain will be caught.

A relatively greater percentage of the total air flow through the conditioner is ordinarily passed through the larger cooling chamber I, where the coils I0, which may be at a considerably higher temperature than the dehumidifying coils, perform a major portion of the cooling operation. The pipe lines leading to the cooling chamber may be run through the dehumidifying chamber to pre-cool the air entering the latter, or as shown in Figure 2, a portion of the tubes themselves may be run through the dehumidifying chamber.

These dehumidifying pre-cooling portionsof the tubes are designated III.

A series of dampers I2-I3 extends across the housing in such manner as to control the entire air flow therethrough. The dampers I2 are arranged to control the flow of the air which has passed through the by-pass and cooling chambers 6-1, which air may mingle in the space 2| above them before flowing through the dampers. The dampers I3, which control the air flow through the dehumidifying chamber 8, may as shown be connected to and controlled together with the same mechanism as the dampers I2, being so arranged that as the dampers I2 are moved toward closed the dampers I3 are moved toward opened position, and vice versa. A lost motion connection is provided, or variant damper construction utilized, so arranged that when the dampers I3 are completely open, the dampers I2 are only partially closed. The details of the mechanism are of course immaterial inasmuch as my invention concerns primarily the process involved. The air which has passed through the dampers into the chamber I4 may beforced from the outlet I8 by the fans I5, driven by an electric motor I6. The desired cooling of the coils I0 may be accomplished by cold water alone. The inlet and outlet couplings for this coil may also be mounted upon the exterior of the casing, as indicated at I0".

The damper 4 controlling the by-pass passage may be directly controlled in response to the temperature changes in the area whose atmosphere is being conditioned, by means of a thermostat (not shown) directly connected to a bellows-operated or other suitable actuating mechanism I9 arranged to open the damper in response to a fall of temperature, and close it upon a rise of temperature, to force a greater percentage of the airto pass through the cooling chamber.

The dampers l2--|3 may be controlled by a hygrostat (not shown) also located in the zone whose atmosphere is to be conditioned, and similar actuating mechanism 20 arranged to be responsive thereto. These dampers are so adjusted that upon a fall of humidity the dampers l3 tend to close and the dampers I2 to open, so that a smaller percentage of the air passes through the dehumidifying chamber 8 and a greater percentage through the sections 6, I, and vice versa.

It will be seen that by virtue of the automatic control of the dampers 4-l2-l3 thus provided, the percentage of air by-passed, and that at any time passing through the cooling. and dehumidifying sections, is constantly subjected to, positive control which is entirely independent of the temperature of the coils 9-40, and responsive only to conditions in the area served. Thus if the temperature in the served area tends to fall too low, the by-pass damper 4 is automatically opened, and a greater quantityof untreated air allowed to flow therethrough, while variances in the humidity of the air in the controlled zone are also automatically compensated for by the dampers l2|3. A drip pan, as 3' may be employed and positioned, as shown in Figure 2, beneath the coils, to catch any condensed moisture which may fall therefrom. A drain pipe 3" is also shown, although these features are ot course immaterial insofar as the invention is concerned.

This method of incorporating dehumidifying, cooling and by-pass passages entirely in one casing, and of varying. in response to continuous automatic control the percentage of the total air flow which is permitted to pass through each chamber, in response to conditions in the served area entirely, and independently of the temperature of the cooling and dehumidifying agents used in the apparatus, may be embodied in apparatus of various forms. The performance of my improved system is further largely dependent upon the constant flow of at least some air through the by-pass, so that by direct and controlled variation of such flow independently of the remainder of the apparatus, the temperature of the controlled air may be subjected to constant and simple control. Many variant but suitable forms of apparatus will doubtless suggest themselves to those skilled in the art.

A more detailed study of the efiect upon the dehumidification and cooling processes of variations in temperature of the dehumidifying and cooling media, and an analysis of the total heat content balance as it is divided between the two chambers, will show both the independence of the systems operation with respect to such variations, its flexibility, and the casualrelation between the scientific control of the variables and the mathematical laws behind the process and the results which the process achieves.

An illustrative case will be considered to show the quantitative analysis of the passage of air through such an arrangement of apparatus as has been described in connection with Figures 1, 2 and 3. The calculations are made on the basis of one pound of air as the unit amount handled 'and passed through the system. The

heat and moisture loads are typical of a residence.

air conditioning problem. The given conditions are as follows:

1. Temperature of air in inlet chamher 3 82 F. 2. Moisture content per pound or air in chamber 1 66 grains 3. Total heat per pound in air in chamber 3 29.6 B. t. u.

4. Heat load to be removed per pound I of air in chamber 3 3.3 B. t. u. 5. Moisture load to be removed per a pound of air in chamber 3 3.9 grains We will further assume the following required conditions:

1. Final moisture content per pound of air at outlet (ll) 62.1 grains 2. Total heat in air per pound delivered at outlet L 26.8 B. t. u. 3. Final temperature of air leaving outlet (approx) '70.5F.

In the tabulated cases below I shall assume three different temperature conditions in the dehumiditying chamber, the temperature in the cooling chamber being assumed to remain constant. The weight of the air thatwill pass through the dehumidiflcation process can be found from the equation:

Di -M W Pounds wherein Wx=weight of air passing through dehumidifying chamber per pound of air delivered to entire system. Mx moisture load to be removed per pound 0! air (given) =3.9 grains,

Ma moisture content per pound of suppliedair (given) =66 grains.

Md=moisture content per pound of air leavin dehumidifying chamber. See tabulated values below for each case. Substituting in the equation, the following results are obtained:

A study of these calculations discloses the fact that a random variation of temperature of the cooling agent of from 10 to 13 F. does not in any manner interfere with the dehumidifying process or its control. The relatively small proportion of the total treated air passing through the dehumidifying chamber (Wx) is shown by Item 6. Item 8 shows the relatively slight in crease in the amount of air necessary to be passed through the dehumidlfying chamber per degree rise in temperature. Comparison oi. thevalues shown in Items 4 and 5 makes plainthe fact that it would require an abnormal increase in the value Mx'to greatly affect in proportion to the volume of air treated, i. e., the value Item 6 In practice, such abnormal changes in the mois-' ture load as those here contemplated do not occur. Thevariation of moisture load, expressed in grains per pound of air is ordinarily very gradual and slight from hour to hour.

Considering Item 6 from a somewhat difl'erent angle it will be seen that its maximum increase relatively to the whole pound of air handled is 14 per cent, but its absolute increase from case 3 to case I is I make use of this relationship to control the process in the dehumidif ying chamber, and the relatively large absolute variation" of the amount of air to be passed through the chamber makes possible the use of a damper to control the same, with-the resultant simple and reliable operation characteristic of this means of com trol, especially where velocities, as here, are low. The process is thus regulated by the value Wx, while Wx in turn is controlled by a damper (l3) responsive only to the variation of Mx in the served area; throughout wide variances in the temperature of the cooling agent.

Considering next the balance of the total heat content as it is divided between the cooling and deh umidifying chambers, it should be noted that some heat is removed from the air in the dehumidifying chamber without a corresponding fall of temperature, in accordance with a well known law of thermodynamics.- The relative quantity of air passing through the dehumidifying chamber is ordinarily less than through the cooling chamber, as above stated. A temperature drop is of course caused by the removal of heat from the air in this chamber, which heat is removed by condensation of moisture in the air. and some by cooling of the air itself. The total heat removed may be expressed by the equation,

Tabulating and calculating yalues for heat balance during dehumidification process in the three assumed cases:

Tabulation of calculated values for heat balance during dehumidz'flcation process Cases Dehumidifier chamber temperatures,

degrees F Wx (from previous tables) in pounds... Hzgatt load to be removed (given) u H; (given) F4 (from standard tables)- H:H H,=Wx (IIJIIJ)=B. t. u Per cent of heat load removed 6 Percent of heat load left to be removed by cooling process 34.

Thus it is seen that in these assumed cases from to per cent of the total heat load is removed by the dehumidifying chamber of the apparatus.

The exact percentage of heat which will be removed by the dehumidifier chamber is proportional to the relation of the sensible heat load to the latent heat load. This, however, is established by the conditions of each problem and cannot be changed very much. It is of course desirable to remove in the dehumidifying chamber as small a percentage of the total heat load as possible.

Examining the equation H:=W:(H3Ha), the

, next important factor, Wx, is also seen to be fixed by the moisture load. The only variables which can be utilized for the purpose of absorbing more of the heat with the coils i0 is to decrease H3 in the equation Hx=W:(H'3-Hd) or to increase Ha. But as I have chosen to allow a random fluctuation of the temperature of the cooling medium in coils 9 from 35 to 48 F. for special purposes, H; is the logical and most effective item to be changed in its relation to the dehumidification chamber process. The means I have chosen to do this are the following: By extending part of coil ID in chamber 1 through the lower part of chamber 8 the air going into the chamber 8 is pre-cooled. It can be shown by calculation that in this way an amount of heat load from 12 to 30% of the total can be added to the cooling chamber coils- Cases 1 2 3 1. Total heat load (given) 13. t. u 3.3 3.3 3.3 2. Heat load removed by dehumidifier... 2. 17 l. 97 1.81 3. Remaining heat load to be removed by cooling process l. 13 1. 33' 1.49 4. Maximum weight 0! air capable oipassing through cooling chamber per pound circulated 756 850 892 5. Temperature of air in chamber 3, given,

degrees F 82 82 82 6. Temperature drop it all air in Item 4 is coo 6. 3 6. 6 7.05 7. Temperature drop of such air is cooled 8. 4 8. 9. 36 8. Temperature of air leaving cooler ii 75% goes through, degrees F 73v 6 73. 15 72. 64' 9. Temperature of air leaving cooler ii 50% goes through, degrees F 71. 5 71 70 Items 6 and 7 show the relatively small temperature drop required to perform the cooling operation. The second result of importance will be noted from a study of Items 8 and 9. Comparing the final temperature here with the final temperature in the dehumidifying chamber it will be seen that there is a difference of about 30 F. The cooling process can thus be carried on with a cooling agent at a much higher temperature than is required in the dehlimidifying chamber. This temperature difference will be seen to represent pure gain insofar as economy of operation is concerned, since it is unnecessary to provide refrigerating means at the relatively greatly re- '.duced temperature used in the dehumidifying chamber. In the cooling chamber it is usually possible to employ city water as the cooling medium rather than artificial refrigeration; at, of course, a considerable saving of expense, since such cooling water is used to remove about half the entire heat load, whereas in the processes heretofore used it has been necessary to use artificially cooled means for. removing the entire heat load. Even if artificial refrigeration is also used to reduce the temperature of the cooling chamber, a considerable saving in expense of operation results from the employment of my improved process, since carrying this chamber at a relatively high temperature (perhaps 60 F.)

permits employing more economical and compact refrigerating apparatus. Perfect results can also be obtained by the use of ice cooled water in the dehumidifying chamber and city water for the cooler, thus dispensing with artificial refrigeration entirely.

A consideration of Items 4, 6 and '7 shows that there may be considerable variation in the amount of air passing through the cooling chamber. I make-use of this fact to further control the process by controlling this factor, rather than controlling the temperature of the cooling agent as is the common practice.

Another suitable arrangement of apparatus for carrying out my improved process is shown in Figures 4 and 5, in which is shown a construction whereby the air is first permitted to flow through the by-pass and cooling chambers, after which a regulatable and variable portion of the entire flow passes through the dehumidifying chamber I08. In this construction, in which analogous parts to those described in connection with the first mechanical embodiment have been given similar reference numerals one hundred integers higher, the dampers |2| I3 may be similarly controllable and reversibly operable, under the influence of the humidity-responsive actuating member I20. Similar lost motion connection between the dampers is also preferably provided. The by-pass dampers I04 are connected to the temperature-responsive controlling member H9,

and thus regulate the percentage of air which is forced to pass through the cooling chamber I01. Separate refrigerating units l22l23 may be used for cooling the coils l09'l l 0, with the benefits of economy previously outlined resulting from the elimination of the necessity of performing the cooling by means of coils maintained at low temperature or if desired, cold water spray may be utilized in the dehumidifying chamber, as shown in Figures 4 and 5. In these views the nozzle-carrying spray pipes are designated I 09, the coupling means for connecting the cold water lines thereto, I09. Whatever the cooling agent utilized in the dehumidifying chamber, the more greatly reduced temperature need be maintained only therein, while the cooling chamber may be operated at the higher temperature made possible by'my improved process, thus obtaining the above outlined inherent economies.

While it will be apparent that the illustrated embodiments of my invention herein disclosed are well calculated to adequately fulfill the objects and advantages primarily set forth, it is to be understood that the invention is susceptible to variation, modification and change within the spirit and scope of the subjoined claims.

What I claim is:

1. In an air conditioning apparatus, separate chambers through which air to be conditioned is tion is the paramount consideration, and in another of which temperature correction is intende ed to be effected, and means for controlling the functioning of the apparatus, comprising interlocked damper means for controlling the flow through each such chamber, so arranged that by continuous movement such damper means may be made to effect opening movement of one and closing movement of the other.

2. In an air conditioning apparatus, separate chambers through which air is adapted to flow, in one of which humidity correction is the primary consideration, in another of which principally tcmperature correction is effected, and through another of which untreated air may pass, and means for controlling the functioning of the apparatus, comprising humidity-responsive damper means for interdependent controlling of the proportion of treated air passed through the dehumidifying chamber and that passed through the remaining portions of the apparatus, one being adapted to be moved toward opened and the other toward closed position by continuing movement of said damper means, and additional damper means, responsive only to the temperature'in the served area, for controlling the proportion of air by-passed.

3. In an air conditioning apparatus incorporating separate chambers, a cooling coil within one chamber adapted primarily for cooling, a second cooling coil at a relatively lower temperature than the first, arranged within another chamber and primarily intended for dehumidification, a portion connected to the first mentioned coil being extended through the second chamber in a manner adapted to pre-cool the air passing therethrough.

4. The process of cooling and dehumidifying air which includes circulating the air desired to be conditioned, dividing the air so circulated, changing the humidity'of one such divided portion, concurrently separately changing the temperature of another divided portion of the air, concurrently by-passing another divided portion, varying the proportion of the air passed thru the humidity-changing medium in response to humidity conditions in the conditioned zone, varying the volumetric proportioning of air between i the by-Dass and the temperature controlling medium in response to thermal conditions in the served zone, and recombining the portions of air so treated.

5. The process of cooling and dehumidifying air which includes circulating the air desired to be conditioned, dividing into separate portions the air so circulated, concurrently varying the humidity of one such divided portion and the temperature 'of another, controlling the air flow thru the humidity varying section in response to humidity conditions in the conditioned zone, concurrently by-passing another portion of the air around the temperature corrective section and? separately controlling the air flow thru the bypass in response to temperature conditions in the conditioned zone.

6. The process of cooling and dehumidifying air which includes circulating air from and to the area desired to be conditioned, dividing into separate portions the air so circulated, varying the humidity of one such divided portion in the desired direction by 'absorbing heat therefrom, concurrently separately varying the temperature of another such divided portion in the desired direction, so controlling the proportion of the total air flow thru the humidity varying section in response to humidity conditions in the served zone and the proportion of the total air flow thru the temperature varying section in response to temperature conditions in the served zone as to provide corrective adustment of the humidity and temperature of the conditioned air relatively independently of reasonable temperature variations of the corrective agencies.

'7. The process of cooling and dehumidifying air which includes circulating air from and to the area whose air is desired to be conditioned, dividing into separate portions the air so circulated, varying the humidity of one such divided portion, concurrently separately varying the temperature of another such divided portion, varyingly apportioning the quantity of air passing thru each in response to humidity and temperature conditions respectively in the served zone, concurrently permitting another divided portion of the air stream to pass untreated, and controlling the volumetric portion of the circulating air so by-passed also in response to temperature variations in the served zone.

8. The process of cooling and dehumidifying air which includes maintaining a refrigerating agency for temperature correction at a tempera ture below that of the air to be conditioned, maintaining a humidity corrective agency at a relatively lower temperature, concurrently causing circulation of separate air streams through each such agency, and controllingly apportioning the quantity of air permitted to flow thru each in response to temperature and humidity .conditions in the area whose air is desired to be conditioned.

9. In air cooling and dehumidifying apparatus, a cooling agency at a lower temperature than the air desired to be cooled, thru which such air may circulate, a dehumidii'ying agency at a more greatly reduced temperature and thru which air may be passed, damper means for controlling the volume of air passing thru each agency, means for so controlling the damper in response to humidity variations in the served zone as to maintain one agency open to the passage of air while restricting the other, and vice versa, a by-pass around the temperature corrective agency, and means for controlling the air fiow thru the bypass in response to variations of temperature in r the served zone.

10. In an air cooling and dehumidifying system having an inlet and an outlet, an air cooling agency at a reduced temperature relatively to the air to betreated, a dehumidifying agency at a. lower temperature, means for conducting air over each agency, a portion of the cooling agency being placed in advance of the dehumidifying agency so that air passes thru them in the order named and is pre-cooled by'the cooling agency before entering the dehumidifying agency, a bypass for conducting air from the inlet to the outlet without passing it through either agency, temperature responsive controlling means for the by-pass, and humidity responsive controlling means whereby the fiow through the dehumidifying agency may be regulated.

11. The process of conditioning air which includes providing a cooling agency at a reduced temperature, and a dehumidifying agency at a lower temperature, and passing a portion of the air to be treated thru each and a portion thru neither, but passing the air supplied to the de-' humidifying agency first thru the cooling agency to be there pre-cooled, and regulating the air by-passed and passed through each agency in response to changes in temperature and humidity in a served zone.

12. The process of conditioning air which in cludes providing a cooling agency at a reduced temperature, and a dehumidifying agency at a. reduced temperature and a dehumidifying agency at a lower temperature, passing a portion of the air thru the cooling section, by-passing a portion therearound, and passing part of the pre-cooled air thru the dehumidifying agency, and controlling the proportion of air by-passed and passed through said agencies in response to temperature and humidity conditions in a served zone.

13. The process of cooling and dehumidifying air which includes forming the air to be conditioned into a flowing stream, passing a portion of the stream through a temperature corrective medium operating by temperature differential, passing another portion of the stream through a humidity corrective medium which also acts by temperature differential, and delivering the stream portions so treated to a served zone.

14. The process of cooling and dehumidifying' air which includes forming the air to be conditioned into a flowing stream, passing a portion of the stream through a temperature corrective medium acting by temperature differential and which is held at a temperature below that of the ity corrective medium held at a still lower tem-- perature, and delivering the stream portions so treated to a served zone.

15. The process of cooling and dehumidifying air which includes forming the air to be conditioned into a flowing stream, passing a portion of the stream through a temperature corrective agency at'a temperature below that of the air to be conditioned, passing a portion of said stream through a humidity corrective agency acting by temperature differential and held at a lower temperature than said first mentioned agency, controllingly varying the percentage of the total air fiow passed through each agency, and delivering the stream portions so treated to a served zone.

16. The process of cooling and dehumidifying air which includes forming the air to be conditioned into a flowing stream, passing a portion of the stream through a temperature corrective agency at a temperature below that of the air to be conditioned, passing aportion of said stream through a humidity corrective agency acting by temperature differential and held at a lower temperature than said first mentioned agency, bypassing a portion of the air untreated past both agencies, and controllingly apportioning the quantities of air by-passed and permitted to flow through each agency.

17. The process of cooling and dehumidifying air which includes forming the air to be conditioned into a flowing stream, passing aportion of the stream through a temperature corrective agency at a temperature below that of the air to be conditioned, passing a portion of said stream through a humidity corrective agency acting by temperature differential and held at a lower temperature than said first mentioned agency, by-passing a portion of the air untreated past both agencies, controllingly apportioning the proportion of air by-passed in response to. temperature conditions in the served area, and similarly controlling the proportion of flow through each of said agencies in response to hygrostatic conditions in said area.

18. The process of dehumidifying air which comprises maintaining a refrigerating agency at a reduced temperature, and varying the quantity of air permitted to pass therethrough in accordance with the equation 19. The process of cooling and dehumidifying air which includes maintaining two separate refrigerating media at reduced temperatures but one at a lower temperature than the other, passing air desired to be dehumidifled through said lower temperatured medium, passing air desired to be cooled but not dehumidified through the other medium, controlling the proportion of the air passed through, the dehumidifying medium in response to changes of humidity in a served zone, and controlling the proportion of air passed through the cooling medium in accordance with a quantity of heat remaining to be removed, considering the proportional quantity .thereof removed by the dehumidifying medium.

20. The process of conditioning air which includes maintaining separate cooling and dehumidifying media at reduced temperatures with respect to the air desired to be conditioned, but holding the dehumidifying medium at a lower temperature than the cooling medium, circulating such air through both media, and controlling the apportionment of the" air allowed to flow through the cooling medium in accordance with the per centage of heat remaining unremoved by the dehumidifying medium, as expressed by the equatiOD H:=W:(H3-Hd).

21. The process of cooling and dehumidifying air which includes maintaining a refrigerating agency for temperature correction at a temperature below that of the air to be conditioned, maintaining another refrigerating agency for humidity correction at a still lower temperature, causing circulation of air through each of said agencies, by-passing another portion of air untreated, con.- trollingly varying the aiiflow through the humidity corrective agency in response to changes of humidity conditions only, and controllingly varying the by-passed air in response to temperature conditions only.

22. In an air cooling and dehumidifying system having an inlet and an outlet, an air cooling agency at a reduced temperature relatively to the air to be treated, a dehumidifying agency at a lower temperature, means for conducting air over each agency, a portion of the cooling agency being placed in advance of. the dehumidifying agency so that air passes through them in the order named and is pre-cooled by the cooling agency before entering tine dehumidifying agency, and humidity responsive controlling means for regulating the flow through both the cooling and dehumidifying agencies.

23. In an air cooling and dehumidifying system having an inlet and an outlet, an air cooling agency at a reduced temperature relatively to the air to be treated, a dehumidifying agency at a lower temperature, means for conducting air over each agency, a portion of the cooling agency being placed in advance of the dehumidifying agency so that air passes through them in the order named and is pre-cooled by the cooling agency before entering the dehumidifying agency, and humidity responsive controlling means for regulating airflow within the system.

24. The process of cooling and dehumidifying air which comprises causing air, which is to be conditioned, to circulate in heat exchange relation with cooling surfaces to remove principally sensible heat from the air when the relative humidity of the air to be conditioned is below a predetermined percentage, causing air, which is to be conditioned, to circulate in heat exchange relation with colder cooling surfaces when the relative humidity of the air to be conditioned is above'a predetermined percentage, the temperature of. which colder surfaces causes the air flowing thereover to be cooled to below the dew point thereof, and controlling the flow of air over the heat exchange surfaces in accordance with the relative humidity of the air to be conditioned.

25. The process of cooling and dehumidifying air which comprises causing air, which is to be conditioned, to circulate in heat exchange relation with cooling surfaces to remove principally sensible heat from the air when the relative humidity of the air to be conditioned is below a predetermined percentage, causing at least a part of such air tocirculate also in heat exchange relation with other cooling surfaces when the relative humidity of. the air to be conditioned is above a predetermined percentage, the temperature of which latter surfaces causes the air flowing thereover to be cooled to below the dew point thereof, and controlling the flow of air over the heat exchange surfaces in accordance withthe.

relative humidity of the air-to be conditioned.

26. An air conditioning system comprising, in combination, a heat absorber, the main function of which is to remove principally sensible heat from air flowing thereover, a second heat absorber adapted to cool air flowing thereover to below the dew point thereof, means for controlling the flow of. air over the second mentioned heat absorber, and means responsive to the relative humidity of the air to be conditioned for actuating the controlling means.

27. An air conditioning system comprising, in combination, a heat absorber, the main function of which is to remove principally sensible heat from air flowing thereover, a second heat absorber adapted to cool at least a part of said air to below the dew point thereof, means for controlling the flow of air over the second mentioned heat absorber, and means responsive to the relative humidity of the air to be conditioned for actuating the controlling'means.

28. An air conditioning system comprising, in combination, refrigerating apparatus including an evaporator, the main function of which is to remove principally sensible heat from air flowing thereover, a second evaporator adapted to cool air flowing thereover to below the dew point thereof, means for controlling the flow of air over the second mentioned evaporator, and means responsi've to the relative humidity of the air to be conditioned for actuating the controlling means.

29. A conditioner unit for air conditioning systems including a pair of. chambers arranged in parallel, one chamber constituting an air cooler for absorbing latent heat from the air stream passing through it, the other chamber having cooling means therein for absorbing substantially only excess sensible heat of the air passing through it, means for delivering an air stream to be conditioned to the inlets of said chambers and for proportioning the amount of the stream which passes through the two chambers, means whereby the divided portions of the air stream commingle after leaving the chambers.

JOSEPH N. HADJISKY.

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