WO2002056989A2 - Distiller employing cyclical evaporation-surface wetting - Google Patents
Distiller employing cyclical evaporation-surface wetting Download PDFInfo
- Publication number
- WO2002056989A2 WO2002056989A2 PCT/US2002/001520 US0201520W WO02056989A2 WO 2002056989 A2 WO2002056989 A2 WO 2002056989A2 US 0201520 W US0201520 W US 0201520W WO 02056989 A2 WO02056989 A2 WO 02056989A2
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- WIPO (PCT)
- Prior art keywords
- evaporation
- chamber
- auxiliary
- evaporator
- condenser unit
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0057—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes
- B01D5/0069—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes with degasification or deaeration
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D1/00—Evaporating
- B01D1/28—Evaporating with vapour compression
- B01D1/2887—The compressor is integrated in the evaporation apparatus
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D3/00—Distillation or related exchange processes in which liquids are contacted with gaseous media, e.g. stripping
- B01D3/08—Distillation or related exchange processes in which liquids are contacted with gaseous media, e.g. stripping in rotating vessels; Atomisation on rotating discs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0057—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes
- B01D5/0072—Condensation of vapours; Recovering volatile solvents by condensation in combination with other processes with filtration
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S203/00—Distillation: processes, separatory
- Y10S203/08—Waste heat
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S203/00—Distillation: processes, separatory
- Y10S203/11—Batch distillation
Definitions
- the present invention is directed to distillation. It has particular, but not exclusive, application to using rotary heat exchangers to purify water by distillation.
- distillation the water to be purified is heated to the point at which it evaporates, and the resultant vapor is then condensed. Since the vapor leaves almost all impurities behind in the input, feed water, the condensate that results is typically of a purity much higher in most respects than the output of most competing purification technologies.
- One of the distillation approaches to which the invention to be described below may be applied employs a rotary heat exchanger. Water to be purified is introduced to one, evaporation set of heat-exchange surfaces, from which the liquid absorbs heat and evaporates.
- the resultant water vapor is then typically compressed and brought into contact with another, condensation set of heat- exchange surfaces that are in thermal communication with the set of evaporation heat-exchange surfaces. Since the water vapor on the condensation side is under greater vapor pressure than the water on the evaporation side, vapor that condenses on the condensation side will be hotter than the evaporating liquid on the evaporation side, and its heat of evaporization will therefore flow to the evaporation side: the system reclaims the heat of evaporization used to remove the relatively pure vapor from the contaminated liquid. To minimize the insulating effects to which a condensation film on the condensation surfaces would tend to contribute, a rotary heat exchanger's heat-exchange surfaces rotate rapidly, so the condensate experiences high centrifugal force and is therefore removed rapidly from the condensation surfaces.
- the rotary heat exchanger's centrifugal force also tends to reduce the water-film thickness on the evaporation side and thereby further benefit heat- exchange efficiency.
- introducing liquid to the evaporation side at too great a rate will compromise the centrifugal force's beneficial effect on heat transfer, so evaporator efficiency is best served by keeping the rate of feed- water introduction relatively low.
- too low a rate of feed-water introduction is counterproductive; it allows surface tension to defeat proper surface wetting and thus heat transfer to the liquid.
- the rate at which the evaporator-side heat-exchange surfaces are irrigated so varies as repeatedly to reach a peak irrigation rate that is at least twice its average rate.
- a peak irrigation rate that is at least twice its average rate.
- that average rate is less than half the steady-state rate required to maintain proper wetting, while the peak rate preferably exceeds that steady-state rate.
- the average rate is low, the repeated increases to such a peak rate can prevent those surfaces from dewetting. The result is a significantly greater heat-exchange rate, and less power consumption, than in a similar system employing the minimum steady- state rate required to maintain wetting.
- Fig. 1 is a front isometric view of a distillation unit that employs the present invention's teachings
- Fig. 2 is a cross-sectional view taken through the distillation unit
- Fig. 3 is a plan view of one of the heat-exchange plates employed in the distillation unit's rotary heat exchanger
- Fig. 4 is a cross-sectional view through two such plates taken at line 4-4 of Fig. 3;
- Fig. 5 is a diagram of the fluid flow through the rotary heat exchanger's evaporation and condensation chambers;
- Fig. 6 is a broken-away perspective view of the distillation unit's compressor;
- Fig. 7 is a broken-away cross-sectional view of one side of the compressor and the rotary heat exchanger's upper portion showing the fluid-flow paths between them;
- Fig. 8 is schematic diagram of the distillation unit's fluid circuit;
- Fig. 9 is a perspective view of the vapor-chamber base, main scoop tubes, and irrigation arms that the distillation unit employs;
- Fig. 10 is a plan view of the elements that Fig. 9 depicts;
- Fig. 11 is a cross-sectional view taken at line 11-11 of Fig. 10;
- Fig. 12 is a cross-sectional view taken at line 12-12 of Fig. 10;
- Fig. 13 is a cross-sectional view of one of the spray arms, taken at line 13-13 of Fig. 12;
- Fig. 14 is a broken-away perspective view of the distillation unit's transfer valve and related elements
- Fig. 15 is a broken-away perspective view of the distillation unit's transfer pump
- Fig. 16 is a broken-away isometric view of the distillation unit's filter assembly
- Fig. 17 is a further broken-away perspective view of the transfer valve illustrating the valve crank and its actuator in particular;
- Fig. 18 is a view similar to Fig. 12, but showing the transfer valve in its elevated position;
- Fig. 19 is an isometric view of one of the distillation unit's counterflow- heat-exchanger modules; and Fig. 20 is a cross-sectional view of that heat-exchanger module.
- Fig. 1 is an exterior isometric view of a distillation unit in which the present invention's heat-exchanger-irrigation approach can be employed.
- the distillation unit 10 includes a feed inlet 12 through which the unit draws a feed liquid to be purified, typically water containing some contamination.
- the unit 10 purifies the water, producing a pure condensate at a condensate outlet 14.
- the volume rate of condensate produced by the unit 10 will in most cases be only slightly less than that of the feed liquid entering inlet 12, nearly all the remainder being a small stream of concentrated impurities discharged through a concentrate outlet 16.
- the unit also may include a safety-drain outlet 18.
- the illustrated unit is powered by electricity, and it may be remotely controlled or monitored.
- the distillation unit 10 is intended for high- efficiency use, so it includes an insulating housing 22. But the present inven- tion's teachings are applicable to a wide range of heat-exchanger applications, not all of which would typically employ such a housing.
- Fig. 2 is a simplified cross-sectional view of the distillation unit. It depicts the housing 22 as having a single-layer wall 24. In single-layer arrangements, the wall is preferably made of low-thermal-conductivity material. Alternatively, it may be a double-layer structure in which the layers are separated by insulating space.
- the present invention is an advantageous way to supply feed liquid to the unit's heat exchanger 32. While the present invention's teachings can be employed to feed a wide variety of heat exchangers, the drawings illustrate a particular type of rotary heat exchanger for the sake of concreteness. As will be explained in more detail directly, the illustrated embodiment's rotary heat exchanger is essentially a group of stacked plates, one plate 34 of which will be described in more detail in connection with subsequent drawings.
- That heat exchanger 32 is part of an assembly that rotates during operation and includes a generally cylindrical shell 36 driven by a motor 38. The rotating assembly's shell 36 is disposed inside a stationary vapor-chamber housing 40 on which is mounted a gear housing 42 that additionally supports the motor 38. The vapor- chamber housing 40 in turn rests in a support omitted from the drawing for the sake of simplicity.
- each plate is largely annular; it may have an outer diameter of, say, 8.0 inches and an inner diameter of 3.35 inches.
- Each plate is provided with a number of passage openings 46.
- Fig. 4 which is a cross section taken at line 4-4 of Fig. 3, shows that the passage openings are formed with annular lips 48 that in alternating plates protrude upward and downward so that, as will explained in more detail presently, they mate to form passages between the heat exchanger's condensation chambers.
- the heat- exchanger plates are provided with annular flanges 50 at their radially inward edges and annular flanges 52 at their radially outward edges. Like the passage lips 48, these flanges 50 and 52 protrude from their respective plates, but in directions opposite those in which the passage lips 48 protrude.
- Fig. 5 which depicts the radially inward part of the heat exchanger on the left and the radial outward part on the right, shows that successive plates thereby form enclosed condensation chambers 54 interspersed with open evaporation chambers 56.
- a recently tested prototype of the heat exchanger employs 108 such plate pairs.
- a sprayer in the form of a stationary spray arm 58 located centrally of the spinning heat-exchanger plates sprays water to be purified onto the plate surfaces that define the evaporation chambers 56.
- That liquid absorbs heat from those surfaces, and some of it evaporates.
- Fig. 2's compressor 60 draws the resultant vapor inward.
- Fig. 6 depicts compressor 60 in more detail.
- the compressor spins with the rotary heat exchanger and includes a (spinning) compressor cylinder 62 within which a mechanism not shown causes two pistons 64 and 66 to reciprocate out of phase with each other.
- a piston rises, its respective piston ring 68 or 70 forms a seal between the piston and the compressor cylinder 62's inner surface so that the piston draws vapor from the heat exchanger's central region.
- its respective piston ring tends to lift off the piston surface and thereby break the seal between the cylinder wall and the pistons.
- annular piston- ring stops 72 and 74 which respective struts 76 and 77 secure to respective pistons 64 and 66, drag respective piston rings 68 and 70 downward after the seal has been broken.
- the piston rings and stops thus leave clearances for vapor flow past the pistons as they move downward, so a downward-moving piston does not urge the vapor back downward as effectively as an upward- moving piston draws it upward.
- the pistons reciprocate so out of phase with each other that there is always one piston moving upward, and thereby effectively drawing the vapor upward, while the other is returning downward.
- the vapor thus driven upward by the pistons 64 and 66 cannot pass upward beyond the compressor's cylin- der head 78, but slots 80 formed in the compressor wall's upper lip provide paths by which the vapor thus drawn from the heat exchanger's central region can be driven down through an annular passage 82 formed between the compressor cylinder 62's outer surface and the rotating-assembly shell 36.
- This passage leads to openings 83 in an annular cover plate 84 sealed by O-rings 85a and 85b between the compressor cylinder 62 and the rotating- assembly shell 36.
- the openings 83 register with the openings 46 (Fig. 3) that form the passages between the condensation chambers.
- the compressor cylinder 62, the cylinder head 78, and the rotating-assembly shell 36 cooperate to form a guide that directs vapor along a vapor path from Fig. 5's evaporation chambers 56 to its condensation chambers 54.
- the compressor compresses the vapor that follows this path, so the vapor pressure in the condensation chambers 54 is higher than that in the evaporation chambers 56, from which the compressor draws the vapor.
- the boiling point in the condensation chambers therefore is also higher than in the evaporation chambers. So the heat of vaporization freed in the condensation chambers diffuses to the (lower-temperature) evaporation chambers 56.
- the rotating assembly rotates at a relatively high rate of, say, 700 to 1000 rpm.
- the resultant centrifugal force causes the now-purified condensate to collect in the outer ends of the condensation chambers, between which it can flow through the passages that the heat- exchanger-plate openings 46 form.
- the condensate therefore flows out through the openings 83 in the top of the heat exchanger and travels along the channel 82 by which the compressed vapor flowed into the heat exchanger.
- the condensate can flow through the openings 80 in the compressor wall's lip.
- the condensate can also flow past the cylinder head 78 because of a clearance 86 between that cylinder head 78 and the rotating-assembly shell, whereas the condensate's presence in that clearance prevents the compressed vapor from similarly flowing past the cylinder head.
- An O-ring 88 seals between the rotating-assembly shell 36 and a rotat- ing annular channel-forming member 90 secured to the cylinder head 78, but spaced-apart bosses 92 formed in the cylinder head 78 provide clearance between the cylinder head and the channel member so that the condensate, urged by the pressure difference that the compressor imposes, can flow inward and into channel member 90's interior.
- the channel-forming member 90 spins with the rotary heat exchanger to cause the purified condensate that it contains to collect under the influence of centrifugal force in the channel's radially outward extremity.
- the spinning condensate's kinetic energy drives it into a stationary scoop tube 94, from which it flows to Fig. 1's conden- sate outlet 14 by way of a route that will be described in due course.
- a pump 100 draws feed liquid from the feed inlet 12 and drives it to the cold-water inlets 102C_IN and 104C_IN of respective counterflow-heat-exchanger modules 102 and 104.
- Those modules guide the feedwater along respective feed-water paths to respective cold-water outlets 102c_ou ⁇ and 104c_ou ⁇ - In flowing along those paths, the feedwater is in thermal communication with counterflows that enter those heat exchangers at hot-water inlets 102H_IN and 104H_IN and leave through hot-water outlets 102H_OUT and 104H_OUT, as will be explained in more detail below, so it is heated.
- counterflow-heat-exchanger module 104 receives a minor fraction of the feed-water flow driven by the pump 100. Its volume flow rate is therefore relatively low, and the temperature increase of which it is capable in a single pass is relatively high as a conse- quence.
- counterflow-heat-exchanger module 102 in the illustrated embodiment is essentially identical to counterflow-heat- exchanger module 104, but it receives a much higher volume flow rate, and the temperature increase that it can impart is correspondingly low. So the cold- water flow through counterflow-heat-exchanger module 102 also flows serially through further modules 106, 108, and 110 to achieve a temperature increase approximately equal to module 104's.
- Fig. 2 omits the degasser, but the de- gasser would typically enclose the motor 38 to absorb heat from it. The degasser thus further heats the liquid. Together with the heat imparted by the counterflow heat exchangers, this heat may be enough to raise the feed-liquid temperature to the level required for optimum evaporator/condenser action when steady-state operation is reached. From a cold start, though, a supplemental heat source such as a heating coil (not shown) would in most cases contribute to the needed heat.
- a supplemental heat source such as a heating coil (not shown) would in most cases contribute to the needed heat.
- the residence time in the degasser is long enough to remove most dissolved gasses and volatiles from the stream.
- the thus- degassed liquid then flows to a filter assembly 114, where its flow through a filter body 116 results in particulate removal.
- the resultant filtered liquid flows from the filter body 116 to an annular exit chamber 118, from which it issues in streams directed to two destinations. Most of that liquid flows by way of tube 119 to a nozzle 120.
- nozzle 120 delivers the filtered feed liquid to the rotating-assembly shell 36's inner surface, where it joins the liquid layer formed by the liquid that has flowed through the evaporation chambers without evaporating.
- Stationary scoop tubes 122 and 124 scoop liquid from this rotating layer.
- the scooped liquid's kinetic energy drives it along those tubes, which Fig. 10 shows in plan view and Figs. 11 and 12 show in cross-sectional views respectively taken at lines 11-11 and 12-12 of Fig. 10.
- each scoop tube bends gradually to a predominantly radial direction.
- each scoop tube is relatively narrow at its entrance but widens gradually to convert some of the liquid's dynamic head into static head.
- Those tubes guide the thus scooped liquid into an interior chamber 126 (Fig. 11) of a transfer-valve assembly 128.
- a transfer-valve member 130 is oriented as Fig. 12 shows.
- Fig. 13 which is cross-sectional view taken at line 13-13 of Fig. 12, shows that each of the spray arms 58 forms a longitudinal slit 138. These slits act as nozzles from which the (largely recirculated) liquid sprays into the evaporation chambers 56 depicted in Fig. 5.
- the liquid-collecting inner surface of the rotating-assembly shell 36, the scoop tubes 122 and 124, the transfer-valve assembly 128, and the spray arms 58 form a guide that directs unevaporated liquid along a recirculation path that returns it to the evaporation chambers 56.
- this guide cooperates with the main pump 100, the counterflow heat exchangers 102, 104, 106, 108, and 110, the degasser 112, the filter assembly 114, and the tubes that run between them as well as tube 118 and nozzle 120 to form a further guide.
- This further guide directs feed liquid along a make-up path from the feed inlet 12 to the evaporation chambers 56.
- the flow volume through the spray arms 58 should therefore be so controlled as to leave that film as thin as possible.
- the flow rate through those spray arms is chosen to be just high enough to keep the surfaces from drying completely between periodic wetting sprays from a scanner 140 best seen in Fig. 9.
- the scanner includes two scanner nozzles 142 and 144 that provide a supplemental spray at two discrete (but changing) heights within the rotary heat exchanger.
- Fig. 14 is a cross-sectional view, with parts removed, of the vapor-chamber housing 40's lower interior.
- Fig. 14 depicts the valve member 130 in the closed state, but when the valve member 130 is in its opposite, open state, it permits flow not only into the spray tubes' ports 132 but also into a path through a separate feed conduit 150 by way of an internal passage not shown into a vertically extending tube 152.
- a telescoping conduit 154 that slides in tube 152 conducts the flow, as best seen in Fig. 9, through the yoke 148 and into the scanner 140. So these elements guide liquid along a further branch of the recirculation and make-up paths.
- the irrigation rate required to keep the plates wetted is about 4.0 gal./hr./plate if the irrigation rate is kept constant.
- Fig. 14 shows that the transfer-valve assembly 128 is provided on a vapor-chamber base 160 sealingly secured to the vapor-chamber housing 40's lower annular lip 162. Together that lip and the vapor-chamber base can be thought of as forming a secondary, stationary sump that catches any spillage from the main, rotating sump.
- the heating coil mentioned above for use on startup may be located in that sump and raise the system to temperature by heating sump liquid whose resultant vapor carries the heat to the remainder of the system.
- the vapor-chamber base 160 forms is a vertical transfer-pump port 164, through which the drive rod 146 extends. That rod extends into a transfer pump 166 that Fig. 14 omits but Fig. 15 illustrates in cross section.
- the transfer pump 166 includes an upper cylinder half 168 that forms a cylindrical lip 169, which mates with the transfer-pump port 164 of Fig. 14. It also forms a flange 170 by which a bolt 172 secures it to a corre- sponding flange 174 formed on a lower cylinder half 176.
- Fig. 15 also depicts a mounting post 178, which is one of two that are secured to Fig. 14's vapor- chamber base 160 and support the transfer pump 116 by means of flanges, such as flange 180, formed on the upper cylinder half 168.
- a piston 182 is movably disposed inside the transfer-pump cylinder that halves 168 and 176 form, and a spring 184 biases the piston 182 into the position that Fig. 15 depicts.
- the drive rod 146 is so secured to the piston 182 as to be driven by it as the piston reciprocates in response to spring 184 and fluid flows that will now be described by reference to Fig. 8.
- the filter assembly 114's output is divided between two flows.
- This tube leads to a channel, not shown in Fig. 14, that communicates with an upper section 188, which Fig.
- the pump's lower portion serves as a concentrate reservoir. While the piston is drawing liquid into the refresh-liquid reservoir, it is expelling liquid from the concentrate reservoir through an output port 190 formed, as Fig. 15 shows, by the lower cylinder half 176.
- the lower cylinder half further forms a manifold 192.
- One outlet 194 of that manifold leads to the filter assembly 114, which Fig. 15 omits but Fig. 16 depicts in cross section.
- Fig. 16 shows that the filter assembly includes a check valve 196 that prevents flow into the filter assembly from manifold outlet 194. As Fig. 15 shows, the flow leaving the transfer pump from its lower outlet 190 must therefore flow through the other manifold outlet 198.
- Fig. 8 shows that a tube 200 receives that transfer-pump output.
- a flow restricter 202 in that tube limits its flow and thus the rate at which the transfer- pump piston can descend. By thus limiting the transfer-pump piston 182's rate of descent, flow restricter 202 also limits how much of the filter assembly 114's output flows through tube 186 into the transfer pump 166's upper side, with the result that the transfer pump receives only a small fraction of the filter output and thus of the output from the input pump 100.
- a flow divider comprising a flow junction 203 and another flow restricter 204 so controls the proportion of pump 100's output that feeds counterflow-heat-exchanger module 104's cold side that this cold-side flow approximates the hot-side flow that flow restricter 202 permits: main pump 100's output is divided in the same proportion as the transfer pump 166's output is.
- the resultant relatively low flow rate into module 104 is what enables the entire heat transfer to occur in a single module 104, whereas the higher flow rate through modules 102, 106, 108, and 110 necessitates, their series combination. Because of the flow restricter 202, Fig.
- 15's transfer-pump piston 182 moves downward under spring force at a relatively leisurely rate, taking, say, five minutes to proceed from the top to the bottom of the transfer-pump cylinder.
- the piston descends, it draws the drive rod 146 downward with it, thereby causing Fig. 9's scanner nozzles 142 and 144 to scan respective halves of the rotary heat exchanger's set of evaporation chambers.
- it slides an actuator sleeve 206 provided by yoke 148 along an actuator rod 208.
- a spring mount 210 is rigidly secured to the actuator rod 208 and so mounts a valve-actuating spring 212 that the spring's tip fits in the crotch 214 of a valve crank 216.
- the spring engages the crank in an over- center configuration that ordinarily keeps that actuator rod 208 in the illustrated relatively elevated position.
- the valve crank 216 is pivotably mounted in the transfer-valve assembly and secured to Fig. 12's transfer-valve member 130 to control its state.
- valve crank 216 When the valve crank 216 is in its normal, upper position depicted in Fig. 17, the transfer-valve member 130 is in the lower position, depicted in Fig. 12, in which it directs liquid from the scoop tubes 122 and 124 (Fig. 10) to flow into the spray arms 58 and scanner 140 but not into the filter inlet port 134.
- Fig. 9's yoke 148 continues its descent, though, its actuator sleeve 206 eventually begins to bear against a buffer spring 218 that rests on the spring mount 210's upper end.
- the resultant force on the mount and thus on the actuator rod 208 overcomes the restraining force of Fig. 17's valve-actuating spring 212, causing the valve crank 216 to snap to its lower position.
- Fig. 12's valve member 130 It thereby operates Fig. 12's valve member 130 from its position illustrated in Fig. 12 to its Fig. 18 position, in which it redirects the scoop-tube flow from the spray arms 58 to the conduit 136 that feeds the filter assembly's upper inlet 220 (Fig. 16).
- the flow directed by this transfer-valve actuation into the filter is the entire recirculation flow; that is, it includes all of the liquid that has flowed through Fig. 5's evaporation chambers 56 without evaporating. Since only a relatively small proportion of the liquid that is fed to the evaporation chambers actually evaporates in any given pass, the recirculation flow is many times the feed flow, typically twenty times.
- the pressure that this high flow causes within the filter assembly opens the filter assembly's check valve 196 (Fig. 16) and thereby permits the recirculation flow to back through the outlet 194 of Fig.
- the duration of this refresh cycle will be only on the order of about a second, in contrast to the recirculation cycle, which will preferably be at least fifty times as long, typically lasting somewhere in the range of two to ten minutes.
- the effect of thus redirecting the feed and recirculation flows is to replace the rotary heat exchanger's liquid inventory with feed liquid that has not recirculated.
- the rotary heat exchanger continuously removes vapor from the evaporation side, leaving impurities behind and sending the vapor to the condensation side. So impurities tend to concentrate in the recirculation flow. Such impurities may tend to deposit themselves on the heat-exchange surfaces.
- the illustrated embodiment periodically replaces essentially the entire liquid inventory on the rotary heat exchanger's evaporation side. This results in an evaporator-side concentration that can average little more than half the exhaust concentration. So less water needs to be wasted, because the exhaust concentration can be higher for a given level of tolerated concentration in the system's evaporator side. As the transfer-pump piston rises rapidly, it slides Fig. 9's actuator sleeve 206 upward rapidly, too.
- the sleeve begins to compress a further buffer spring 226 against a stop 230 that the actuator rod 208 provides at its upper end.
- the resultant upward force on the actuator rod 208 overcomes the restraining force that Fig. 17's valve-actuating spring 212 exerts on it through the spring mount 210, and the actuator rod rises to flip the valve crank 216 back to its upper position and thus return the transfer valve 130 to its normal position, in which the recirculation flow from Fig. 9's scoop tubes 122 and 124 is again directed to the spray arms and scanner. So the unit returns to its normal regime, in which the transfer pump slowly expels concentrate from its concentrate reservoir and draws feed liquid through the feed-liquid storage path to its refresh-liquid reservoir.
- Fig. 17's valve-actuating spring 212 overcomes the restraining force that Fig. 17's valve-actuating spring 212 exerts on it through the spring mount 210, and the actuator rod rises to flip the valve crank 216 back to its upper position and thus return the transfer valve
- tube 200 shows, tube 200, counterflow-heat-exchanger module 104, and a further tube 232 guide the concentrate thus expelled along a concentrate-discharge path from manifold outlet 198 to the concentrate outlet 16.
- different refresh-cycle frequencies may be used in different installations.
- some embodiments may be designed to make that fre- quency adjustable.
- some embodiments may make the piston travel adjustable by, for instance, making the position of a component such as Fig. 9's stop 230 adjustable.
- that travel also controls scanner travel, and any travel adjustability would instead be used to obtain proper scanner coverage. So one may instead affect frequency by adjusting the force of Fig. 15's transfer-pump spring 184. This could be done by, for instance, making the piston 182's position on the drive rod 146 adjustable. Refresh-frequency adjustability could also be provided by making the flow resistance of Fig. 8's flow restricter 202 adjustable.
- flow restricter 204 which balances the two counterflow- heat-exchanger flows to match the relative rate of concentrate discharge, would typically also be made adjustable if the refresh-cycle frequency is.
- the flow re- stricters could take the form of adjustable bleed valves, for instance.
- a condensate pump 238 drives this flow. After being cooled by flow through the serial heat-exchanger-module combination, the cooled condensate issues from module 102's "hot"-water outlet 102 H _ou ⁇ and flows through a pressure- maintenance valve 240 and the concentrate outlet 16. Valve 240 keeps the pressure in the hot sides of counterflow heat exchangers 102, 106, 108, and 110 higher than in their cold sides so that any leakage results in flow from the pure-water side to the dirty-water side and not wee versa.
- the main pump 100's drive is controlled in response to a pressure sen- sor 242, which monitors the rotary heat exchanger's evaporator-side pressure at some convenient point, such as the transfer valve's interior chamber.
- tubes to the drain outlet 18 may be provided from elements such as the pump, pressure-maintenance valve, and sump. It can be seen from the description so far that the counterflow-heat- exchanger modules 102, 104, 106, and 108 act as a temperature-transition section.
- the rotary-heat-exchanger part of the fluid circuit is a distiller by itself, but one that relies on a high-temperature input and produces high-temperature outputs.
- the counterflow-heat-exchanger modules make the transition be- tween those high temperatures and the relatively low temperatures at the feed inlet and condensate and concentrate outlets.
- the counterflow-heat-exchanger modules in essence form two heat exchangers, which respectively transfer heat from the condensate and concentrate to the feed liquid.
- Fig. 19 which is an isometric view of counterflow heat exchanger 102 with parts removed, shows tubes that provide its cold-water inlets 102C_IN and 102c_ou ⁇ . It also shows the hot-water outlet 102H_OUT but not the hot-water inlet, which is hidden.
- Fig. 20 is a cross section taken through the cold-water inlet 102 c _iN and the hot-water outlet 102 H _ou ⁇ - That drawing shows that heat exchanger 102 includes a generally U-shaped channel member 250, which provides an opening 252 that communicates with the heat exchanger's "hot"- side outlet. Similar openings 254 in a cover 258 and gasket 260 ( both of which Fig.
- a folded stainless-steel heat-transfer sheet 262 provides the heat-exchange surfaces that divide the cold-water side from the hot-water side, and elongated clips 264 secure the folded sheet's flanges 266, channel-member flanges 268, cover 258, and cover gasket 260.
- spacer combs 270 are provided at spaced-apart locations along the heat exchanger's length.
- One spacer comb 270's teeth 272 are visible in Fig. 20, and it can be seen that the teeth help to maintain proper bend locations in the folded heat-transfer sheet 262.
- Similar teeth 274 of a similar spacer comb at the opposite side of the heat-transfer sheet 262 also serve to space its bends.
- Fig. 19 shows the upper surfaces of diverter gaskets 278, which extend between the upper spacer combs 270 and serve to restrict the cold-water flow to regions close to the folded heat-transfer sheet 262's upper surface.
- Fig. 19 also shows that the module includes end plates 280 and 281. These end plates cooperate with the channel member 250, the cover 258, and the cover gasket 260 to form a closed chamber divided by the sheet 262. Additionally, the leftmost diverter gasket 278 cooperates with the end plate 280 and the cover 258 and cover gasket 260 to form a plenum 282 (Fig. 20) by which cold water that has entered through port 102C_IN is distributed among the heat- exchange-surface sheet 262's several folds.
- End plate 280 similarly cooperates with another diverter gasket 284 (Fig. 20) to form a similar plenum 286 by which water on the hot-water side that has flowed longitudinally along the heat-exchange surfaces issues from the heat exchanger 102 by way of its hot-water outlet 102 H _ou ⁇ - Incoming hot-side water and outgoing cold-side water flow through similar plenums at the other end.
Abstract
Description
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Priority Applications (1)
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---|---|---|---|
AU2002234263A AU2002234263A1 (en) | 2001-01-18 | 2002-01-18 | Distiller employing cyclical evaporation-surface wetting |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/765,263 | 2001-01-18 | ||
US09/765,263 US6802941B2 (en) | 2001-01-18 | 2001-01-18 | Distiller employing cyclical evaporation-surface wetting |
Publications (2)
Publication Number | Publication Date |
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WO2002056989A2 true WO2002056989A2 (en) | 2002-07-25 |
WO2002056989A3 WO2002056989A3 (en) | 2003-03-13 |
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Family Applications (1)
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PCT/US2002/001520 WO2002056989A2 (en) | 2001-01-18 | 2002-01-18 | Distiller employing cyclical evaporation-surface wetting |
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US (3) | US6802941B2 (en) |
AU (1) | AU2002234263A1 (en) |
WO (1) | WO2002056989A2 (en) |
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- 2001-01-18 US US09/765,263 patent/US6802941B2/en not_active Expired - Fee Related
-
2002
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- 2002-01-18 AU AU2002234263A patent/AU2002234263A1/en not_active Abandoned
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2004
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2005
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Also Published As
Publication number | Publication date |
---|---|
US20050121302A1 (en) | 2005-06-09 |
US20040222079A1 (en) | 2004-11-11 |
US6802941B2 (en) | 2004-10-12 |
US7641772B2 (en) | 2010-01-05 |
AU2002234263A1 (en) | 2002-07-30 |
WO2002056989A3 (en) | 2003-03-13 |
US20020092759A1 (en) | 2002-07-18 |
US7368039B2 (en) | 2008-05-06 |
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