Background of the Invention

The present invention relates generally to an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, thermal storage system, air cooler or air heater. More specifically, the present invention relates to a combination or combinations of separate indirect heat exchange sections enclosed in a housing and direct evaporative heat exchange sections arranged in the same structure to achieve improved capacity, improved performance and allowing a wet and dry mode.

The invention includes the use of a plate type or coil circuit tube type of heat exchanger as an indirect heat exchange section. Such indirect heat exchange section can be combined with a direct heat exchange section, which usually is comprised of a fill section over which an evaporative liquid such as water is transferred, usually in a downwardly streaming operation. Such combined indirect heat exchange section and direct heat exchange section together provide improved performance as an overall heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater.

Part of the improved performance of the indirect heat exchange section comprising a plate heat exchanger is the capability of the indirect heat exchange section hereinafter called a plate type heat exchanger but could can also be a coil circuit tube type heat exchanger, to provide both sensible and latent heat exchange with the evaporative liquid which is streamed or otherwise transported over and through the indirect heat exchange section. The improved performance is achieved by insuring that 100% of the plate heat exchanger is wetted while also operating at substantially higher evaporative fluid velocities resulting in higher external forced convection heat transfer coefficients relative to gravity drain indirect heat exchangers. Various combinations of the heat exchange arrangements are possible in accordance with the present invention. Such arrangements could include an arrangement wherein the indirect heat exchange section is physically located within the arrangement and being above, adjacent or below the direct heat exchange section. In such arrangements, the indirect heat exchange section is comprised of a plate type heat exchanger located in a housing located within the evaporative heat exchanger. An internal fluid stream to be cooled, heated, evaporated or condensed is passed through the internal passageways of the plate type heat exchanger. An evaporative liquid is passed through the indirect heat exchange section housing and distributed through the external passageways of the plate type heat exchanger to indirectly exchange heat with the internal fluid stream. Due to varying heat loads, varying ambient conditions, economical needs to save energy or water and needs of heat exchange, the indirect heat exchanger of the present invention could be operated wherein both air and an evaporative liquid such as water are drawn or supplied across the indirect heat exchanger. This is accomplished by selectively pumping air into the indirect heat exchanger to travel with the evaporative liquid which causes increased agitation and evaporative fluid velocities hence increased external heat transfer coefficients while also allowing evaporative heat exchange to occur on the outside of the indirect heat exchanger. A dry mode of operation is made possible by pumping only air through the indirect heat exchange section housing in thermal contact with the outside of the internal passageways of the plate type heat exchanger to indirectly exchange heat with the internal fluid stream. Because of the increased efficiency of the indirect heat exchange section, the size of the indirect heat exchanger can be reduced thereby allowing more room for adding direct heat exchanger surface area and even allowing a larger diameter fan in some orientations both of which increase the improved heat exchanger capacity. Because the indirect heat exchange section is located within the improved arrangement and being above, adjacent or below the direct heat exchange section, either air or evaporative liquid or both are in direct contact with the housing of the indirect heat exchanger thereby increasing the heat transfer of the indirect heat exchange section.

The evaporative liquid then exits the indirect heat exchange section housing to be distributed onto and through the direct heat exchange section which is usually comprised of a fill arrangement. Air is moved over the direct heat exchange section to evaporatively cool the evaporative liquid. The evaporative liquid draining from the direct heat exchange section is typically collected in a sump and then pumped upwardly for redistribution through the indirect heat exchange section housing.

Accordingly, it is an object of the present invention to provide an improved heat exchange apparatus, which could be a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, which includes an indirect heat exchange section located within a housing and located above, below or adjacent to the direct heat exchanger all which are located within the improved heat exchange apparatus.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section that comprises a plate type heat exchanger or a coil circuit tube type heat exchanger located within a housing.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section located within a housing wherein either evaporative liquid, air or both evaporative liquid and air exchange heat with the housing of the indirect heat exchange section. It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section located within a housing wherein the customer piping between the pump and the indirect heat exchange section has been eliminated.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section located within a housing wherein the cost of the housing is substantially reduced because of a lower pressure requirement.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, by decreasing the size of indirect heat exchanger while increasing the size of direct heat exchanger located within the same heat exchange apparatus while increasing the size of the fan while maintaining the size or footprint of the cooling tower in order to increase the thermal capacity and reduce the manufacturing cost for a given footprint of the cooling tower.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section located within a housing wherein air streams are injected into the evaporative liquid of the indirect heat exchange section housing during wet operation.

It is another object of the present invention to provide an improved heat exchange apparatus such as a closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater, including an indirect heat exchange section located within a housing wherein the indirect heat exchange section may operate in a dry mode by operating an air blower that blows air through the indirect heat exchanger housing to move cold ambient air through the exterior passages of the indirect heat exchanger to indirectly and sensibly cool the internal fluid stream. 95 Summary of the Invention

The present invention provides an improved heat exchange apparatus which typically is comprised of a combination of an indirect heat exchange section and a direct heat exchange section. The indirect heat exchange section provides improved performance by utilizing a plate type heat exchanger usually within a housing. A plurality of internal passages and external

100 passages are formed between plates. Such plates are designed to allow an internal fluid stream to be passed through the internal passages and an evaporative liquid, air, or evaporative liquid with air to be passed through the external passages to indirectly exchange heat with the internal fluid stream within the plate heat exchanger. Such utilization of a plate heat exchanger in the closed circuit fluid cooler, fluid heater, condenser, evaporator, air cooler or air heater of the present

105 invention provides improved performance and also allows for combined operation or alternative operation wherein only air or only an evaporative liquid or a combination of the two can be passed through or across the external passages of the plate heat exchanger. Since the housing of the indirect heat exchanger is located within the evaporative structure, the evaporative liquid moving within the housing as it is absorbing heat can be further cooled by the evaporative liquid,

110 air, or evaporative liquid and air which is in contact and moving across the outside surface of the housing.

A direct heat exchange section is located beneath, adjacent or above the indirect heat exchange section. The evaporative liquid leaving the indirect heat exchange section housing passes onto and through the direct heat exchange section fill and accordingly allows heat to be 115 drawn from such evaporative liquid by a passage of air across or through the direct heat exchange section fill by air moving therethrough. The evaporative liquid exiting the direct heat exchange section is collected in a sump and then pumped back for distribution through the indirect heat exchange section housing. While the sump is typically locating in the bottom of the evaporative heat exchanger, it is also possible to locate the sump remotely as is known in the art.

120 The present invention further concerns the design of an improved heat exchange

apparatus that has a direct heat exchanger, usually a fill pack and an indirect heat exchanger, usually a plate type heat exchanger. The size of the more expensive indirect heat exchanger can be decreased while the size of the inexpensive direct heat exchanger can be increased. In addition, because some indirect and direct evaporative heat exchangers have the indirect heat

125 exchanger and fan located at the top, the fan and indirect heat exchanger compete for precious footprint and in this improved heat exchange apparatus, since the indirect heat exchanger is smaller or located adjacent or under the direct heat exchange section, the fan diameter may be increased while maintaining the size or footprint of the cooling tower in order to increase the thermal capacity and reduce the manufacturing cost for a given footprint of the cooling tower.

130 The size reduction of the indirect heat exchanger can be achieved by increasing the rate of sensible heat transfer between the evaporative liquid and the indirect heat exchanger. In general, the rate of sensible heat transfer is increased when the velocity of liquid traveling across the surface of indirect heat exchanger is increased. Since the pull of gravity is constant and cannot be increased, the velocity of the evaporative liquid that is naturally flowing over the

135 external surface of prior art indirect heat exchange sections is limited and cannot be substantially increased. Without significantly increasing this cooling tower liquid velocity, it is difficult to increase the rate of sensible heat transfer between the evaporative liquid and the surface of the indirect heat exchanger plates. In one embodiment of this invention, the plates of the indirect heat exchanger are enclosed in a water tight housing and then a pump is used to force a larger

140 quantity of evaporative liquid into the housing and then rapidly through the plurality of passages between adjacent plates. Because the forced liquid velocity can be substantially higher than the naturally flowing liquid by gravity, a higher sensible heat transfer rate between the evaporative liquid and the external surface of the plates is achieved.

Because the indirect heat exchanger plates are typically made out of metal or of a highly

145 conductive plastic, which is typically more expensive than the fill pack of the direct heat

exchange section which are usually made of plastic, the overall manufacturing cost of the cooling tower can be reduced substantially. By increasing the rate of sensible heat transfer significantly without reducing the size of indirect heat exchanger plates significantly, the overall cooling tower's thermal capacity is increased without increasing the cooling tower footprint.

150 The overall cooling tower performance could additionally be increased by injecting air streams into the indirect heat exchange section housing during wet operation. The injected air stream, which becomes air bubbles inside the housing when filled with evaporative liquid, increases the heat transfer rate by both agitating and increasing the evaporative liquid's local velocity. Further, the injected air into the evaporative liquid allows evaporative heat transfer to

155 occur in addition to sensible cooling by just the evaporative fluid alone.

In another embodiment, the indirect heat exchange section housing can be drained of evaporative liquid while still having the ability to cool the internal fluid stream within the indirect heat exchange section plate passageways. This can be achieved by operating an air blower that is attached to the plate housing to move cold ambient air through the plate housing

160 through the passages outside the plate internal passageways to indirectly sensibly cool the

internal fluid inside the plate passageways with ambient air. Brief Description of the Drawings

In the drawings,

165 FIG 1 is a side view of the first embodiment using a plate type heat exchanger in the housing of the indirect heat exchange section in accordance with the present invention

FIG 1 A is a side view of the first embodiment using a coil circuit tube type heat exchanger in the housing of the indirect heat exchange section in accordance with the present invention

170 FIG IB is a side view of the first embodiment using a different water distribution system to direct the evaporative fluid to the direct heat exchanger in accordance with the present invention;

FIG. 2 is a side view of a second embodiment of a heat exchanger in accordance with the present invention;

175 FIG. 3 is a side view of a third embodiment of a heat exchanger in accordance with the present invention;

FIG. 4 is a side view of a fourth embodiment of a heat exchanger in accordance with the present invention;

FIG. 5 is a side view of a fifth embodiment of a heat exchanger in accordance with the 180 present invention;

FIG. 6 is a side view of a sixth embodiment of a heat exchanger in accordance with the present invention;

FIG. 7 is a side view of a seventh embodiment of a heat exchanger in accordance with the present invention; 185 FIG. 8 is a side view of an eighth embodiment of a heat exchanger in accordance with the present invention;

FIG. 9 is a perspective view of the indirect heat exchange section having a plate type heat exchanger located inside a housing in accordance with an embodiment of the present invention;

FIG. 10 is a cutaway view of the indirect heat exchange section having a plate type heat 190 exchanger located inside a housing in accordance with an embodiment of the present invention

FIG. 11 is a cutaway view of the indirect heat exchange section having a coil circuit tube type exchanger located inside a housing in accordance with an embodiment of the present.

Description of the Preferred Embodiment

Referring now to FIG. 1 of the drawings, a first embodiment of the present invention is 195 shown generally as heat exchanger 20, which is generally in the form of a closed circuit cooling tower.

Such heat exchanger generally is present in a closed circuit cooling tower with indirect heat exchange section 25 located above direct heat exchange section 24.

Direct heat exchange section 24 is typically comprised of fill usually comprised of sheets 200 of polyvinyl chloride. Direct heat exchange section 24 receives air through air inlet 28 on the outside of heat exchanger 20, with air being drawn generally across and somewhat upwardly through direct heat exchange section 24 by fan 26 rotated by motor 27.

Indirect heat exchange section 25 is usually comprised of a plurality of plate type heat exchangers has preferably internal fluid inlet 21 and internal fluid outlet 22 and is positioned 205 inside housing 34. It should be understood that the operation of internal fluid inlet 21 and

internal fluid outlet 22 can be reversed if it is desired. An evaporative cooling tower liquid, usually water, flows downwardly from water distribution assembly 23 such that the evaporative cooling tower liquid falls downwardly onto and through direct heat exchange section 24. While falling downwardly and through direct heat

210 exchange section 24, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from the evaporative cooling tower liquid to air. It should be noted that in some applications, condensation takes place from air into cooling tower liquid.

The cooling tower liquid that passes downwardly and through direct heat exchange section 24 is then collected in sump 31 and is pumped by pump 29 to indirect section housing 34

215 and through indirect heat exchange section 25 then back to water distribution assembly 23.

Water distribution assembly 23 can be comprised of a variety of pipes with openings and using orifices or spray nozzles 36 as shown in Figure 1 or as shown in Figure IB, may have gravity water basin 35 with orifices or nozzles 36 or can be of other water distribution assemblies as known in the art.

220 In Figure 1, indirect heat exchange section 25 is usually comprised of a plate type heat exchanger 32 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or evaporated passes within the joined plates or cassettes of plate type heat exchanger 32. It should be further understood that the heat exchanger 25 can be situated in any available location within

225 the improved heat exchange apparatus in any position because the evaporative liquid is pumped through the indirect heat exchange section. An advantage of having indirect heat exchange section 25 and direct heat exchange section 24 located within the improved heat exchanger 20 is that the piping between indirect heat exchange section 25 and water distribution assembly 23 is minimized and customer piping is eliminated. Another advantage of having indirect heat 230 exchange section 25 and direct heat exchange section 24 located within the improved heat exchanger 20 is that indirect heat exchanger 25 is in very close proximity to water distribution assembly 23, requiring much lower pressure to pump the evaporative liquid hence the pressure rating and cost of housing 34 may be substantially reduced.

In Figure 1 A, indirect heat exchanger 30 may be constructed of tubes and inlet header 22 235 and outlet header 21 in any configuration and material as known in the art as long as it is

enclosed by housing 34.

In Figures 1,1 A, and IB, fan 26 is shown to induce airflow through direct heat exchange section 24 but can also be a forced air type as known in the art and is not a limitation of the invention. This is true for all subsequent Figures as well.

240 Referring now to FIG. 2 of the drawings, a second embodiment of the present invention is shown generally as heat exchanger 10, which is generally in the form of a closed circuit cooling tower.

Such heat exchanger generally is present in a closed circuit cooling tower with indirect heat exchange section 5 located below direct heat exchange section 4. Direct heat exchange 245 section 4 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 4 receives air through air inlet 8 on the outside of heat exchanger 10, with air being drawn generally across and somewhat upwardly through direct heat exchange section 4 by fan 6 rotated by motor 7.

Indirect heat exchange section 5 is usually comprised of plate type heat exchanger 12 250 having fluid inlet 1 and fluid outlet 2 and is positioned inside housing 16. It should be

understood that fluid inlet 1 and fluid outlet 2 can be reversed if it is desired. An evaporative cooling tower liquid, usually water, flows downwardly from water distribution assembly 3 such that the cooling tower liquid falls downwardly onto and through direct heat exchange section 4. While falling downwardly and through direct heat exchange

255 section 4, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from the evaporative cooling tower liquid to air. It should be noted that in some applications, condensation takes places from air into cooling tower liquid.

The evaporative cooling tower liquid that passes downwardly and through direct heat exchange section 4 and collected in sump 11 is pumped by pump 9 to indirect heat exchange

260 housing 16 and through indirect heat exchange section 5 then back to water distribution assembly 3. Water distribution assembly 3 can be comprised of a variety of pipes with openings or nozzles 13 as shown, or any other water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

Indirect heat exchange section 5 enclosed in housing 16 is usually comprised of a

265 plurality of plate type heat exchangers 12 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or evaporated passes within the joined plates or cassettes of plate type heat exchanger 12.

An advantage of placing indirect heat exchange section 5 into sump 11 is that evaporative 270 cooling tower water flows over the surface of the housing 16 of indirect heat exchange section 5 and heat transfer takes place because the cold water in sump 11 cools the surface of housing 16 of indirect heat exchange section 5 further cooling the fluid within the plurality of plates 12. When heat transfer takes place between housing 16 and sump water 11, sump water 11 becomes hotter and the sump water top surface can be used as an added evaporative surface to the fill and

275 increase the overall efficiency of the cooling tower.

Indirect heat exchange section 5 may be either fully or partially submerged in cold water sump 11. Another advantage of placing indirect heat exchange section 5 into sump 11 is that there is room now for a larger or taller direct heat exchange section 4 thereby increasing the capacity of the unit. An advantage of having indirect heat exchange section 5 and direct heat

280 exchange section 4 located within the improved heat exchanger 10 is that the piping between indirect heat exchange section 5 and water distribution assembly 3 is minimized and customer piping is eliminated.

Referring now to FIG. 3 of the drawings, a third embodiment of the present invention is shown generally as heat exchanger 40, which is generally in the form of a closed circuit cooling 285 tower.

Such heat exchanger generally is present in a closed circuit cooling tower with indirect heat exchange section 45 located in air plenum 53 next to and toward the lower half of direct heat exchange section 44. It should be understood that positioning indirect heat exchange section 45 in the air plenum 53 adjacent to direct heat exchanger 44, allows for easier access and

290 cleaning of indirect heat exchanger 45 while allowing a larger size (full height) direct heat

exchange section 44 in the design.

Direct heat exchange section 44 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 44 receives air through air inlet 48 on the outside of heat exchanger 40, with air being drawn generally across and somewhat upwardly

295 through direct heat exchange section 44 by fan 46 rotated by motor 47. Indirect heat exchange section 45 is usually comprised of a plurality of plate type heat exchangers 52 having fluid inlet 41 and fluid outlet 42 and positioned inside housing 56. It should be understood that the operation of fluid inlet 41 and fluid outlet 42 can be reversed if it is desired.

300 An evaporative cooling tower liquid, usually water, flows downwardly from water

distribution assembly 43 such that the evaporative cooling tower liquid falls downwardly onto and through direct heat exchange section 44. While falling downwardly and through direct heat exchange section 44, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from cooling tower liquid to air. It should be noted that in some

305 applications, condensation takes places from air into cooling tower liquid.

The evaporative cooling tower liquid that passes downwardly onto and through direct heat exchange section 44 and collected in sump 51 is pumped by pump 49 to indirect heat exchange housing 56 and through indirect heat exchange section 45 then back to water distribution assembly 43. Water distribution assembly 43 can be comprised of a variety of pipes

310 with openings or nozzles 36, or be of any other water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

Indirect heat exchange section 45 is usually comprised of a plurality of plate type heat exchangers 52 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or

315 evaporated passes within the joined plates or cassettes of plate type heat exchangers 52.

Air 54 exits from direct heat exchange section 44 and flows into discharge air plenum 53 on the way to fan 46 then flows over the surface of housing 56 of indirect heat exchange section 45 and heat transfer takes place. In the case in which direct heat exchange section 44 is used to cool evaporative cooling tower liquid, air 54 cools the surface of housing 56 of indirect heat 320 exchange section 45, which is an added benefit from placing heat exchanger 45 in discharge air plenum 53. It is possible to mount the indirect section at any height within air plenum 53 where the air will be in heat exchange with housing 56.

An advantage of having indirect heat exchange section 45 and direct heat exchange section 44 located within the improved heat exchanger 40 is that the piping between indirect heat 325 exchange section 45 and water distribution assembly 43 is minimized and customer piping is eliminated.

Referring now to FIG. 4 of the drawings, a fourth embodiment of the present invention is shown generally as heat exchanger 90, which is generally in the form of a closed circuit cooling tower.

330 Such heat exchanger generally is present in a closed circuit cooling tower with direct heat exchange section 94 underneath water distribution assembly 93 with indirect heat exchange section 95 located in sump 101.

Direct heat exchange section 94 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 94 receives air through air inlets 98 on the 335 outside of heat exchanger 90, with air being drawn generally upwardly through direct heat

exchange section 94 by fan 96 rotated by motor 97.

Indirect heat exchange section 95 is usually comprised of a plurality of plate type heat exchangers 102 having fluid inlet 91 and fluid outlet 92 positioned in housing 105. It should be understood that the operation of fluid inlet 91 and fluid outlet 92 can be reversed if it is desired. 340 An evaporative cooling tower liquid, usually water, flows downwardly from water

distribution assembly 93 such that the cooling tower liquid falls downwardly onto and through direct heat exchange section 94. While falling downwardly onto and through direct heat exchange section 94, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from cooling tower liquid to air. It should be noted that in some

345 applications, condensation takes places from air into cooling tower liquid.

The cooling tower liquid that passes downwardly onto and through direct heat exchange section 94 and collected in sump 101 is pumped by pump 99 to housing 105 then through indirect heat exchange section 95 then back to water distribution assembly 93. Water distribution assembly 93 can be comprised of a variety of pipes with openings or nozzles 100, or any other

350 water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

Indirect heat exchange section 95 is usually comprised of a plurality of plate type heat exchangers 102 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or

355 evaporated passes within the joined plates or cassettes of plate type heat exchanger 102.

It can be noted that by placing the indirect heat exchange section 95 under the direct heat exchange section 94, there is room for a greater size (taller) direct heat exchange section 94. An advantage of placing indirect heat exchange section 95 into sump 101 is that cold evaporative cooling tower water flows over the surface of the housing 105 of indirect heat exchange section

360 95 and heat transfer takes place. In the case in which direct heat exchange section 94 is used to cool the evaporative cooling tower liquid, the cold water in sump 101 cools the surface of housing 105 of indirect heat exchange section 95 further cooling the fluid within the plurality of plates 102 which is an added benefit. Indirect heat exchange section 95 may be either fully or partially submerged in cold water sump 101. 365 An advantage of having indirect heat exchange section 95 and direct heat exchange section 94 located within the improved heat exchanger 90 is that the piping between indirect heat exchange section 95 and water distribution assembly 93 is minimized and customer piping is eliminated.

Referring now to FIG. 5 of the drawings, a fifth embodiment of the present invention is 370 shown generally as heat exchanger 110, which is generally in the form of a closed circuit cooling tower.

Such heat exchanger generally is present in a closed circuit cooling tower with indirect heat exchange section 115 located underneath direct heat exchanger 114 and at least partially above the pool of evaporative cooling tower liquid in sump 121.

375 Direct heat exchange section 114 is typically comprised of fill usually comprised of

sheets of polyvinyl chloride. Direct heat exchange section 114 receives air through air inlets 118 on the outside of heat exchanger 110, with air being drawn generally upwardly through direct heat exchange section 114 by fan 116 rotated by motor 117.

Indirect heat exchange section 115 is usually comprised of a plurality of plate type heat 380 exchangers 122 having fluid inlet 111 and fluid outlet 112 and positioned inside housing 125. It should be understood that the operation of fluid inlet 111 and fluid outlet 112 can be reversed if it is desired.

An evaporative cooling tower liquid, usually water, flows downwardly from water distribution assembly 113 such that the cooling tower liquid falls downwardly onto and through 385 direct heat exchange section 114. While falling downwardly onto and through direct heat

exchange section 114, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from cooling tower liquid to air. It should be noted that in some applications, condensation takes places from air into cooling tower liquid.

The evaporative cooling tower liquid that passes downwardly onto and through direct

390 heat exchange section 114 and collected in sump 121 is pumped by pump 119 to housing 125 through indirect heat exchange section 115 then back to water distribution assembly 113. Water distribution assembly 113 can be comprised of a variety of pipes with openings, orifices or nozzles 120, or any other water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

395 Indirect heat exchange section 115 is usually comprised of a plurality of plate type heat exchangers 122 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or evaporated passes within the joined plates or cassettes of plate type heat exchanger 122.

Some of the air entering through air inlet 118 on the way to direct heat exchange section

400 114 blows over and cools the surface of housing 125 of indirect heat exchange section 115 which in turn further cools plate type heat exchangers 122.

An advantage of having indirect heat exchange section 115 and direct heat exchange section 114 located within the improved heat exchanger 110 is that the piping between indirect heat exchange section 115 and water distribution assembly 113 is minimized and customer

405 piping is eliminated.

Referring now to FIG. 6 of the drawings, a sixth embodiment of the present invention is shown generally as heat exchanger 130, which is generally in the form of a closed circuit cooling tower. Such heat exchanger generally is present in a closed circuit cooling tower with direct heat 410 exchange section 134 underneath water distribution assembly 133 indirect heat exchange section 135 located underneath redistribution pan 149 and positioned above cooling tower liquid in sump 141.

Direct heat exchange section 134 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 134 receives air through air inlets 138 415 on the outside of heat exchanger 130, with air being drawn generally upwardly through direct heat exchange section 134 by fan 136 rotated by motor 137.

Indirect heat exchange section 135 is usually comprised of a plurality of plate type heat exchangers 142 having fluid inlet 131 and fluid outlet 132 and positioned inside housing 145. It should be understood that the operation of fluid inlet 131 and fluid outlet 132 can be reversed if 420 it is desired.

An evaporative cooling tower liquid, usually water, flows downwardly from water distribution assembly 133 such that the cooling tower liquid falls downwardly onto and through direct heat exchange section 134. While falling downwardly onto and through direct heat exchange section 134, a small portion of cooling tower liquid is evaporated by moving air and

425 latent heat transfer takes place from cooling tower liquid to air. It should be noted that in some applications, condensation takes places from air into cooling tower liquid.

The evaporative cooled cooling tower liquid that passes downwardly onto and through direct heat exchange section 134 gets collected in redistribution pan 149 and is re-sprayed onto indirect heat exchange section housing 145. The redistribution pan 149 guides the evaporative

430 cooling tower water over housing 145 such that the housing is cooled and indirectly helps to cool indirect heat exchange section 135. The evaporative cooling tower liquid is then collected in sump 141 and is pumped by pump 139 to housing 145 then through indirect heat exchange section 135 then back to water distribution assembly 133. Water distribution assembly 133 can be comprised of a variety of pipes with openings, orifices or nozzles 140, or any other water 435 distribution arrangement such as using spray nozzles, troughs, or other water distribution

assemblies.

Indirect heat exchange section 135 is usually comprised of a plurality of plate type heat exchangers 142 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or 440 evaporated passes within the joined plates or cassettes of plate type heat exchanger 142.

An advantage of having indirect heat exchange section 145 and direct heat exchange section 134 located within the improved heat exchanger 130 is that the piping between indirect heat exchange section 145 and water distribution assembly 133 is minimized and customer piping is eliminated.

445 Referring now to FIG. 7 of the drawings, a seventh embodiment of the present invention is shown generally as heat exchanger 150, which is generally in the form of a closed circuit cooling tower.

Such heat exchanger generally is present in a closed circuit cooling tower with indirect heat exchange section 155 located in plenum 163 adjacent to and towards the lower half of direct 450 heat exchange section 154. It should be noted that indirect heat exchanger 155 can be located above, below or adjacent to direct heat exchanger 154 as shown in other Figures but is presented as adjacent to direct heat exchanger 154 for illustrative purposes.

Direct heat exchange section 154 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 154 receives air through air inlet 158 455 on the outside of heat exchanger 150, with air being drawn generally across and somewhat upwardly through direct heat exchange section 154 by fan 156 rotated by motor 157.

Indirect heat exchange section 155 is usually comprised of a plurality of plate type heat exchangers 162 having fluid inlet 151 and fluid outlet 152. It should be understood that the operation of fluid inlet 151 and fluid outlet 152 can be reversed if it is desired.

460 An evaporative cooling tower liquid, usually water, flows downwardly from water

distribution assembly 153 such that the evaporative cooling tower liquid falls downwardly onto and through direct heat exchange section 154. While falling downwardly onto and through direct heat exchange section 154, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from cooling tower liquid to air. It should be noted that in

465 some applications, condensation takes places from air into cooling tower liquid.

The evaporative cooling tower liquid that passes downwardly onto and through direct heat exchange section 154 and collected in sump 161 is pumped by pump 159 to housing 169 then through indirect heat exchange section 155 then back to water distribution assembly 153. Water distribution assembly 153 can be comprised of a variety of pipes with openings, orifices or

470 nozzles 160, or any other water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

Indirect heat exchange section 155 is positioned in housing 169 and is usually comprised of a plurality of plate type heat exchangers 162. A fluid to be cooled, condensed, heated, or evaporated passes within the joined plates or cassettes of plate type heat exchangers 162.

475 Air 164 exits from direct heat exchange section 154 into plenum 163 on the way to fan

156 and flows over housing 169 of indirect heat exchange section 155 and heat transfer takes place. In the case in which direct heat exchange section 154 is used to cool the evaporative cooling tower liquid, air 164 cools housing 169 of indirect heat exchange section 155, which in turn cools the evaporative cooling tower liquid and plate type heat exchanger 162 inside indirect

480 heat exchange section 155.

In embodiment 150, air pump 166 is attached to heat exchanger 150 and supplies pressurized ambient air to air distribution tube 167 inside and near the bottom of housing 169 and indirect heat exchange section 155. It is to be noted that the source of pressurized air also could be the facility that uses heat exchanger 150 such as from an available pressured air source.

485 Check valve 168 prevents evaporative cooling tower liquid from flowing into air pump 166 when air pump 166 is turned off. During operation streams of air bubbles come out from air distribution tube 167 and travel upward with evaporative cooling tower liquid that is pumped by pump 159. Injecting air bubbles into the evaporative cooling tower liquid that travels through the plurality of liquid passages within plurality plate type heat exchangers 162 increases the

490 agitation and increases the velocity of the evaporative cooling tower liquid and also serves to enhance the heat transfer between the cooling tower water/air mixture compared to the evaporative cooling tower water alone. With the evaporative cooling tower liquid traveling at a higher speed, the sensible heat transfer rate between the evaporative cooling tower liquid and the surface of plurality of plate type heat exchangers 162 increases, and with the presence of air

495 bubbles in the evaporative cooling tower liquid, latent heat transfer may now take place,

increasing the overall thermal capacity of the heat exchanger 150.

It should be noted that indirect heat exchange section 155 may be located under the direct heat exchange section as shown in Figures 4, 5 & 6 with the air being drawn generally upwards through the direct heat exchange section and is not a limitation of the invention.

500 An advantage of having indirect heat exchange section 155 and direct heat exchange section 154 located within improved heat exchanger 150 is that the piping between indirect heat exchange section 155 and water distribution assembly 153 is minimized and customer piping is eliminated.

505 Referring now to FIG. 8 of the drawings, an eighth embodiment of the present invention is shown generally as heat exchanger 60, which is generally in the form of a closed circuit cooling tower. Such heat exchanger generally is present in a clqsed circuit cooling tower with indirect heat exchange section 65 located in plenum 73 adjacent to and towards the lower half of direct heat exchange section 64. It should be noted that indirect heat exchanger 65 can be

510 located above, below or adjacent to direct heat exchanger 64 as shown in other Figures but is presented as adjacent to direct heat exchanger 64 for illustrative purposes.

Direct heat exchange section 64 is typically comprised of fill usually comprised of sheets of polyvinyl chloride. Direct heat exchange section 64 receives air through air inlet 68 on the outside of heat exchanger 60, with air being drawn generally across and somewhat upwardly

515 through direct heat exchange section 64 by fan 66 rotated by motor 67. It should be noted that indirect heat exchange section 65 may be located under the direct heat exchange section as shown in Figures 4, 5 & 6 with the air being drawn generally upwards through the direct heat exchange section and is not a limitation of the invention.

Indirect heat exchange section 65 is usually comprised of a plurality of plate type heat

520 exchangers 72 positioned in housing 83 having internal fluid inlet 61 and fluid outlet 62. It

should be understood that the operation of fluid inlet 61 and fluid outlet 62 can be reversed if it is desired. An evaporative cooling tower liquid, usually water, flows downwardly from water distribution assembly 63 such that the evaporative cooling tower liquid falls downwardly onto

525 and through direct heat exchange section 64. While falling downwardly onto and through direct heat exchange section 64, a small portion of cooling tower liquid is evaporated by moving air and latent heat transfer takes place from cooling tower liquid to air. It should be noted that in some applications, condensation takes places from air into cooling tower liquid.

The evaporative cooling tower liquid that passes downwardly onto and through direct

530 heat exchange section 64 and collected in sump 71 is pumped by pump 69 to housing 83 then through indirect heat exchange section 65 then back to water distribution assembly 63. Water distribution assembly 63 can be comprised of a variety of pipes with openings, orifices or nozzles 70, or any other water distribution arrangement such as using spray nozzles, troughs, or other water distribution assemblies.

535 Indirect heat exchange section 65 is usually comprised of a plurality of plate type heat exchangers 72 but can be any type of indirect heat exchanger such as and not limited to a coil circuit tube type heat exchanger as known in the art. A fluid to be cooled, condensed, heated, or evaporated passes within the joined plates or cassettes of plate type heat exchangers 72.

Air 74 exits from direct heat exchange section 64 into plenum 73. Air 74 on the way to

540 fan 66 flows over housing 83 of indirect heat exchange section 65 and heat transfer takes place.

In the case in which direct heat exchange section 64 is used to cool evaporative cooling tower liquid, air 74 cools housing 83 of indirect heat exchange section 65 which in turn cools the evaporative cooling tower liquid and then plate type heat exchangers 72 inside indirect heat exchange section 65. 545 Embodiment 60 has a wet and a dry mode of operation to cool indirect heat exchanger

65. During wet operation, air valves 78 and 79 are closed and air blower fan 81 is turned off while liquid valves 76 and 80 are open. Air valves 78 and 79, and also water valves 76 and 80 may be manually or automatically operated as known in the art and is not a limitation of the invention. During dry operation, liquid valves 76 and 80 are closed and air valves 78 and 79 are

550 opened. Alternatively, air outlet valve 78 and water valve 76 may be omitted and air may

discharge through distribution 63. During dry operation fan motor 67 is turned off and air blower fan 81 blows cold ambient air into housing 83 of indirect heat exchange section 65. Cold, ambient air cools down the plurality of plate type heat exchangers 72 using sensible heat transfer and the heated air exits through air exit 77 and then to outside of heat exchanger 60.

555 An advantage of having indirect heat exchange section 65 and direct heat exchange

section 64 located within the improved heat exchanger 60 is that the piping between indirect heat exchange section 65 and water distribution assembly 63 is minimized and customer piping is eliminated.

Referring now to FIGS. 9 and 10, a perspective view and a cutaway side view,

560 respectively, of indirect heat exchange section 200 in accordance with the present invention are shown.

Indirect heat exchange section 200 is shown to be comprised of a plurality of plate type heat exchangers 201, process fluid inlet 202, process fluid outlet 203, evaporative cooling tower fluid outlet 204 and inlet 205, inlet and outlet plate header end caps 207 and housing 206. It 565 should be understood that the operation of the internal process fluid inlet 202 and process fluid outlet 203 can be reversed if it is desired. Internal, closed circuit cooling tower process fluid enters the plurality of plate type heat exchangers 201 through process fluid inlet 202 and is separated from the exterior of the plurality of plate type heat exchangers 201 and from the evaporative cooling tower fluid that enters 570 through cooling tower fluid inlet 205 of housing 206. Housing 206 may be designed such that it can be easily removed for cleaning the exterior of plate type heat exchangers 201 and is not a limitation of this invention.

As shown by directional arrows 208, internal process fluid flows through a plurality of internal parallel passageways of plate type heat exchangers 201 and exits through process fluid 575 outlet 203. As shown by cooling tower fluid directional arrows 209, exterior evaporative cooling tower fluid enters housing 206 through fluid inlet 205 and flows through a plurality of external passageways within plate type heat exchangers 201 and comes out of housing 206 through fluid outlet 204.

While flowing through the plurality of passageways within plate type heat exchangers 580 201, sensible heat transfer takes place between the evaporative cooling tower fluid and plate type heat exchangers 201.

In all the embodiments of the present invention, plate type heat exchanger 201 can be comprised of various metals such as stainless steel or other corrosion resistant steels and alloys. It is also possible that such plates can be comprised of other materials that would lead to good 585 heat exchange between the fluid within the plate and the evaporative cooling tower liquid or air passing outwardly therefrom. Such materials could be aluminum or copper; various alloys, or plastics that provide corrosion resistance and good heat exchange and are not a limitation of the invention. Referring now to FIG. 11 , a side view of a coil circuit tube type heat exchanger of 590 indirect heat exchange section 300 in accordance with the present invention is shown.

Indirect heat exchange section 300 is shown to be comprised of a plurality of coil circuit tube type heat exchangers 301, process fluid inlet 302, process fluid outlet 303, evaporative cooling tower fluid outlet 304 and inlet 305, inlet and outlet header end caps 307 and housing 306. It should be understood that the operation of the internal process fluid inlet 302 and process 595 fluid outlet 303 can be reversed if it is desired.

Internal, closed circuit cooling tower process fluid enters the plurality of coil circuit tube type heat exchange 301 through process fluid inlet 302 and is separated from the exterior of the plurality of coil circuit tube type heat exchangers 301 and from the evaporative cooling tower fluid that enters through cooling tower fluid inlet 305 of housing 306. Housing 306 may be 600 designed such that it can be easily removed for cleaning the exterior of coil circuit tube type heat exchangers 301 and is not a limitation of this invention.

As shown by directional arrows 308, internal process fluid flows through a plurality of internal parallel passageways of coil circuit tube type heat exchangers 301 and exits through process fluid outlet 303. As shown by evaporative cooling tower fluid directional arrows 309, 605 exterior evaporative cooling tower fluid enters housing 306 through fluid inlet 305 and flows through a plurality of external passageways within plate type heat exchangers 301 and comes out of housing 306 through fluid outlet 304.

While flowing through the plurality of passageways within plate type heat exchangers 301, sensible heat transfer takes place between the evaporative cooling tower fluid and coil 610 circuit tube type heat exchangers 301. In all the embodiments of the present invention, coil circuit tube type heat exchangers 301 can be comprised of various metals such as stainless steel or other corrosion resistant steels and alloys. It is also possible that such tubes can be comprised of other materials that would lead to good heat exchange between the fluid within the plate and the evaporative cooling tower liquid or air passing outwardly therefrom. Such materials could be aluminum or copper; various alloys, or plastics that provide corrosion resistance and good heat exchange and are not a limitation of the invention.

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