GB2619110A

GB2619110A - Separation device

Info

Publication number: GB2619110A
Application number: GB2217780.2A
Authority: GB
Inventors: Stephen Bell Ian
Original assignee: Individual
Current assignee: Individual
Priority date: 2022-11-28
Filing date: 2022-11-28
Publication date: 2023-11-29
Also published as: GB202217780D0

Abstract

A separation device for removing salt from a saline solution comprises: a mixer for mixing a gas, such as air, with a fluid containing dissolved solids; a mechanical compressor, such as a piston compressor 484, capable of compressing the gas to heat the gas to a temperature sufficient to vaporise the fluid with dissolved solids mixed in the gas; and a separator 1400, such as a cyclonic separator (468, Fig. 4A) or filter 1408, to subsequently separate the vapourised fluid from the solids. The mechanical compressor comprises a pressure chamber 428 and at least one valve (600, 602, Fig. 8A) to allow the gas to enter and/or exit the pressure chamber. A timing device operates the valve(s) to allow the gas with vapourised fluid to exit the pressure chamber when the temperature of the gas has been increased to a temperature sufficient to vaporise the fluid. The mixer is capable of mixing the fluid containing dissolved solids with the gas either prior to the gas entering the pressure chamber or when the gas is in the pressure chamber. A method of desalinating a salt solution (e.g. seawater) is also described.

Description

SEPARATION DEVICE

The present invention relates to a separation device for extracting solids from a fluid in which they at dissolved, and in particular, to the use of a med-anical compressor in such a separation Eevice and, more in particular, to the use of a separation device comprising a mechanical compressor to desalinate salt water.

One tine of a fluid with dissolved solids is salt water (i.e. salt dissolved within water) such as sea wate-(i.e. sodium chloride dissolved in water).

One tepe of mechanical cart pressor is a piston compressor which can be used in a separation device to desalinate salt water.

A problert with existing designs of desalination apparatus (in particular, for the extraction of drinkable water from sea water) is that they are complex in their construction and are expensive to cperate. Otter, the apparatus requires constant monitoring and regular servicing y trained personnel using specific service parts. Such apparatus can utilise a number of different types of desalination technology, suci as, solar distillation, natural evaporation, vacuum distillation, thermal distillation, multi-stage flash distillation, multiple-effect distillation, vapor-conpression distillation, wave-powered distillation, membrane distillation, forward and reverse osmosis, freeze-thaw desalination and electrodialysis membranes.

Typically, such apparatus is constructed to operate on an industrial scale. Whilst that is advantageous for providing drinking water for a large population, such as a town or a city, it is often not practical for use in situations where a small-scale operation is required, such as on a farm.

Many known solutions for desalination focus on the efficiency of the system i.e. the amount of energy 3ut in versus the amount of desalinated water eittracted. This leads to complex solutiors. Again, whilst this may be acceptable on apparatus used on an industrial scale, it hinders the use of such apparatus in small operations, especially where the personhel operat ng such apparatus are often not trained to use such apparatus and the operation of such apoaratus is not the peisonnel's primary function.

The present invention is intended to provide a predominantly mechanical device, and clealry, a pure', mechanical device which can desalinate salt water. A predominantly or purely mechanical device would be easy and cheap to construct and operate. It is intended to minimise tie number of component parts, thus providing reliability and minimisingthe need for repa r. Such a design can also be made small for use in small scale operations.

The presert irvention comprises a mechanical compressor in a separation device to desalinate salt water. The advantage of such a device is that it can be made to have a purely mechanica construction or a substantially mechanical construction. Such a device can be made to be easy to operate and require minimal maintenance and repair.

Three pieces cf relevant prior, art will now be briefly described with reference to Figures 1 to 3, the first aril° providing technology which can be utilised to desalinate water and the third one which 'uthises piston compression to heat a gas.

The first piece of prior art is a spray drying apparatus will now be described with reference to Figure 1.

Spray drying is commonly used in the production of food stuffs or pharmaceuticals for the extraction of solids from a fluid. Examples of solids are salts or chemicals dissolved in the fluid or a powered solid suspended in the fluid. The solids are extracted from the fluid by, first, atomizing the fluid containing the solid by passing it through an atomizer and then, second, spraying the atomised fluid and solids into a hot drying gas medium, for example, air. The atomised fluid is then rapidly evaporated and subsequently separated from the solids. The solids are then collected. The evaporated fluid can then be condensed to form a liquid again. The spray drying process provides a rapid, continuous, cost-effective, reproducible and scalable process for the extraction of solids from a fluid. Such a process can be utilised to separate salt from water in wiich it is dissolved and as such, can be used to desalinate sea water.

Figure 1 shows a schematic diagram of a spray drying apparatus to show the basic principles of the construction of the spray drying apparatus.

Referring to Figure 1, the spray drying apparatus comprises a tank 100 in which is inserted the fluid 102 containing the solids. A first pipe 104 connects the tank 100 to a pump 106. A second pipe 108 connects the pump 106 to a housing 110 which forms a mixing chamber 112. The second pipe 108 pas>es through the wall of the housing 110 and extends into the mixing chamber 112. A nozzle 114 is attached to the end of the second pipe 108 inside of the mixing chamber 112.

An air pump 116 is attached t3 a third pipe 118. The third pipe 118 connects between the air pump 116 and an air heater 120. A fourth pipe 122 attaches between the air heater 120 and the housing 110 of the mixing chamber 112, the end of the fourth pipe 122 connecting to an aperture 124 formed through the wall of the housing 110.

A fifth pipe 126 attaches between the housing 110 of the mixing chamber 112 and a cyclonic separator 128, one end of the fifth pipe 126 connecting to an aperture 127 formed through the wall of the housing 110, the other end of the fifth pipe 126 connecting to an aperture 125 formed through the wail of the cyclonic separator 128.

The cyclonic separator 128 has a separation chamber 130 which tapers at its lower end to a sixth solids exit pipe 131 A seventh vapour exit pipe 134 connects to an aperture 136 formed through an upper part of the wall of the cyclonic separator 128.

The operation of the spray drying apparatus will now be described.

In use, tie air pump 116 sucks in air from the surrounding atmosphere into the third pipe 118 The air is blown through the third pipe 118 and into the air heater 120. The air passes through the air heater 120 wtere it is heated to a high temperature. The heated air is then blown through the fourth pipe 122, through the aperture 124 and into the mixing chamber 112.

The tank 100 is filled with a fluid 102 containing the solids (such as sea water). The fluid 102 containing the solids then flows into the pump 106. The pump 106 then pumps the fluid 102 with the solids at high pressure through the second pipe 108 and the nozzle 114 and into the mixing chamber 112. As the Fuld 102 with the solids passes through the nozzle 114, the fluid 102 is atomized into a spray 138. The spray 138 mixes with the heated air where it is rapidly heated, the fluid 138 vaporising as it does so. The vaporised fluid 102 and solids then pass out of the mixing chamber 112 through the fifth pipe 126 and into the separating chamber 130 where it is rotated rapidly to cyclonically separate the solids from the vaporised fluid 102. The solids then exit the separation chamber 130 through the sixth solids exit pipe 132. The vaporised fluid 102 then exits the separation chamber 130 through the seventh vapour exit pipe 134 where the vaporised fluid 102 can be cooled to return it to a liquid.

The second piece of prior art is a pulse combustion spray dryer which will now be described with reference to Figure 2.

Figure 2 shows a schematic diagram of a pulse combustion spray dryer to show the basic principles of the const-uction of the pulse corn Dustion spray dryer.

A pulse combustion spray dryer comprises a pi Ise combustor which produces a series of pulses of hot exhaust gases and a pulse spray cryer.

Referring to Figure 2, the pulse spray dryer comprises a tank (not shown) in which is inserted the fluid containing the solids. A first pipe 204 connects the tank to a pump 206. A second pipe 208 connects the pump 206 to a housing 210 which forms a mixing chamber 212. The second pipe 208 passes through the wall of thE housing 210 and extends into the mixing chamber 212. A nozzle 214 is attached to the end of the second pipe 208 inside of the mixing chamber 212.

Mounted on top of the housing 210 is a pulse corr bustor 250 comprising an inner wall 252 and an outer wall 254. The inner wall 252 forms a combustion chamber 256. The combustion chamber 256 is connec:ed to the mixing chamber.212 via a third pipe 258. Mounted on the top on the inner wall 252 is a valve 260. The tea of the valve 260 is connected to a fourth pipe 262 through which a combustible fuel is fed into the valve 260.

An air filter 264 is connected to an air pump nti via a fifth pipe 266. The air pump 116 is attached to a sixth pipe 218. The sixth pipe 216 cc nnects between the air pump 216 and the outer walk 254. When the air pump 216 is activated, air is drawn from the environment into the filter 264, through the fifth pipe 266, through the air pump 216, through the sixth pipe 218 and into a separation chamber 268 formed between the inner wall 252 and the outer wall 254. Air in the separation chamber 268 is in direct contact with side of and capable of being drawn into the valve 260.

The valve 260 injects a mixture of the combustible fuel and air into the combustion chamber 256 at pre-determine time intervals.

Mounted inside the combustion chamber 256 is a spark plug (not shown) or some other type of ignition device. After the valve 260 injects a mixture of the combustible fuel and air into the combustion chamber 256 at pre-determine time intervals, the spark plug ignites the fuel/air mixture inside of the combustion cham be-256.

The pulse spray dryer:urther comprises a seventh pipe 226 which attaches between the housing 210 of the mixing chamber 212 and a cyclonic separator 228, one end of the seventh pipe 126 connecting to an aperture formed through the base wall of the housing 210, the other end of the sever th pipe 226 connecting lo zn aperture formed through the wall of the cyclonic separator 228.

The cyclonic separator 228 has a separation chamber 230 which tapers at its lower end to an eighth solids exit pipe 232.

A ninth vapour exit pipe 234 connects to an aperture formed through an upper part of the wall of the cyclonic separator 228 to an apertu-e formed through a lower part of a wall of a condenser 270. The condenser 270 forms a condensing chamber 272 which has a tapered section 274 at its lower end where it connects 70 a tenth liquid exits pipe 276.

An eleventh air exit pipe 278 connects between the top of the condenser 270 and an exit fan 280. A twelfth pipe 28 a connects between the exit fan and an exhaust duct 284.

The operation of the pulse combustion spray dryer will now be described.

Combustible fuel is fed into the valve 260. The air pump 216 draws air into the filter 264, through the fifth pipe 266, through the air pump 216, through the sixth pipe 218, into the separation chamber 263 formed between the inner wall 252 and the outer wall 254 and then into the valve 260. The valve 260 then injects a mixture of combustible fuel and air into the combustion chamber 256 at pre-determine time intervals. After the valve 260 injects a mixture of the combustible ft-el and air into the combustion chamber 256 at pre-determine time intervals, the spark plug ignites the fuel/air mixture inside of the combustion chamber 256 to generate a series of combustions, which in turn proouce a series of pulses of hot exhaust gas. The pulses of hot-exhaust gases created by the combustions pass from the combustion chamber 256 through the third pipe 258 into the mixing chamber 212. The entry of the series of pulses of hot eThaust gas into the mixing chamber 212 generate a gas stream of pulsed hot exhaust gas insice of the mixing chamber 212.

The tank is filled with fluid containing the solids. The fluid containing the solids then flows into the pump 206. The pump 206 then pumps the fluid with the solids through the second pipe 208 and the nozzle 214 and into the mixing chamber 212. As the fluid with the solids passes through the nozzle 2144 it is atomized into a spray 238. The spray 238 mixes with the gas stream of pulsed hot exhaust gas where it is rapidly heated, the fluid vaporising as it does so, the pulsation of the gas stream assisting the atomisation. The vaporised fluid and solids then pass out of the mixing clamber 212 through the seventh pipe 226 and into the separating chamber 230 where it is rotated rapidly to cyclonically separate the solids from the vaporised fluid. The solids then exit the separation chamber 230 through the eight solids exit pipe 232. The vaporised fluid the exits the separation chamber 230 through the ninth vapour exit pipe 234 where the vaporised fluid is condensed in the condensing chamber 272 to return it to a liquid which an then exit the condensing chamber 272 via the tenth liquid exits pipe 276. The exhaust ws can then be removed from the condensing chamber 272 via the exit fan 280 and exhaust duct 284.

A pulse combustion spray dryer has been used for extracting salts from a fluid, and as such, can be used to desalinate sea water. The paper entitled "Application of Pulse Combustion Technology in Spray Drying Frocess" by I Zbicinski, I Smucerowicz, C Strumillo and C Crowe of Technical University of Lodz, Faculty of Process and Environmental Engineering or Washington State University. School of Mechanical and Material Engineering, describesthe use of such apparatus.

A problem with pulse omlit stion spray drying apparatus is that it requires the provision of a combustion fuel in order to operate. Another problem is that the fluid with the solid, once atomised are mixed with thE exhaust gases of the burnt combustion fuel which may not be desirable.

The third piece of prior art is 3 four-stroke diesel engine will now be described in relation to Figures 3A to 3D.

Referring to Figures 3A to 313 a diesel engine comprises a cylinder block 300 which is mounted on a crank shaft housing 302. The cylinder block 300 comprises an elongate cylinder 304 having a longitudinal axis and a uniform circuiar cross section, in a direction perpendicular to the axis, along the length of the cylinder 304. Slideably mounted within the cylinder 304 is a piston 306 of circular cross section of similar size to that of the cylinder 304. Mounted around the external sidewall of the piston 306 are piston rings (not shown) which form a seal between the external sidewall of the piston 306 and the internal side wall of the cylinder 304. The lower section of the cylinder 304 opens lnto a chamber 308 formed inside of the crank shaft housing 332. A rotatable crank shaft 310 is mounted inside of the crank housing 302 which is capable of rotating about an axis which extends perpendicularly to the longitudinal axis of the cylincer 304. A connecting rod 312 is pivotally attached to the crank shaft 310 at a lower end, the axis of pivot being parallel to but eccentrically off set from the axis cf rotation of the crank shaft 310. The other upper end of the connecting rod 312 is pivotally attached to the piston 306, the axis of pivot being parallel to the axis of rotation of the crank shaft 310. Rotatior of the crank shaft 310 results in a linear reciprocation motion of the piston 306 inside the cylinder 304 along the longitudinal axis of the cylinder 304 in well know manner. A counterweight 31415 eccentrically mounted on the crank shaft 310 to counteract any vibrations generated by the eccentric connection of the lower end of the connecting rod 312 as the crank shaft 310 rotates.

The upper section of the cylinder 304 is terminated by an upper wall formed by the top of the cylinder block 300. A combustion chamber 318 is formed inside of the upper section of the cylinder which is bounded by the upper wall of the cylinder block 300 at the top, by the inner side wall a' the cylinder 304 at the sides, and the top of the piston 306 at the bottom. As the piston 306 reciprocatingly slides up and down within the cylinder 304, the volume of tie chamber 318 varies, the volume of the chamber 318 being the smallest when the piston 306 is in its highest position, closest to the upper wall of cylinder block 300; the volume of the chamber 318 being the largest when the piston 306 is in its lowest position, closest to the crank shaft 310.

A first inlet passage 316 is formed through the upper wall which allows filtered air from outside of the cv finder block 300 to enter into the combustion chamber 318. A first slideable valve 320 is able to open and close the inlet passage 316. Movement of the valve 320 is controlled using a first cam shaft (not shown) in well-known manner.

A second outlet passage 326 is formed through the upper wall which allows fumes from the burnt d;esel tc exit from the combustion chamber 318 to outside of the cylinder block 300. A second slideable valve 322 is able to open and close the outlet passage 326. Movement of the valve 322 is controlled using a second cam shaft (not shown) in well-known manner.

An injector nozzle 324 in mounted in the upper wall between the inlet and outlet passages 316, 32E througn which diesel fuel can be injected in the combustion chamber 318 in well-known manner.

Figures 3A to 3C show the combustion cycle of the engine.

Figure 3A shows the start of the cycle. At the start, the first valve 320 opens the first irnet passage 316. The second valve 322 closes the second outlet passage 326_ At the star of the cycle, the piston 306 slides downwardly (Arrow A) in the cylinder 304 due to the rotation of the crank shaft 310, increasing the volume of the combustion chamber 318. As the volume of the combustion chamber 318 increases, air is drawn into the combustion chamber 318 through the fit inlet passage 316.

Figure 3B shows the second stage of the combustion cycle. During the second stage, the first valve 320 closes the first inlet passage 316. The second valve 322 maintains the second outlet passage 326 closed. In the second stage, the piston 306 slides upwardly (Arrow B) in the cylinder 304 due to the continued rotation of the crank shaft 310, decreasing the volume of the combustion chamber 318. As the volume of the combustion chamber 318 decreases, the air in the combustion chamber 318 is compressed as both the first inlet passage 316 and second outlet passage 326 are closed. As the air is compressed, its pressure and temperature;n the combustion chamber 318 increases.

Figure 3C shows the third stage of the combustion cycle. During the third stage, the first valve 320 maintains the first inlet passage 316 closed. The second valve 322 also maintains the second outlet passage 326 closed. In the third stage, the piston 306 moves to its upper most position:referred to as "top dead centre") in the cylinder 304. The volume of the combustion clamber 318 is the smallest when the piston 306 is in this position. The tempe-ature ard pressure of the air in the combustion chamber 318 are also at their highest. When the piston 306 is at top dead centre, diesel fuel is injected into the combustion chamber 318 through the nozzle 324. As the diesel fuel enters the combustion chamber 318, it begins to burn due to the elevated temperature of the air in the combustion chamber 318.

The ignition of the fuel is caused by the elevated temperature of the air in the combustion chamber 318 due to the mechanical compression of the air (the diesel engine i 3 a so-called "compression-igntion engir e"). The burning of the diesel fuel causes the piston 306 to stcrt moving downwa-dly (Arrow C.), causing the crank shaft 310 to continue to rotate.

Figure 30 shows the end of the cycle. During the fourth stage, the first valve KO maintains the first inlet passage 316 closed. The second outlet valve 322 opens the second outlet passage 326. During the fourth stage, the piston 306 slides upwardly (Arrow D) in the cylinder 304 due to the rotation of the crank shaft 310, decreasing the volume of the combustion chamber 318. As the volume of the combustion chamber 318 decreases, the fumes generatec oy the burn ng of the diesel fuel in the air in the combustion chamber 318 is expelled from the combustion chamber 318 through the second outlet passage 326.

Diesel engines work by compressing only the air (not a mixture of air and diesel fuel). A typical compression ratio of a diesel engine is between 14 to 1 and 22 to 1. This increases the air temperature nside the co-nbustion chamber 318 to such a high degree that when atomised diesel luel is injected into the combustion chamber 318, it ignites spontaneously. The temperature nside of the combustion chamber 318 when the air is fully compressed s typically greater trial 526 degrees Centigrade (>979 degrees Fahrenheit).

It will be appreciated that there are also two stroke diesel engines. These also ignite atomised diesel fuel by first compressing the air inside of a combustion chamber to increase the temperature of the compressed air and then secondly injecting the diesel fuel into the combustion chamber-to be ignited by the high temperature of the compressed air.

Accordingly, there is providec a separation device in accordance with claims 1 or 2.

Accordingly, there is providec a method of desalinating a salt solution using a separation device for removing salt fromi a saline solution comprising: a mixer; a mechanical conpressor; a separator; 1. wherein a gas is mixed a fluid with dissolved solids in the mixer; 2. wherein tie mechanical compressor compresses a gas to heat the gas; 3. wherein tie heated gas vaporizes the fluid; 4. wherein tie separator separates the vapourised fluid from the solids; 5. condensir g the vapourised fluid.

Relevant prior art (described above) and eleven embodiments of the invention (describec below) will now be cescribed with reference to tie following drawings of which: Figure 1 shows a prior art des-gn of spray drying a cparatus; Figure 2 shows a prior art des gn of pulse combustion spray dryer; Figure 3A shows a vertical cross section of a prior art four-stroke diesel engine when the piston is moving downwardly (Arrow A) within the cylinder to draw air into the combustioi chamber of the cylinder; Figure 3B shows a, vertical cross section of the four-stroke diesel engine of Figure 3A when the piston is moving upwarcly (Arrow B) within the cylinder to compress the air within the combustion chamoer of the cylinder; Figure 3C shows a vertical cross section of the four-stroke diesel engine of Figure 3A when the piston is at top dead centre within the cyLinder before moving downwardly (Arrow C) with n the cylinder after the ignition of diesel fuel and air in the combustion chamber of the cylinler; Figure 3D shows a vertical cross section of the four-stroke diesel engine of Figure 3A when the piston is moving upwardly (Arrow D) within the cylinder to expel burnt diesel fuel and air from the combustion chamber of the cylinder; Figure 4A shows a vertical cross section of a separation device according to a first embodimert of the present invention comprising a piston compressor with the piston is at its highest position with the compression chamber at its largest volume filled with air at atmospheric pressure and fluid with dissolved solids enters the compression chamber; Figure 48 shows a vertical cross section of the separation device of Figure 4A when the piston is mcving downwardly (Arrow IV), reducing the volume of the compression chamber to compress and heat the air within the compression chamber in order to vaporise tie fluid; Figure 4C shows a vertical cross section of the separation device of Figure 4A when the piston is at its lowest poslion and the volume of The compression chamber at its smallest with the air w thin the compression chamber fully compressed and heated and the fluid totally vaporised; Figure 4D shows a vertical cross section of the separation device of Figure 4A when the piston is moving upwardly (Arrow 0), increasing the volume of the compression chamber whilst it is being filled with air at atmospheric pressure; Figure 5 shows a vertical cross section of a second type of separation device according to a second embodimeit of the present invention which comprises four piston compressors; Figure 6 shows a vertical cross section of a third type of separation device according to a third embodiment of the present invention which comprises a separator which uses a filter; Figure 7A Sh3W5 a vertical cross section of a fourth embodiment of separation device which comprises a separator which uses a filter and in which the piston of the piston compressor is at its highest position; Figure 78 shows a vertical cross section of the third embodiment shown in F:gure 7A which comprises a separator which uses a filter and in which the piston of the piston compressor is at its owest position; Figure 13A shows a vertical cross section of a piston compressor of a fifth embodiment of separation device which comprises two electronically controlled valves; Figure 88 shows the status of the two valves in comparison with the volume of the comp -ession chamber; Figure 9A shows a vertical cross section of a sixth embodiment of the present invention which comprises a s ngle three way electronically controlled valve; Figure 9B shows the status of the three way electronically controlled valve in comparison with tie volume of the compression chamber; Figure 10A shows a vertical cross section of a seventh embodiment of the present invention comprising a propellor to compress the air; Figure 108 shows the status of the valve in comparison with the pressure of the gas within the pressure chamber; Figure 11A shows a vertical cross section of a seventh embodiment of the present ir.vention comprising a propellor to compress the air; Figure 118 shows a first example the status of the two valves in comparison with the pressure of the gas within the pressure chamber; Figure 11C shows a second example the status of the two valves in comparison with the pressure of the gas within the pressure chamber; Figure 12 shows an example of an impeller; Figure 13 shows an example of the use of a bellow to compress air; and Figure 14 shows an example of a pump to compress air.

The first embodiment Of the invention will now be described with reference to Figures 4A to 40. The first embodiment of the separation device comprises a piston compressor.

Referring to Figures 4A to 4D, the separation device comprises a piston compressor 484 which produces a series of pulses of compressed hot air, together with vapourised fluid and solids, and a separator 490.

The piston compressor 484 comprises a cylinder block 400 which is mounter.' below a crank shaft housing (not shown). The cylinder block 40C comprises an elongate cyl-nder 404 having a longitudinal axis and a uniform circular cross section, in a direction perpendicular to the axis, along the length cf the cylinder 404. Slideably mounted within the cylinder 404 is a piston 406 of circular cross section of similar size to that of the cylinder 404. Mounted circumferentially around the internal wall of the cylinder 404 towards the top of the cylinder 404 are two seals 408 which form a seal between the external sidewall of the piston 406 and the inner side wall of the cylinder 404 and which prevent any gases from passing tha seals 408. The seals 408 slidE along the external sideman of the piston 406 when the piston 406 reciprocates within the cylinder 404. The upper section of the cylinder 404 c pens into a chamber 410 formed ir side of the crank shaft housing. The lower section of cylinder 404 forms a compression chamber 428, the compression chamber 428 being defined oy the lower internal walls of the cylinder 404 and a lower surface 417 of the piston 406.

A rotatable crank shaft 41.2 is mounted inside of the crank shaft housing wh-ch is capable of rotating about an axis which extends perpendicularly to the longitudinal axis of the cylinder 404. A connecting rod 414 is pivotally attached to the crank shaft 412 at an upper end, the axis of pivot being parallel to but eccentrically off set from the axis of rotation of the crank shaft 412. The lower enc of the connecting rod 414 is pivotally attached to a first valve 416 formed in the top of the piston 406, the axis of pivot being parallel to the axis of rotation of the crank shaft 412. Rotation of the crank shaft 412 results in a inear reciprocation motion of the piston 406 inside the cylinder 404 along the longitudinal axis of the cylinder 404 in well known manner. A counterweight (not shown) is eccentrically mounted on the crank shaft 412 to counteract any vibrat ons generated by the eccentric connection of the upper erd of the connecting rod 414 as the crank shaft 412 rotates.

The first valve 416 comprises a valve chamber 418 formed in the top of the piston 406. The valve chamber 418 is arcular in cross-section (perpendicularly to the longitudinal axis of the cylinder 404) with a flat lower side wall 420 and a flat upper side wall 422. A lower elongate tubular passage 424 extends from the lower side wall of the valve chamber 418 through the piston 406 to the lower surface 417 of the piston 406. The lower elongate tubular passage 424 allows air to freely pass between the valve chamber 418 and the compression chamber 428 of the cylinder 404.

A first upper elongate thbular passage 434 extends from the uppe: side wan 422 of the valve chamber 418 through the piston 406 to the upper surface of the piston 406 The first upper elongate passage 434 extends parallel to ane is co-axial with the longitudinal axis of the cylinder 404.

A second upper elongate tubular passage 436 extends from the upper side wall 422 of the valve chamber 418 through the piston 406 to the upper surface of the piston 406. The second upper elongate passage 436 extends parallel to and but is offset from:he longitudinal axis of the cylinder 404. The second upper elongate tubular passage 436 allows air to freely pass between the valve chamber 418 and the space 410 above the piston 406 facing towards and/or connected to the chamber in the crank shaft housing.

Mounted inside of the valve chamber 418 are two valve disks 430, 432. The tcp disk 430 is mounted on top of the lower disk 432, the two disks 430 432 being integrally 2ormed as one component. The valve disks 430, 432, are circular in cross-section (perpendialarly to the longitudinal axis of the cylinder 404), both having the same constant thickness (parallel to the longitudinal axis of the cylinder 404), both being sma;ler in diameter that the valve chamber 418, the top disk 430 being smaller in diameter than the lower disk 432.

The top disk 430 is rigidly attached to the lower end of a slide rod 438. The slide rod 438 is sldieably mounted inside of a side bearing 440 mounted within the first upper tubular passage 434. The slide rod 438 extends parallel to and is co-axial with the longitudinal axis of the cylinder 404 and is capable of sliding axially along its longitudinal axis within the slide bearing 440. The upper end of the slide roc 438 is pivotally attached to the lower end of the connecting rod 414, the axis of pivot being parallel to tne axis of rotation of the crank shaft 412. Rotation of the crank shaft 412 results in a linear reciprocation motion of the slide rod 438 inside of the slide bearing 440.

A weak helical spring 442 is sandwiched between the upper side wall 422 of The valve chamber 418 and top surface of the disk 432, the lower end of the spring 442 surrounding the top disk 430. The spring 442 biases the two valves disks 430, 432 towards their lowest position in the valve chamber 418.

A seal 444 is mounted on the lower surface of the lower disk 432. When the two valve disks 430, 432 are in their lowest position (as shown in Figures 4B and 4C), the sea 444 is sandwiched between the lower surface of the lower disk 432 and the lower fat side wall 426 of the valve chamber 418. When the seal 444 and valve disks 430, 432 are in this position, the entrance to the lower elongate tubular passage 424 is sealed, thus preventing air from passing between the valve chamber 418 and the compression chamber 428 of the cylinder 404. When the two valve disks 430, 432 are in their highest position (as shown in Figures 4A and 40), the seal 444 is located away from the lower flat side wall 420 of the valve chamba418. When the seal 444 and valve disks 430, 432 are in this position, the entrance to the lower elongate tubular passage 424 is oper, thus allowing air to pass freely between the valve chamber 418 and the compression chamber 428 of the cylinder 404.

When the crank shaft 412 rotates to move the piston 406 downwardly inside of the cylinder 404, the crank shaft 412, causes the slide rod 438 to slide downwardly inside the slide bearing 440, moving the two valve disks 430, 432 downwardly inside of the valve chamber 418 until the two valve disks 430,432 are in their lowest position (as shown n Figures 4B and 4C) with the seal 444 sandwiched between the lower surface of the lower disk 432 and the lower flat side wall 420 of the valve chamber 418. As the crank shaft 412 continues to rotate to move the piston 406 downwardly inside of the cylinder 404, the crank shaft 412, continues to push the slide rod 438 downwardly, the slide rod 438 pushing the valve disks 430, 432 downwardly, which in turn push the piston 406 downwardly inside of the cylinder 404 by their engagement of the lower wall 420 of the valve chamber 418. As the valve 430, 432 pushes the piston 406 downwardly, the entrance to the lower elongate tubular passage 424 is sealed, thus preventing air from passing between the valve chamber 418 End the compression chamber 428 of the cylinder 404 as the piston 406 moves downwardly within the cylinder 404.

When the crank shaft 412 rotates to move the piston 406 upwardly inside of the cylinder 404, the crank shaft 412 causes the slide rod 438 to slide upwardly inside the s ide bearing 440, moving the two valve disks 430, 432 upwardly inside of the valve chamber 418 until the two valve disks 430, 432 are in their highest position (as shown in Figures 4A and 4D) with the seal 444 located remotely from flat lower wall 420 of the valve chamber 418 and the upper disk 430 located against the upper flat side wall 422 of the valve chamber 418. As the crank shaft 412 continues to rotate to move the piston 406 upwardly inside of the cylinder 404, the crank shaft 412, continues to pull the slide rod 438 upwardly, the slide rod 438 pulling the valve disks 430, 432 upwardly, which in turn pull the piston 406 upwardly inside of the cylinder 404 by their engagement of the flat upper side wall 422 of the valve chamber 418. As the valve 430, 432 pulls the piston 406 upwardly, the entrance to the lower elongate tubular passage 424 is open, thus allowing air to pass between the valve chamber 418 and the compression chamber 428 of the cylinder 404 as the piston 406 moves upwardly within the cylinder 404 The design of the first valve 416 is such that it acts a timing device for the entry of air into the compression chamber 428. When the piston 406 is moving upwardly, the first,r alve 416 opens, allowing air to enter into the compression chamber 428. When the piston 406 is moving downwardly, tie first valve 416 closes, preventing air entering or exiting the compression chamber 428. A such, the first valve 416 controls when and wher not air can pass through the first valve 416 dependent on the direction of movement of the piston 406 by the crank shaft 412 The lower section of the cylinder 404 is terminated by a lower wall formed by the bottom of the cylinder block 400. The compression chamber 428 is formed inside of the lower section of the cylinder 404 which is bounded by the lower wall of the cylinder block 400 at the bottom, by the side wall of the cylinder 404 at the sides, and the lower surface 417 of the piston 406 at the top. As the piston 406 reciprocatingly slides up and down within the cylinder 404, the volume of the compression chamber 428 varies, the volume nf tne compression chamber 428 being the smallest when the piston 406 is in its low.est position as shown in Figure 4C, closest to the lower inner wall of cylinder block 400, the volume of the chamber 428 being the largest when the piston 406 is in its highest position, c osest to the crank shaft 412, as shown in FigLre 4A.

An inlet 1300 is formed through the side wall of the cylinder 404. The inlet 1300 is located approximately half-way along the length of cylinder 404 such that, when the volume of the compression chamber 428 is at I'S maximum, the inlet 1300 faces into the corn pression chamber 428 below the piston 436 as shown in Figure 4A. A tank (rot shown) in which is inserted a fluid 1304 with dissolved solids, is connected via a pipe 1302 to the inlet 1300. A nozzle (not shown) can be optionally attached to the end of the pipe 1302. A valve 1308 is mounted in the pipe 1302 to ensure that the fluid 1304 with the dissolved solids can only flow one way into the compression chamber 428 and that pressurised air from the compression chamber 428 cannot exit the compression chamber 428 via the inlet 1300. The valve 1308 is opened and closed so that the fluid 1304 with dissolved solids can only flow through the valve 1308 into the sompression chamber 428 at set times. The valve 1308 is mechanical linked (incicated by dashed lines 1306), for example by a cam mechanism or an eccentric drive, to the crank shaft 412 in order to enable the mechanical motion of the crank shaft 412 to utilised in opening and closing the valve 1308. When the crank shaft 412 is at pre-set angular positions, it opens the valve 1308 using the mechanical link 1306. When the crank shaft 412 is at the other angular positions, it closes the valve 1308 using the mechanical link 1306. As such, it can be ensured that the fluid 1304 with the cissolved solids only enters the compression chamber 428 when the piston 406 is at predetermined positions within the cylinder 404.

The inlet 1300 acts as a mixer, mixing the fluid 1304 with dissolved solids with the gas inside of the compression clamber 423.

The fluid 1304 containing the Tssolved solids can flow into the compressior. charnber 428 due to gravity. However, it will be appreciated that a pump (not shown) can be used to assist with the flow of the fluid 1304 with the dissolved solids into the compression chamber 428, the pump pumping the fluid 1304 with the dissolved solids into the compression chamber 428 under a higher p-essure tt an that generated by gravity. Such a pump can be activated when the valve 1308 is open aid deactivated when the valve 1308 is closed.

An outlet 446 is formed through the wall of the cylinder 404. The outlet 446 is located between the two seals 408. Formed in the side of the piston 406 is a U-shaped passage 448. The U shaped passage 448 a nc i he two seals 408 form a second valve 486. The U shaped passage 448 connects between a lower entrance 450 formed in the side wa I of the piston 406 and an upper errrance 452 formed inside wall of the piston 406 and which is located axially above the lower entran:e 450. When the piston 406 reciprocatingly slides up and down, the U-shaped Dassage 448 similarly slides up and down with it. When the Jistor. 406 is at its lowest position as shown in Figure 4C, the lower entrance 450 of the U shaped passage 448 is located below the lower of the two seals 408 whilst the upper entrance 4E2 of the U shaped passage 448 races into the space formed between the two seals 406 towards the outlet 446. When the piston 406 is in this position, the air in the compression chamber 428, which is compressed and heated due to the compression chamber 428 having its smallest volume, is able to pass between the side of the piston 406, enter the lower entrance 450 of the U shaped passage 448, pass through the 1..1 shaped passage 448 and exit the upper entrance 452 of the U shaped 3assage 448, enter the space between the two seals 408 and then enter the outlet 446. The U shaped passage 448 enables the compressed heated air to by-pass the lower of the two seals 408, thus allowing the compressed heated air from the compression chamber 428 to exit via the outlet 446 when the piston 406 is located in this position.

When the piston starts to move upwardly from its lowest position shown in Figure 4C, for a brief period of time, :he upper entrance 452 of the Li shaped passage 448 is located above the upper of the two seals 408 whilst the lower entrance 450 of the U shaped passage 448 faces into the space formed between the two seals 408 towards the outlet 446. During the brief period when the piston 405 is in this position, air located above the piston 406 is able to pass between the side of the piston 406 and the cylinder wall, enter the upper entrance 452 of the U shaped oassage 448, pass through the U shaped passage 448, exit the lower entrance 450 of the U shaped Onssage 448, enter the space between the two seals 408 and then enter the outlet 446.

Similarly, when the piston 405 is moving downwardly and is approaching its lowest position as shown in Figure 4C, for a br El period of time, the upper entrance 452 of the U shaped passage 448 is located above the upper of the two seals 408 whilst the lower entrance 450 oi the U shaped passage 448 faces into the space formed between the two seals 4C8 towards the outlet 446. During the brief period when the piston 406 is in this position, air located above the piston 40E is able tc pass between the side of the piston 406 and the cylinder wall: enter the upper entrance 452 o'the U shapec passage 448, pass through the U shaped passage 448, exit the lower entrance 450 of the U shaped passage 448, enter the space between the two seals 408 and then enter the outlet 446.

During the rest of the cycle of the reciprocation of the piston 406, both of the entrances 450, 452 are located above both sea s 408. As such, the space between the seals 408 is sealed by the side of the piston 406, sealing the entrance to outlet 446. As such, air is unable to pass through the outlet 446.

The design of the second valve 486 is such that it acts a timing device for the exit of air from the compression chamber 423. When the piston 406 has moved to its lowest posbion, the second valve 486 opens, allowing air to exit the compression chamber 428. When the piston 406 subsequently moves upwardly, the second valve 486 closes, preventing air entering Dr exiting the compression chamber 428 through the second valve 486. As such, the second valve 486 controls when and when not air can pass through the second valve 486 dependent on the position cf the piston 406 within the cylinder 404.

The separator 450 comprises a housing 458 which forms a cyclonic separator 468. The cyclonic separator 468 forms a separation chamber 470 which tapers at its lower end to a solids exit pipe 4;2.

The outlet 446 connects to the top of the housing 458 via a connection pipe 466 SD that any air exiting the compression chamber 428 via the outlet 446 can pass through the connection pipe 466 and into:he cyclonic separator 468.

A vapour exit pipe 474 connezts to an aperture formed through an upper part of the wall of the cyclonic separator 468 to a vapour pump 476. The vapour exit pipe 474 is made of material, such as metal, which conducts heat efficiently. Attached, in a heat conductive manner, to the s de of the vapour exit pipe 474, are a series of fins 478, each of which are made from heat conductive material such as metal. The vapour exit pipe 474, together with the fins 478, act ss* a condenser, cooling any gases, liquids and/or and vapours which pass through the vapor exit pipe 474 from the cyclonic separator 468 to a vapour pump 476.

An exit pipe 480 connects to:he vapour pump 476 and extends downwardly towards a collection tank 4E2.

The operation of tie separation device will now be described with reference to Figures 4A to 4D. During the ozeration of the separation device, the piston compressor 484 produces a series of pulses o'compressed hot air containing vapourised fluid 1304 and entrained solids released from the fluti 1304 when it was vapourised. These are fed into the separator 490 where the solids are separated from the hot air and vapourised fluid 1304. The solids are then discharged from the separator 490. The vaporized fluid is then condensed, thscharged from the separator 490 and t nen collected.

Figures 4A to 4D show the operating cycle of the separation device, Figures 4A to 4D showing the pistzin compressor 464 in four different operating positions during the cycle.

In order for the pSton compressor 484 to operate to produce a series of pulses of compressed hot air, the crank shaft 412 of the pulse compressor must be rotationally driven (Arrow M) by an erternal rotary force.

The crank shaft 2.42 is rotationally driven in the direction of Arrow M in order drive the piston compressor 484 through its cycle. The crank shaft 412 is rotated using the external force. Such a force can be generated by a separate fan or propellor (not shown) due to the movement of air zr water through the fan or propellor such as wind acting on a wind turbine or sea water passing through a water turbine due to the movement of the water caused by the tide. Alternar:vely, the force could be generated by an electric motor (not shown), a pneumatic motor:not shown), a kydracilic motor (not shown), a petrol or diesel engine (not shown) or any knzwri device which is capable of generating a rotational movement.

Figure 4A shows the start of the cycle. At the start, the crank shaft 412 has movec the piston 406, using the connecting rod 414, to its highest position within the cylinder 404. The connecting rod 414 is attached to the slide rod 438 of the first valve 416. Because the crank shaft 412 has moved the piston 406 to its highest position, the slide rod 438 has been slid upwardly inside the slide bearing 440, moving the two valve disks 430, 432 upwardly inside of the valve chamber 418 until the two valve disks 430, 432 are ir their highest positiort (as shown in Figures 4A) with the seal 444 located remotely from lower wall 420 of the valve chamber 418 and the up 3er disk 430 located against the upper wall of the valve chamber 418. As such, the entrance to tie lower elongate tubular passage 42415 open, thus allowing air to pass between the valve &amber 418 and the compression chamber 428 of the cylinder 404. The compression chambe-428 is at its greatest volume V1 when the piston 406 is in its highest position. As the valve disks 430, 432 are in their highest position, air is able pas from above the piston 406 from the surrounding atmosphere, through the second upper elongate passage 436, through the valve chamber 418 and then through the lower elongate tubular passage 424 and into the compression chamber 428 of the cylinder 404. As such, the air pressure inside the compression chamber 428 is the same as that of the atmosphere surrounding the piston compression pulse spray dryer.

When the piston 406 is in its highest position, the volume of the compression chamber 428 is at its maximum V1 and the inlet 1300 faces Into the compression chamber 423 below he piston 406 as shown in Figure 4A. Whilst the piston 406 is in its h:ghest position, as shOwn in Figure 4A, the valve 130E is opened by the crank shaft 412 via the mechanical link 130 The fluid 1304 containing the disso ved solids flows from the tank (not shown) via the pipe 1302 to the inlet 1300 and then into the compression chamber 428. The fluid 1304 with dissolved solids mixes with the air in the compression chamber 428. As such, the inlet acts as a Mixer. The valve 1308 is kept open for a predetermine amount of time by the crank shaft 4121as it passes through a predetermined range of angular positions whilst the piston 406 is approaches, passes through anc leaves its highest position, to ensure that a predetermine amount of fluid 1304 with dissolved solids enters the compression chamber 428. Once the crank shaft 412 exits the predetermined range of angular positiors, it closes the valve 1304.

When the piston 406 is in its hignest position, as shown in Figure 4A, both of the entrances 450,452 of the U shaped passaFe 448 of the second valve 486, are located above both seals 408. As such, the space between the seals 408 is sealed by the side of the piston 406 and therefore the entrance to outlet 446 is sealed by the second valve 486 and as such, air is unable to pass through the outlet 446.

Figure 4B shows the second sta e of the cycle. During the second stage, the crank shaft 412 is moving the piston 406 downwardly (Arrow N), using the connecting rod 414 which is attached to the first valve 416. 1 As the crank shaft 412 rotates (Arrow M) to move the piston 405 downwardly inside of the cylinder 404, the crank shaft 412 causes the slide rod 438 to slide downwardly inside the slide bearing 440, moving the two valve disks 430, 432 downwardly inside of the valve chamber 418 until the two valve disks 430, 432 are in their lowest position (as shown in Figure 4B) with the seal 444 sandwiched between the lower surface of the lower disk 432 and the flat side wall 420-of the valve chamber 418. As the crank shaft 412 continues to? rotate (Arrow 114) to move the piston 406 downwardly inside of the cylinder 404, the crank shaft 412 continues to pi.sh the slide rod 438 downwardly, the slide rod 438 pushing the valve disks 430, 432 downwardly, which in turn push the piston 406 downwardly insidei of the cylinder 404 by their engagement of the lower wall 420 of the valve chamber 418. As the valve 430, 432 pushes the piston 406 downwardly (Arrow N), the entrance to the lower elongate tubular passage 424 is sealed, thus preventing air from passing between the valve chamber 418 and the compression chamber 428 of the cylinder 404 as the piston 406 moves downwardly within the cylinder 404. As such, air is unable to pass from above the piston 406 from the surrounding atrtiosphe-e into the compression chamber 428 of the cylinder 404.

When the aiston 406 is being moved downwardly, the volume of the compression Clamber 428 is reduced. The inlet 1300 faces into the side of the piston 406 inside of compression chamber 428 as shown in Figure 48. When the piston 406 is in this position, the valve 1308 is kept closed by the crank shaft 412 via the mechanical link 1306. As such, additional fluid 1304 containing the dissolved solids is prevented from entering the compression chamoer 428. Furthermore, the closed valve 1308 prevents any air, fluid or solids inside the compression chamber 428 exiting tie compression chamber 428, as the pressure increases, through the inlet 1300.

When the p ston is be ng moved downwardly (Arrow h) by the crank shaft 412 as shown in Figure 48, both of the entrances 450, 452 of the U shaped passage 448 of the second valve 486, remain located, above both seals 408. As such, the space between the seals 408 is sealed by the side of the piston 406 and therefore the entrance to outlet 446 is sealed by the second valve 486 ard as such, air is unable to pass through the outlet 446.

As such, the compressor chamber 428 in the cylinder 404 is completely sealed, with air being unable exit through either the first or second valves 416, 486. Therefore, as the piston 406 moves cownwardiy, the air located in the compression chamber 428 becomes compressed, with both the pressure and temperature of the air within the compression chamber 428 increasing. As the air pressure in the compression chamber increases, ar upward force is exerted onto the piston 406, which in turn assists in maintaining the engagement of the discs 430, 432 and seal 444 with the lower wall 420 of the valve chamber 418. Furthermore, as tie temperature of the air the compression chamber 428 increases, the temperature of the fluid 1304 with the dissolved solids also increases. This results in the fluid 1304 evaporating, the solids dissolved within the fluid 1304 being released from the fluid 1304 and teing able to move around the compression chamber 428 inside the heated air and vapourised fluid.

Figure 4C shows the th rd stage of the cycle. During the third stage, the crank shaft 412 nas moved the piston 406 to its lowest position within the cylinder 404. In this position, the compression chamber 428 has its smallest volume V2. As such, the air located in the compression chamber 428 is at its maximum compression with both the pressure and temperature of the air, vapourised fluid 1304 and solids in the compression chamber 428 being at their maximum. As the air pressure in the compression chamber is much higher than that exerted on the top of the piston 406 (which is that of the surrounding atmosphere), an upward forze is exerteo onto the piston 406. As such, the two valve disks 430, 432 are maintained in their lowest position in the valve chamber 418 (as shown in Figure 4C) with the seal 444 is sandwiched between the lower surface of the lower disk 432 and the flat side wall 420 of the valve chamber 418. Therefore, the entrance to the lower elongate tubular passage 424 remains sealed, thus preventing air from passing between the valve chamber 418 and the compressicn chamber 428 of the cylinder 404_ When the piston 406 is at its lowest position, the volume of the compression chamber 428 is at its minimum. The inlet 1300 faces into the side of the piston 406 inside of compression chamber 428 as shown n Figure 4C. When the piston 406 is in this position, the valve 1308 is kept closed by the crank shaft 412 via the mechanical link 1306. As such, additional fluid 1304 with dissolved solids is prevented from entering the compression chamber 428. Furthermore, the closed valve 1308 prevents any air, fluid or solids inside the compression chamber 428, exiting the compressionchamber 428 as the pressure increases, through the inlet 1300.

As the piston 406 moves downwardly (Arrow N), towards the position shown in Figure 4C, for a brief period of time, the upper entrance 452 of the U shaped passage 448 is located above the upper of tne two seals 408 whilst the lower entrance 450 of the U shaped passage 448 faces into the space formed between the two seals 408 towards the outlet 446. During the brief period when the piston 406 is in this position, air located above the piston 406:sable to pass between the side of the piston 406 near the top of the piston 406 and tie cylinder wall, enter the upper entrance 452 of the U shaped passage 448, pass through the U shaped passage 448 and exit the lower entrance 450 of the U shaped passage 448, er ter the space between the two seals 408 and then enter outlet 446.

When the piston has moved to its lowest position as shown in Figure 4C, the Lower ertrance 450 of the LI shaped passage 448 is located below the lower of the two seals 408 whilst the upper entrance 452 of the U shaped passage 448 faces into the space formed between the two seals 408 towards the outlet 446. When the piston 406 is in this position, the air, vaoourised fluid 1304 and solids in the compression chamber 428, which is at its maximum compression and highest temperature due to the compression chamber having its smallest voiume V2, is able to pass between the lower side of the piston 406, enter the lower entrance 450 of the U shaped passage 448, pass through the U shaped passage 448 and exit the entrance 452 of the U shaped passage 448. enter the space between the two seals 408 and then enter the outlet 44-6. As the air, vapourised fluid and solids in the compression chamber 428 is at the maximum pressure and temperature, a pulse of compressed and heated air, with the vapourised fluid and solids, enters the outlet 446. The pulse of compressed and heated air, with the vapourised fluid and solids, then passes th-ough the second pipe 466 and into the housing 458 which forms the cyclonic separator 468. The heated air, vapourised fluid 1304 and solids then enter the cyclonic separation chamber 470 where the solids are separated from the heated air and vapourised fluid 1304.

As the pulse of compressed and heated air, with the vapourised fluid and solics, passes between the side of the piston 406, enters the lower entrance 450 of the U shaped passage 448, passes through the U shaped passage 448 and exits the upper entrance 452 of the U shaped passage 448, enters the space between the two seals 408, enters the outlet 446, through the second pipe 466 and into the mixing chamber 460 of the housing 458, the pressure and temperature of the pulse of air wLII drop as the air expands and cools. As-such, the combined volumes of the compression chamber at its smallest volume V2 (Figure 4C) and the volume V3 of the interconnection passageway between the compression chamber 428 and the mixing chamber 460 (comprising the volume of the space down the lower side of the piston 406, the volume of the space in the U shaped passage 448, the volume of space between the two seals 408 and the volume within the second pipe 466) needs to be less than the volume of the compression chamber 428 at its maximum volume V1, and ideally significantly less, in order tc ensure that the puise of air entering the mixing chamber 460 is at a reasonable pressure and temperature in order for it to vaporise any atomised fluid entering the mixing chamber 460. Ideally, the volume of V2 + V3 is less than 95% of Vi. and preferably, the volume of V2 + V3 is less than 93% of V1, and preferably, the volume of V2 + V3 is less than 90% of V1, and preferably, the volume of V2 + V3 is less than 80% of V1, and preferably, the volume of V2 + V3 is less than 75% of V1, and more preferably, the volume of V2 + V3 is less than 50% of V1, and preferably, the volume of V2 + V3 is less thzn 40% of V1, and more preferably, the volume of V2 + V3 is less than 30% of V1, and preferably the volume of V2 + V3 is less than 10% of Vi.

Ideally, the combined volumes of the compression chamber 428 at its smallest volume V2 (Figure 4C), the volume V3 of the interconnection passageway between the compression chamber 428 and the mixing chamber 460 (comprising the volume of the space down the lower side of the piston 406, the volume of the space in the U shaped passage 448, the volume of space between the two seals 408 and the volume within the second 3ipe 466) and the volume V4 of the mixing chamber 460 needs to be less than the volume of the compression chamber 428 at its maximum volume V1, and ideally significantly less. ideally, the volume of V2 + V3 + V4 is less than 95% of VI, and preferably, the volume of 'J2 + ka + V4 is less than 90% of VI, and more preferably, the volume of V2 + V3 + V4 is less than 50% of V1, and more preferablyrthe volume of V2 + V3 + V4 is less than 30% of VI the volume of V2 + V3 + V4 is less than 10% of VI.

Figure 4D shows the fourth s:age of the cycle. During the fourth stage, the crank shaft 412 is moving the piston 406 upwarcly, using the connecting rod 414 which is attached to the first valve 416.

When the piston 406 is being moved upwardly. the volume of the compression chamber 428 is increasing. The inlet 1300 faces into the side of the piston 406 inside of compression chamber 428 as shown in Figire 4D. When the piston 406 is in this position, the valve 1308 is kept closed by the crank shaft L12 via the mechanical link 1306. As sun, the fluid 1304 containing the dissolved solics is prevented from entering the compression chamber 428.

When the piston 404 starts to move upwardly IArrow 0) from its lowest position as shown in Figure 4C, for a brief period at time, the upper entrance 452 of the U shaped passage 448 is located above the upper of the two seals 408 whilst the lower entrance 450 of the LI shaped passage 448 faces into the space formed between the two seals 408 towards the out-et 446. During this brief pen)d when the piston 406 is in this position, air loca:ed above tre piston 406 is able to pass between tie side of the piston 406 near the top of tie piston 406 and the cylinder wall, enter the upper Entrance 452 of the U shaped passage 448, pass through the U shaped passage 448. exit the lower entrance 450 of the U shaped passage 448, enter the space between the two seals 4C8 and then enter the outlet 446.

Subsequently, as the piston is being moved upwardly (Arrow 0) by the:rank shaft 412 as shown in Figure 4D, both of the entrances 450, 452 of the U shaped passage 448 of the second valve 486, remain located above both seals 408. As such, the space between the seals 408 is sealed by the side cf the piston 406 and therefore the entrance to outlet 446 is sealed by the second valve 486 and as such, air is unable to pass through the outlet 446.

As the crank shaft 412 rotates to move the piston 406 upwardly inside of the cylinder L04, the crank shaft 412 causes the slide rod 438 to slide upwardly inside the slide bearing 440, moving the two valve disks 4311 432 upwardly inside of the valve chamber 418 until the two valve disks 430, 432 are in their highest position (as shown in Figure 4Di with the seal 444 located remotely from lower wall of the valve chamber 418 and the upper disk 430 located against the upper wail 422 of the valve chamber 418. As the crank shaft 412 continues to rotate (Arrow M) to move the piston 406 upwardly inside of the cylinder 404, the crank shaft 412, continues to puil the slide rod 438 upwardly, the slide rod 438 pulling the valve disks 430,432 upwardly, which in turn pull the piston 406 upwardly inside of the cylinder 4)4 by their engagement of the upper wall 422 of the valve chamber 418. As the valve 430, 432 pulls the piston 406 upwardly, the entrance to the lower elongate tubular passage 424 is open, thus allowing zit-to pass between the valve chamber 418 and the compression chamber 428 of the cylinder 434 as the piston 406 moves upwardly within the cylinder 404. As such, as the pistor 406 rises, air is able pass from above the piston 406 from the surrounding atmosphere, throu h the second ipper elongate passage 436, through the va:ve chamber 418 and then througi the lower elongate tubular passage 424 and into the compression chamber 428 of the cylinder 404. Therefore, air is able to enter the compression chamber 428 as the p stop 406 moves upwardly, replenishing the air previously em fled as a pulse through the outlet 446. The air pressure inside the compression chamber 428 remains the same as that of the surrounding atmosphere as it is replenished as tie piston 406 moves upwardly. This allows the compression chamber 428 to be fully replenished with air wien ft reaches its highest position as shown in Figure 4k Once the piston 406 has returned to the position shown in Figure 4A, the cycle of the piston compressor 484 is repeated as the crank shaft 412 continues to rotate (Arrow M).

Each 360 degree rotation of the crank shaft 412 results in a single cycle of the piston compressor 484. Each cycle results in a single pulse of compressed heated air, with vapourised fluid 1304 and solids, entering the cyclonic separation chamber 470 of -the housing 458 of the separator.

The operation of the separa7or 490 in conjunction with the piston compressor 484 vial now be described.

The pulse of heated air, vapourised fluid 1304 and the solids enter the cyclonic sepa-ation chamber 470 of the housing 458 of the separator. The solids are separated from the heated air and vapourised fluid 1304, the solids exiting the cyclonic separation chamber 47D via the solids exit pipe 472.

The vapourised fluid 456 then passes through the vapour exit pipe 474 to the vapoL r pump 476. As the vapourised fluid 456 passes through the vapour exit pipe 474, the heat of the vapourised fluid 456 transfers to the fins 478 via the pipe 474 where it is dissipated into the surrounding environment. As such, the vapourised fluid 456 is condensed as it passe through the fourth vapour exit pipe 474 and turns back into a liquid by the time it arthes at the vapour pump 476.

The liquidised fluid 456 then passes through the exit pipe 480 towards the collection tank 482 where the fluid is collected.

It will be appreciated that, during the operation of the separator, the fluid with the dissolved solids can be introduced into the compression chamber 428 with the air when the air enters the compression chamber 428 via the first valve 416. The fluid with the dissolved so ids can be mixed with the air in a mixer prior to the air, together with the fluid with dissolved solids, entering the compression chamber via the first valve 416. By introducing the fluid w th the dissolved solids with the air, the need for the inlet 1300 and associated valve 1308 is no longer required and as such, can be removed to simplify the construction of the separation device.

It will be appreciated that during the operation of the separator, the fluid with dissolved solids can be introduced into the compression chamber 428 when the compression chamber 428 is at its smallest volume (in a similar manner to diesel being injected into the combustion chamber of a diesel engine) prior to second valve being opened to allow the exit of t7e heated compressed air. Whei the volume of the compression chamber is at its smallest, the air within it is at the maximum temperature and pressure. The fluid with dissolved solids would need to be injected int) the air due to the increased temperature and pressure. The injector would act as a mixer, mixing the fluid with dissolved solids and compressed a r. The fluid would them immediately vaporize, releasing the dissolved solids from the fluid. The heated air, vapourised fluid, and solids can then be released from the compression chamber by opening the second valve, allowing heated air, vapourised fluid, and solids to the exit the compression chamber 428 and enter the separator.

The operation of the separation device will now be described in relation to desalinating a saline solution, such as sea water, where the saline solution (e.g. water with sodium chloride dissolved within it) is fed into the separation device where the salts within the saline sedition are separated from the solution. Where the saline solution is sea water, by separating the salt from the water in which it is dissolved, drinkable water can be produced.

In order to desalinate sea water, the separation device as descrioed above with reference to Figures 4A to 40 is used to desalinate sea water by placing sea water into the tank of the separation device. Ideally, the sea water has been previously filtered to remove any unwanted debris. The sea water is then fed through the pipe 1302 and then through the inlet 1300 into the compression chamber 428 when the piston 406 is ats highest position as shown Figure 4A. The sea water is then heated by the movement of the piston 406 from its highest position (as shown in Figure 4A) to its lowest position (as shown in Figure 4C) which compresses the air in the compression chamber 428 and which results in its increased pressure and temperature. The heated and compressed air heats the sea water which results in the water vaporising, separating it from the salt dissolved within the sea water.

The heated air, vapourised water and salt enter the cyclonic separation chamber 470 of the cyclonic separator 468. The vapourised water is then separated from the salt, the salt exiting the separation chamber 470 via the solids exit pipe 472.

The vapourised water 456 then passes through the vapour exit pipe 474 to the vapour purnp 476. As the vapourised water passes through the vapour exit pipe 474, it is condensed inta liquid water.

The liquidised water 456 then passes through the exit pipe 480 towards the collection tank 482 where the water is collected.

A second embodiment of the invention will now be described with reference to Figure 5.

Referring to Figure 5, the second embodiment of the separation device comprises four piston compressors 484A-484D, each of which are of the same design as the single piston compressor 484 described in the first embodiment with reference to Figures 4A to 4D, and a single separator 490 which is the same design as the separator 490 described in the first embodiment with reference to Figures 4A to 4D. Eaca piston compressor 484A-4840 produces a series of pulses of compressed hot air, vapourised fluid and solids, the series pulses from each of the piston compressor 484A-484D being fed into the single separator 490. Where the same features which are present in the first embodiment of the separation device are present in the second embodiment, the same reference numbers have been used. As there are four piston compressors 484A-4840, the reference numbers used in relation to a particular piston compressor 484A-484D will have a letter added, to identify which piston compressor 484A-484D it is, the first piston compressor 484A having an "A", the second piston compressor 484B having a "B", the third piston compressor 484C having a "C", and the fourth piston compressor 484D having a Referring to Figure 5, the se aeration device comprises a rotatable crank shaft 412 mounted inside of a crank housing (not shown) which is capable of rotating about an axis. Each end of the crank shaft 412 is supported by a bearing 500. Rigidly attached to one end of the crank shaft 412 is a first gear wheel 502. The first gear wheel 502 meshes with a second gear wheel 504 which is rigidly mounted on one end of a drive shaft 506. The drive shaft 506 is rotationally supported by bearings 512. A propeller 508 is mounted on the other end of the drive shaft 506. The propeller 508 is located within an air flow, such as being located on a tower to engage with a breeze or wind. The air flow through the propeller 508 causes the propellor 508 to rotate which in turn causes the first and second gears 502, 504 to rotate, which in turn causes the cra ak shaft 412 to rotate. The ratio of the sizes of the gears 502, 504 is chosen in order to optimise the speed of rotation of the crank shaft 412.

The crank shaft 412 comprises four offset connection sections 510. The four piston compressors 484A -4840 are attached to the crank shaft 412, one piston compressor 484A-484D being connected to each of the connection sections 510. The four piston compressors 484A -484D are mounted relative to crank shaft 412 such that the axis of the crank shaft 412 extends perpendicularly to the longitudinal axes of the cylinders of the four piston compressors 484A-4840, the longitudinal axes of all of the cylinders being parallel to each other. A connecting rod 5144-5140 is pivotally attached to each of the connection sections 510 of the crank shaft 412 as their upper end, the axes of pivot being parallel to but eccentrically off set from the axis of rotation of the crank shaft 412. Each of the lower ends of the connecting rods 514A-514D is pivotally attached to a first valve formed in the top of the pistons 406A-406D of each of the four piston compressors 484A-484D, the axes of pivot being parallel to the axis of rotation of the crank shaft 412. Rotation of the crank shaft 412 results in a linear reciprocation motion of the pistons 406A -406D inside the cylinders along the longitudinal axe! of the cylinders in well know manner. Each connection section 510 is located at 90 degrees in a tangential direction around the longitudinal axis of the crank shaft 412 relative to any adjacen-. connection section 510 such that, when the crank shaft 412 is rotationally driven, each piston compressor 484A-4840 is 90 degrees out of phase in its operating cycle:n reation to the adjacent piston compressor 484A-484D.

The operation of each of single piston compressors 484A -484D is the same as that of the single piston compressor 484 in the first embodiment described above with reference to Figures 4A to 4C. All of the piston compressors 484A-48413 are connected to a single housing 458 of the sepatator 490, each piston compressor 4S4A -484D being connected via a pipe 466A -4660. Each piston compressor 484A-48413 produces a series of pulses of compressed hot air, fluid vapour and solids, the series of pulses -From each of the piston compressors 484A -4840 be rg fed into the cyclonic separation chamber of the housing 458 of the single separator 490. As there are four piston compressors 484A -48413, each single rotation of the crank shaft 412 results in each of the piston compressors 484A-4840 injecting a pulse of compressed heate.d air, together with vapourised fluid and solids, into the cyclonic separation chamber, the four pulses of compressed heated air being injected into the cyclonic separation chamber every time the crank shaft 412 makes a single rotation. As each piston compressor 484 is 90 degrees out of phase in its operating cycle in relation to its adjacent pistcn compressor 484A-484D, the four pulses of compressed heated air, vapourised fluid and solids enters the cyclonic separation chamber in a sequential manner at a pre-set frequency with same time period being between adjacent pulses, the time period being dependent of the rate of rotation of the crank shaft 412.

The operatior of the separator 490 is the same as that as the separation device 490 in the first embodiment described in the first embodiment with reference to Figures 4A to 40.

The advantage of the design of the separation device in the second embodiment over that of the separation device in the first embodiment is that, every time the crank shaft 412 makes a 360 degree rotation, four pulses of compressed healed air, together with vapourised fluid and solids, enter the cyclone separation chamber in the second embodiment versus a single pulse of compressec heated air, with vapourised fluid and solids, entering the cyclonic separation chamber 460 in the first embodiment. This allows an increased rate of pulses of compressed heated air intc the chamber 460 versus the rate of rotation of the crank shaft 412.

A third embodiment of the invention will now be described with reference to Figure 6.

Referring to Figure 6, the third embodiment of the of the separation device comprises a single piston compressor 484, which is the same design as the piston compressor described in the first embodiment with reference to Figures 4t. to 40, connected to a separator 1400. The piston compressor 484 produces a series of pulses of compressed hot air, vapourised fluid and solics, which are led into the separator. Where the same features which are present in the first embodiment of the separation oevice are present in the third embodiment, the same reference numbers have been used.

The difference between the third embodiment of the separation device and the first embodiment of the separation device is the design of the separator 1400. In the design of the separation device of the first embodiment, the separator is a cyclonic separator, the solids being separated from the vapourised fluid using a cyclone. In the design of the separation device of the third embodiment, the separator uses a Titer 1408 to separate the solids from the heated air pulse and vapourised fluid.

The separator 1400 comprises a housing 1404 which forms a chamber 1406. A filter 1408 extends across the width of the chamber 1406 to separate the clamber 1406 into an upper chamber 1406A and a lower chamber 14068. The filter 1408 is a simple filter, in that, it constructed from a single material. However, the filter 1408 can be a complex filter which is constructed from a range of materials, for example, different materials can be used to form different layers in the filter. However, the filter 1408 has to be constructed such that the heated pulses of compressed air and vapourised fluid from the pis:on compressor can pass through the filter 1408, whilst the solids 1410 cannot. It will be appreciated that several filters arrange in series and/or parallel may be utilised.

In operation, the piston compressor 484 produces a series of pulses of compressed hot air, vapourised fluid 1304 and solids 1410, which are fed via a pipe 1412 into the upper chamber 1406A (indicated by krrow W). The series of pulses of compressed hot air and vapourised fluid pass through the filter 1408 and enter the lower chamber 14068 (indicated by Arrow Y). However, the solids 1410 are prevented from passing through the filter 1408. The series of pulses of compressed hot air and vapourised fluid pass then exit the lower chamber 140613 via the exit pipe 1416. The heated air and vapourised fluid can then be cooled in well-known manner to turn the vapourised fluid back into a liquid.

As the solids 1410 are prevented from passing through the filter 1408, the solids 1410 buildup on the top surface of the filter 1408. A door 1418 provides access to the upper chamber 1406k When sufficient solids 1410 have built up on the filter 1408. an operator can remove them from the filter 1408 by opening the door 1418 and vacuuming the solids off the filter 1408.

As such, the solids 1410 are separated from the fluid in which they were dissolved.

As the pulse of compressed and heated air, with the vapourised fluid and solids, passes between the side of the piston 406, enters the lower entrance 450 of the U shaped passage 448, passes through the U shaped passage 448 and exits the upper entrance 452 of the U shaped passage 448, enters the space between the two seals 40E, enters the outlet 446, through the pipe and into the upper and lower chambers of the rousing 1404, the pressure and temperature of the pulse of air and vapourised fluid will dro 3 as the air expands and cools. As such, the combined volumes of the compression chamber at its smallest volume V2 (Figure 4C) and the volume V3 of the interconnection passageway between the compression chamber 428 and the chamber 1406 of the separator (comprising the volume of the space down the lower sice of the piston 406, the volume of the space in the U shaped passage 448, the volume of space between the two seals 408 and the volume within the pipe) needs to be less than the volume if the compression chamber 428 at its maxi-n Jfil volume V1, and ideally significantly less, in order to ensure that the pulse of air entering:he chamber 1406 is at a reasonable pressure and temperature in order for it to maintain the fluid in a vaporised form in the chamber 1406. Ideally, the volume of V2 + V3 is less than 95% of V1, and preferably, the volume of V2 + VE. is less than 93% of V1, and preferably, the volume of V2 + V3 is less than 90% of V1, and preferably, the volume of V2 + V3 is less that SO% of V1, and preferably, the volume of V2 + V.T.. is less than 75% of V1, and more preferably, the volume of V2 + V3 is less than 50% of V1, and preferably, the volume of V2 + V3 is less than 40% of V1, and more preferably, the volume of V2 + V3 is less than 30% of V1, and prefer3bly the volume of V2 + V3 is less than 10% of Vi.

Ideally, the combined volumes of the compression chamber 428 at its smallest volume V2 (Figure 4C), the volume V3 of the interconnection passageway between the compression chamber 428 and the mixing chamber 460 (comprising the volume of the space down the lower side of the piston 406, th a volume of the space in the U shaped passage 448, the volume of space between the two seals 408 and the volume within the pipe) and the volume V4 of the chamber 1406 of the separator needs to be less than the volume of the compression chamber 428 at its maximum volume V1, and ideally significantly less. Ideally, the volume of V2 + V3 + V4 is less than 95% of V1, and preferably, the volume of V2 + V3 + V4 is less than 90% of V1, and more preferably, the volume of V2 + V3 + V4 is less than 50% of and more preferably, the volume of V2 + V3 + V4 is Its than 30% of V1 the volume of V2 + V3 + V4 is less than 10% of It will be appreciated that, during the operation of the separator, the fluid with the dissolved solids can be introduced into the compression chamber 428 with the air when the air enters the compression chamber via:he first valve 416. The fluid with the dissolved solids can be mixeo with the air prior to the air, together with the fluid with the dissolved solids, entering the compression chamber vie:he first valve 416. By introducing the fluid with Ite dissolved solids with the air, the need for the inlet 1300 and associated valve 1308 is no longer required and as such, can be removed to simply the construction of the separation device.

A fourth embodiment of the invention will now be described with reference tc Figures 7A and 73.

Referring to Figures 7A and 78, the fourth embodiment of the of the separatior device comp-ises a single piston compressor 484, which is the same design as the piston compressor described in the first embodirr ent with reference to Figures 4A to 40, connected to a separator 1400 as described in the third embodiment with reference to Figure S. The piston comp-essor 484 produces a ser es of pulses of compressed hot air, vapourised fluid and solids, which are fed into the separator 1400. Where the same features which ore present in the third embodiment of the separation device are present in the fourth embodiment, the same reference numbers have been used.

The cf fference between the fourth embodiment of the separation device and the third embodiment of the separation device is the addition of a filter 1500 inside of tie cylinder 404 between the cylinder wall and the side of the piston 406.

Figure 6A shows the piston 406 of the piston compressor at its highest position. Figure 7B shows the piston 406 of the piston compressor at its lowest position. As can be seen, the filter i500 remains at all times sandwiched between the cylinder wall and the side of the pistor 406.

The filter 1500 is a simple filter, in that, it constructed from a single material. However, the filter:500 can be a complex filter which is constructed from a range of materia:s, for example, different materials can be used to form different layers in the filter. However, the filter has to be constructed such that the heated pulses of compressed air and vapourised fluid f-om the piston compressor can pass through the filter 1500, whilst the sends 1410 cannot. It will be appreciated that several filters arranged in series and/or parallel may be utilised.

The operation of the piston compressor is the same as that described in the first embodiment with reference tc r.rigures 4A to 40. Therefore, when the air in the compression chamber 428, together with the fluid with dissolved solids are compressed by movement of the piston from its highest postion to its lowest position to heat the air and vaporise the fluid, the heated air and vaporised fluid are able to exit the compression chamber through the second valve by passing through the filter. However, the solids are prevented from exiting the compression chamber 428 due to the filter 1500 which bocks the scuds. As such, durinE the operation of the piston compressor, solids build up I the compression chamber 428. Once a large amount of solids has accumulated, it can be removed from thE compression chamber 428 by a door (not shown) in the cylinder 404 wall or by the removal of the piston 406 from the cylinc er 404.

When the heated air and vaporiied fluid exit the compression chamber through the second valve 486, it passes into the separator 1400 and then pass through the filter 1408 in the separator. It will be appreciated that the filter 1408 in the separator 1400 is redundant due to the filter 1500 in the cylinder 404.

A fifth embodiment of the invernion will now be descrioed with reference to Figures 8A and 8B.

Referring to Figure 8A, the fifth embodiment of separation device comprises a single piston compressor 484 connected to a E i ngl e separator which is the same design as the separator described in the third embodiment with reference to Figure 6. The piston compressor 484 produces a series of pulses of compressed hot air, with vaporised fluid and solids, which are fed into the separator 1400. Where the same features are present in the third embodiment of the separa: on device are present in the fifth embod ment, the same reference numbers have been used.

The difference between the fifth embodiment of separation device and the third embodiment of the separation device is the design of the piston compressor 484. In the design of the piston compressor of the third embodiment, the air flow in and out of the compression chamber 428 is con:rolled by two mechanical valves 416, 486. In the design of the piston compressor 484 of the fifth embodiment, the air flow in and out of the compression clamber 428 is controlled by two electronically controlled valves 600, 602.

Referring to F gure 8A, the piston compressor 484 creates pulses of compressed heated air, vapourised flr id and solids in a similar manner to that of the piston compressor in the third embodiment. The piston compressor 484 comprises a cylinder block 400 which is mounted below a crank shaft housing (not shown). The cylinder block 400 comprises an elongate cylinder 404 having a longitudinal axis and a uniform circular cross section, in a direction perpendicular 70 the axis, along the length of the cylinder 404. Slideably mounted within the cylinder 404 i a piston 406 of circular cross section of similar size to that of the cylinder 404. Mounted arm nii the internal wail of the cylinder 404 towards the top of the cylinder 404 is a seal 604 which forms a seal between the external sidewall of the piston 406 and the side wall of the cylinder 404 and which prevents any gases from passing the seal 604. The seal 604 slides along the external sidewall of the piston 406 when the piston 406 reciprocates within the cylinder 404. The upper section of the cylinder 404 opens into a chamber 410 formed inside of the rank shaft housing. The lower section of cylinder 404 forms a compression chamber 428, the compression chamber 428 being defined by the lower internal walls of the cylinder 404 and a lower surface of the piston 406.

A rotatable crank shaft (not shown) is mourned inside of the crank housing which is capable of rotating oboist an axis which extends perpendicularly to the longitudinal axis of the cylinder 404. A connecting rod 414 is pivotally attached to the crank shaft at an upper end, the axis of pivot being parallel to but eccentrically off set from the axis of rotation of the crank shaft. The lower end of the connecting rod 414 is pivotally attached to the top of the piston 406, the axis of pivot being parallel to the axis of rotation of the crank shaft. Rotation of the crank theft results in a linear reciprocation motion of the piston 406 inside the cylinder 404 along the longitudinal axis of the cylinder 404 in well know manner. A counterweight (not shown) is eccentrically mounted on the crank shaft 70 counteract any vibrations generated by t-e etcentric connection of the upper end of the connecting rod 414 as the crank shaft rotates.

The lower section of the cylinder 404 is terminated by a lower wall formed by:he uottom of the cylinder block 400. A compression chamber 428 is formec inside of the lower section of the cylinder which is bounded by the lower wall of the cylinder block 400 at tha bottom, by the side walls of the cylinder at the sides, and the lower surface of the piston 406 at the top.

An inlet 1300 is formed through the side wall of the cylinder 404. The inlet 1300 is located approximately half-way along the length of cylinder 404 such that, when the volume of the compression chamber 428 is at its maximum, the inlet 1300 faces into the compression chamber 428 below the piston 406 as shown in Figure 4A. A tank (not shown). 4r which is inserted a fluid 1304 in which is dissclved solids, is connected via a pipe 1302 to the inlet 1300. A nozzle (not shown) can be optionally attached to the and of the pipe 1302 A valve 1308 is mounted in the pipe 1302 to ensure that the fluid 1304 with the dissolved solids can only flow one way into the compress:on chamber 428 and that pressurised air from the compression chamber 428 cannot ex t the compression cham Der 428 via the ir let 1300. The valve 1308 is opened and closed so that the fluid 1304 with dissolved solids can only flow through the valve into the compression chamber 428 at set times. The valve 1308 is mechanical linked (indicated by dashed lines 1306), for example by a cam mechanism or an eccentric drive, to the crank shaft 412 in order to enable the mechanical motion of the crank shaft 412 to utilised in opening and closing the va ve 1308. When the crank shaft 412 is at pre-set angular positions, it opens the valve 1308 using the mechanical link 1306. When the angular shaft 412 is at the other angular positions, it doses the valve 1308 using the mechanical fink 1306. As such, it can be ensured flat the fluid1304 with the dissolved solids only enters the compression chamber 428 when the piston 406 is at predetermined positions.

An outlet 446 is formed through a lower section of the wall of the cylinder 404_ A first pipe 608 connects between the outlet 446 and the first electronically controlled valve 602. A second pipe connects between the first electronically controlled valve 602 and the separator. The separator is the same design as the separator described Fr the third embodiment with reference to Figure 6.

An inlet 612 is formed through a lower section of the wall of the cylinder 404. A third pipe 614 connects between the inlet 612 and the second electronically controlled valve 600. A fourth pipe 616 connects between the second electronically controlled valve 600 and the surrounding environment.

A controller (not shown) is connected:to a sensor I not shown) mounted adjacent the crank shaft. The sensor provides information to the controller as to the angular posit:on of the crank shaft. Based on this information the controlier can dete-mine axial positlon of the piston 406 within the cylinder 404 and therefore the size of the compression chamber 428.

The crank shaft is rotatably driven by an external rotary force in order to reciprocatingly drive the piston 406 within the cylinder 434.

Figure B shows a series of graphs relating to the operation of tie piston compressor 484 shown in Figure 6A. Graph 1 shows gra volume Vo of the compression chamber 428 versus time t, Vo MAX indicating the maximum volume of the compression chamber 428, Vo MIN indicating the minimum volume of the compression chamber 428. Graph 2 shows the status of second electronically controlled valve 600 versus time t, OPEN indicating the second electronically controlled valve 600 is open allowing air to pass chrough the second electronically controlled valve 600, CLOSED indicating the second electronically controlled valve 600 is closed preventing air from, passing through the second electronically controlled valve 600. Graph 3 shows the status co' first electronically controlled valve 602 versus time t, OPEN indicating the first electronically controlled valve 602 is open allowing air to pass through the first electronically controlled valve 602, CLOSED indicating the first Electronically controlled valve 602 is closed preventing air from passing through the first electronically controlled valve 602.

The operating cycle of the fiftn embodiment of the separation device wi now be cesuibed.

When the piston 406 is being axially driven upwardly so that the volume of the compression chamber 428 is increasing, the second electronically controlled valve 600 is opened by the controller to allow air to pass from the surrounding environment through the fourth pipe 616, through the second electronically controted valve 600, through the third pipe 614 and then enter the compression chamber 428 in order to replenish the air wthin the compression chamber 428 as it expands. As the compressior chamber 428 expands. the temperature and pressure of:he air within the compression chamber 428 remains the same as that of the air in the surrounding environment from which the air is being drawn. Whilst the piston 406 is being axially driven upwardly so that the volume of the compression chamber 428 is increasing, the first electronically controlled valve 602 is kept closed by the controller to prevent air from p2ssing through it.

When the piston 406 is at its highest position so that the volume of the compression chamber 428 is at its maximum Vo MAX, the second electronically controlled valve4600 is closed by the controller to prevent air from passing through it. The first electronically controlled valve 602 is maintained closed by the controller to prevent air from passing through it whilst the piston 406 is in its highest position.

When the piston 406 is in its highest position, the volume of the compression chamber 428 is at its maximum VoMax and the inlet 1300 face; into the compression chamber 4213 below the piston 406. Whilst the pis:on 406 is in its highest position, the valve 1308 is opened by the crank shaft (not shown) via the mechanical link 1306. The fluid 1304 zontainingtne dissolved solids flows from the tank (not shown) via the pipe 1302 to the inlet 130C and then into the compression chamber 428. The valve 1308 is kept open for a predetermine amount of time by the crank shaft as it passes through a predetermined range of angular positions whilst the piston 406 is approaches, passes through and leaves its highest position, to ensure that a predetermine amount cf fluid 1304 with dissolved solids enters the compres;ion chamber 428. Once the crank shaft exists the predetermined range of angular positions, it closes the valve 1304.

When the piston 406 is being axially driven downwardly so that the volume of the compression chamber 428 is decreasing, the second electronically controlled valve 600 is kept closed by the controller to prevent air from passing through it. Whilst the piston 406 is being axially driven downwardly so that the volume of the compression chamber 428 is decreasing, the first electronically controlled valve 602 is still kept closed by the cortroller to also prevent air form passing through it. As such, the air and fluid with solids in the compression chamber 428 is compressed increasing both their pressure and tempe-ature as they are compressed.

When the piston 406 is at its lowest position so that the volume of the compression chamber 428 is at its minimum Vo MIN and the pressure and temperature of the at vapourise.d fluid and solids inside of the compression chamber 428 are at their maximum, the first electronically controlled valve 502 is opened the controller to allow a compressed heated pulse of air to pass through the first pipe 608, through the first electronically controlled valve 602, through the second pipe £66 and then enter the separator 1400 so that the solos can removed from the vapourised Fluid in the same manner as described above in the third embodiment with reference to Figure 6. The second electronically contorted valve 600 is maintained closed by the controller whilst the f rst electronically controlled valve 602 is open. The inlet 1300 is maintaihed closed by the valve 1308 which is kept closed.

The first electronically controlled valved is then closed and the cycle is then repeated.

It will be appreciated that the valve 1308 for the inlet 1300 can also be an electronic valve controlled by the controller, thLs avoiding the need for the mechanical link between valve 1304 and the crank shaft.

It will be also appreciated that an additional filter (indicated by dashed lines 1600) can mounted inside of the compression chamber 428, preventing the solids from exiting the compression chamber 28 and only allowing the heat compressed air and vapourised fluid to exist the chamber and enter separator.

A sixth embodiment of the invention will now be described with reference to Figures 9A and 96.

Referring to Figure 9A, the sixth embodiment of the of the separation device comprises a single piston compressor 484 connected to a single separator (not shown) which is the same design as the separator described in the third embodiment with reference to Figure 6. The piston compressor 484 produces a series of pulses of compressed hot air, vapourised fluid and solids wnich are fed into the single separator. Where the same features which are present in the third embodiment of the separation device are present in the sixth embodiment, the same reference numbers have been used.

The difference between the sixth embodiment of the separation device and the third embodiment of the separation device is the design of the piston compressor 484. In the design of the piston compressor of the third embodiment the air flow in and out of the compression chamber 428 is controlled by two mechanical valves 416, 486. In the design of the piston compressor 484 of the sixth embodiment, the air low in and out of the compression chamber 428 is controlled by a three yday electronically controlled valve 700.

Referring to Figure 9A, the piston compressor 484 creates pulses of compressed heated air. vapourised fluid and solids in a similar manner to that of the piston compressor in the third embodiment. The piston compressor 484 comprises a cylinder block 400 which 7s mounted below a crank shaft housing (not shown). The cylinder block 400 comprises an elongate cylinder 404 having a longitudinal axis and a uniforrr circular cross section, in a direction perpendicular to the axis, along the length of the cyl nder 404. Slideably mounted within th: cylinder 404 is a piston 406 of circular cross section of similar size to that of the cylinder 404. Mounted around the internal wall of the cylinder 434 towards the top of the cylinder 404 is a seal 704 which forms a seal between the external;idewall of the piston 406 and tie side wall of the cylinder 404 and which prevents any air from passing the seal 604. The seal 704 slides along the external sidewall of the piston 406 when the piston 406 reciprocates within the cylinder 404. The upper section of the cylinder &CM opens into a chamber 410 formed inside of the crank shaft housing. The lower section of cylinder 404 forms a compression chamber 428, the compression chamber 428 being dafined by the lower internal walls of the cylinder 404 and a lower surface of the piston 406.

A rotatable crank shaft (not shown) is mounted inside of the crank housing which is capable of rotating about an axis which extends perpendicularly to the longitudinal axis of the cylinder 404. P. connecting rod 414 is pivotally attached to the:rank shaft at an upper end, the axis of pivot being parallel to but eccentrically off set from the axis of rotation of the crank shaft. The lower end of the connecting rod 414 is pivotally attached to the top of the piston 406, the axis of pivot being parallel to the axis of rotation of the crank shaft. Rotation of the crank shaft results in a linear reciprocation motion of the piston 406 inside the cylinder 404 along the longitudinal axis of the cylinder 404 in well know manner. A counterweight (not shown) is nccentrically mounted on the crank shaft to counteract any vibrations generated by the ecentric connection of the upper end of the connecting rod 414 as the crar k shaft rotates.

The 'tower section of the cylinder 404 is terminated by a lower wall formed by the bottom of the finder block 400. A:compression chamber 428 is formed inside of the lower section of the z...vlinder which is bounded by the lower wall of the cylinder block 400 at the bottom, by the side walls of the cylinder at the sides, and the lower surface of the piston 406 at the top.

An inlet 1300 is formed through the side wall of the cylinder 404. The inlet 1300 is located approximately half-way a ong the length of cylinder 404 such that, when the volume of the compression chamber 423 is at its maximum, the inlet 1300 faces into the compression chamber 428 below the piston 406. A tank (not shown), in which is inserted a fluid 1304 in which is dissolved sclids, s connected via a pipe 1302 to the inlet 1300. A nozzle (no: shown) can oe optionally attached to the end of the pipe 1302. A valve (not shown) is mounted in the pile 1302 to ensure toot the fluid with the dissolved solids can only flow one way into the ccmpression chamber 428 and that pressurised air from the compression chamber 428 cannot exit the compression chamber 428 via the inlet 1300. The valve is opened and closed so that the fluid 1304 with dissolved solids can only flow through the valve into the compression chamber 423 at set times. The valve is mechanical linked, for example by a cam menanism or an eccentric drive, to the crank shaft in order to enable the mechanical motion of the crank shaft to utilised in opening and closing the valve 1308. When the crank shaft 412 is at p-e set angular Positions, it opens the valve using the mechanical link. When the angular shaft is at the other angular positions, it closes the valve using the mechanical link. As such, it can be ensured that the fluid 1304 with the dissolved solids only enters the compression chamber 428 when the pi ston 406 is at predetermined positions.

An outlet 446 is forn-ed through a lower section of the wall of the cylinder 404. A first pipe 708 ccnnects between the outlet 446 and the three way electronically controlled valve 700. A second pipe 466 cornetts between the three way electronically controlled valve 700 and the separator 1400. The separator (riot shown) is the same design as the separator described in the third embodirr.Ent with reference to Figure 6. A third pipe 710 connects between the three way electronically controlled vaive 700 and the surrounding environment.

A controller (not showm) is connected to a sensor (not shown) mounted adjacent the crank shaft. The sensor provdes information to the controller as to the angular position of toe crank shaft. Based on this information the cootroller can determine axial position of the piston 406 within the cylinder 404 arid therefore the size of the compression chamber 428.

The crank shaft is rotatabl y driven by an external rotary force in order to reciprocatingly drive the piston 406 within the cylinder 404-.

Figure 98 shows a series of graphs relating to the operation of the piston compressor 484 shown in Figure 9A. Graph 1 shows the volume Vo of the compression chamber 428 versus time t, Vo MAX indicating the maximum volume of the compression chamber 428, Vc MIN indicating the minimum volume of the compression chamber 428. Graph 2 shows the status of the three way electronically controlled valve 700 versus time t in relation to the connectivity of the first pipe 708 and the third pipe 710, OPEN indicating the connect on of the three way electrcnicaly controlled valve 700 between the first pipe 708 and the third pipe 710 is open allowing air to pass through the three way electronically controlled valve 700 between these two pipes, CLOSED indicating the connection of the three way electronically controlied valve 700 between the first pipe 708 and the third pipe 710 is closed preventing air from passing through the three way electronically controlled valve 700 between these two p pes. Graph 3 shows the status of the three way electronically controlled valve 700 versus time t in relation to the connectivity of the first pipe 708 and the second pipe 466, OPEN incicating the connect on of the three way electronically cont-olled valve 700 between the first pipe 708 and the second pipe 466 is open allowing air to pass through the t nree way electronically controlled valve 700 between these two pipes, CLOSED indicating the connecion of the three way electronically controlled valve 700 between the first pipe 708 and the second pipe 466 is closed preventing air from passing through the three way electronically controlled valve 700 between these two pipes.

The operating cycle a' the sixth embodiment of the separation device will now be described.

When the piston 406 is being axially driven upwardly so that the volume of the compression chamber 4281s increasing, the three way electronically controlled valve 700 is opened by the controller to allow air to pass from the surrounding environment through the third pipe 710, through the tiree way electronically controlled valve 700, through the first pipe 708 and then enter the compression chamber 428 in order to replenish the air within the compression chamber 428 as it expands. As the compression chamber expands, the temperature and pressure ot. the air within the compression chamber 428 remains the same as that of the air in the surrounding environment from which the air is being drawn. Whilst the piston 406 is being axially driven upwardly so that the volume of the compression chamber 428 is increasing, the three way electronically controlled valve 700 prevents air from passing through the second pipe 466. The inlet 1300 is kept closed by the valve 1308.

When the piston 406 is at its nighest position so that the volume of the compression chamber 428 is at its maximum Vo MAX, the three way electronically controlled valve 700 is closed by the controller to prevent air from passing through it via any of the pipes 708, 466, 710.

When the piston 406 is in its highest position, the volume of the compression chamber 428 is at its maximum VoMEx and the inlet 1300 faces into the compression chamber 428 below the piston 405. Whilst the p ston 406 is in its highest position, the valve 1308 is opened by the crank shaft (not shown) '1 a the mechanical link. The fluid 1304 containing the dissolved solids flows from the tank (nct shown) via the pipe 1302 to the inlet 1300 and then into the compression:hamber 428. The valve 1308 is kept open for a predetermine amount of time by the crank shaft as it passes through a predetermined range of angular positions whilst the piston 406 is approaches, passes through and leaves its highest position, to ensure that a predetermine amount of fluic 1304 with dissolved solids enters the compression chamber 428. Once the crank snaft exists the predetermined range of angular positions, it closes the valve 1304.

When the piston 406.s being axially driven downwardly so that the volume of the compression diamber 428 is decreasing, the three way electronically controlled valve 700 is kept dosed by the controller to prevent air from passing through any of the pipes 708, 466, 710. The inlet 1300 is also kept dosed by the valve 1308. As such, the air in the compression chamber 428 are compressed increasing both its pressure and temperature as it is compressed. This increases the temperature of the fluid 1304 and solids causing the fluid 1304 to evaporate.

When the piston 406 s at its lowest position so that the volume of the compression chamber 428 is at its minimum Vo MI14 and the pressure and temperature of the air, vapourised fluid 1304 and solids inside of the compression chamber 428 are at their maximum, the three way electronically controlled valve 700 is opened by the controller to allow a compressed heated pulse of air to pass, with the vapourised fluid and solids, through the first pipe 708, through the three way electronically controlled valve 700, through the second pipe 466 and then enter the separator 1400 so flat the separator can operate in the same manner as described above in the third em3odiment with reference to Figure 6. Whilst the pulse of heated compressed air, with the vapourised fluid and solids, pass into the separator, the three way electronically controlled valve 700 maintains the second pipe 710 closed.

The cycle is then repeated.

A seventh embodiment of the invention will now be described with reference to Figure > 10A and 10l3.

Referring to Figure WA, the seventh embodiment of the separation device comprises a propellor 800 which pressurises air within a pressure chamber 810. The pressure chamber 810 is connected to a separator 1400 (not shown) which is the same design as the sepa-ator described in the third embodiment with re ference to Fig ire 6. A valve V1 allows the pressurised air to periodically be released from the pressure chamber 802 and enter the separator 1400 as a series of pulses of hot pressurised ai-. Where the same features which are present in the third embodiment of the separation device are present in the seventi embodiment, the same reference numbers have been used.

The difference between the seventh embodiment of the separation device ard the previous embodiments is the design of the mechanical compressor 806. Referring to Figure 10A, the mechanical compressor 806 comprises an elongate tube 808 which forms a tubular passageway 810. Attached at one end is a propeller housing 812, the chamber 814 in wrich is connected to the tubular passageway 810. Attached, close to the other end is the valve Vi. A controller (not shown) controls the operation of the valve Vito open or close the valve. The operadon of the valve V1 can either be controlled mechanically or electronically. An inlet 1300 is attached to the side the elongate tube 808, through which the fluid with the dissolved solids can be injected into the tubular passageway 808. The injection is also controlled by the controller.

The propeller 800 is located within the chamber 814 of the propeller housing 812 and is rigidly mounted on a rotatable shaft 816. The rotatable shaft 816 is rotated using an external force. Such a force can be generated by a separate fan or propellor (not shown) due to the movement of air or water through the fan or propellor such as wind acting on a wind turbine or sea water passing through a water turbine due to the movement of the water causec by the tide. Alternatively, the force could be generated by an electric motor (not shown), a pneumatic motor (not shown), a hydraulic motor (not shown), a petrol or diesel engine (not shown) or any known device which is capable of generating a rotational movement.

When the propeller 800 is rotationally driven in the direction of Arrow T, air is driven in the direction of Arrow U from the chamber 814 into the tubular passageway 810. When the valve V1 is closed, preventing any air from passing through the valve V1, the air enters the tubular passageway 810 but is prevented from exiting it. As such both the pressure and temperature of the air within the tubular passageway 810 increases, the tubu ar passageway 810 acting as a pressure chamber. A return valve (shown by dashed lines 818) can be located near the entrance of the tubular passageway 810 which prevents air, which has been dr ven into the tubular passageway 810 by the rotating propelle-800, from exiting the tubular passageway way 810 and re-entering the chamber 814.

Whilst the valve V1 is closed and the propeller 800 is rotating, the air is driven i-rto the tubuia-passageway 810 with its temperature and pressure increasing. Fluid with the dissolved solids is injected into the tubular passageway 808 whilst the valve V1 is closed. The fluid vaporises due to the increase in temperature of the air in the passageway 808. When the valve V1 is opened, the hot pressurise air, vapourised fluid and solids passes from the tubular passageway 810, through the yak& V1 and exits tie end of the tubular passageway as it does. The end of the tubular passageway 810 is connected to an entrance pipe of a separator 1400 (not shown) which is the same design as separator described in the third embociment with reference to Figure 6. As such, with the appropriate control of the valve V1, pulses of hot air, vapourised fluid and solids can be eraitted from the tubu ar passageway 810 into the separator.

Figure -10B shows two graphs relating to the operation of the mechanical compressor 806 shown in Figure 10A. Graph 1 shows the status of the valve Vi versus time t with "0' indicating open and "C indicating closed. Graph 2 shows the pressure P inside of the tubular passageway 810 versus time t with "AT" indicating atmospheric pressure. When the valve V1 is closed ("C" in graph 1), the pressure inside of the tubular passageway 810 increases (see graph 2) due to the rotating propeller BOO driving air from the chamber 814 into the tubular passageway 810. As the pressure increases, the temperature of the air within the tubular passageway 810 also increases. This causes the fluid to vapririse.

When the valve V1 is opened ("0" in graph 1), the air, vapourised fluid and solids is able to pass through the valve V1, exit the tubular passageway and enter the entrance pipe of the separator, the pressure inside of the tubular passageway 81C decreasing rapidly (see graph 2) as k. does so. By opening and closing the Valve V1 as shown in graph 1, a series of hot air pulses with vapourised fluid and solids can be generated which can be fed into the separator.

An eighth embodiment of the invention w,1 now be described with reference to Figures 11A. I1B and 11C.

Referring to Figure 11A, the eighth embodiment of the of the separation device comprises a pro:char 900 which pressurises air within a pressure chamber 910. The pressure chamber 910 is connected to a single separator 1400;not shown) via a side pipe 930. The separator is the same design as the separator described in the third embodiment with reference to Figura 6.. A first valve VI allows the pressurised air to periodically be released from the pressure cha-nber 910 into the surrounding atmosphere. A second valve V2 allows the pressurised air tc periodically be released from the pressure chamber 910 and enter the separator 1400 as a series of pulses of hot pressurised air. Where the same features which are present in the seventh embodiment are present -n the eighth embodiment, the same reference numbers haw, been used.

The difference between the eighth embodiment of the separation device and the previous embodiments is the design of the mechanical compressor 906. Referring to Figure 11A, the mechanical compressor 906 comp -ises an elongate tube 908 which forms a tubular passageway 910. Attached at one end is a propeller housing 912, the chamber 914 in which is con-Rcted to the tubular passageway 910. Attached close to the other end is the valve Vi. Theside pipe 930 attaches to the side of the elongate tube 908 so that internal passageway 932 of the side pipe 930 connects and is in fluid communication with the tubular passageway 910. Attached, close to the end of the side pipe 930 remote from the elongate tube 908, is the second valve V2. A controtle-(not shown) controls the operation of the valves V, V2, to open or closed the valves. The operation of the valves V1, V2 can either be con:rolled mechanically or electronically. An inlet 1300 is attached to the side of the elongate tube 908 through which the fluid with dissolved solids can be injected into the tubular passageway 910. The injection is controlled by the controller.

The propeller 900 is located within the chamber 914 of the propeller housing 912 and is rigidly mounted on a rotatable shaft 916. The rotatable shaft 916 is rotated using an external force. Such a force can be generated by a separate fan or propellor (not shown) due to the movement of air or water through the fan or propellor such as wind acting on a wind turbine or sea water passing through a water turbine due to the movement of the water caused by the tide. Alternatively, the force could be generated by an electric motor (not shown), a pneimatic motor (not shown), a hydraulic motor (not shown), a petrol or diesel engine (not shown) or any known device which is capable of generating a rotational movement.

When the propeller 900 is rotationally driven in the direction of Arrow T, air is driven in the dire:lion of Arrow U from the chamber 914 into the tubular passageway 910. When the valvas V1, V2 are closed, preventing any air from passing through the valves VI, V2, the air enters the tubular passageway 910 but is prevented from exiting it. As such, both the pressure and temperature of the air within the tubular passageway 910 increases, the tubular passageway £10 acting as a pressure chamber. A return valve (shown by dashed lines 918) can be located near the entrance of the tubular passageway 910 which prevents air, which has been driven into the tubular passageway by the rotating propeller 900, from exiting the tubular passageway way 910 and re-entering the chamber 914.

Whilst the valves V1, V2 are closed and the propeller 900 is rotating, the air is driven into the tubular passageway £10 with its temperature and pressure increasing. The fluid with dissolved solids is injected through the inlet 1300 into the tubular passageway 910. The fluid vaporises due to the temperature increase of the air.

When the first valve V1 is opened whilst the second valve V2 remains closed, the hot pressurised air, vapourised fluid and solids passes from the tubular passageway 910, through the first valve V1 and exits the end of the tubular passageway 910 and enters the surrounding atmosphere. The pressure inside of the tubular passageway drops as the air passes through the first valve Vi.

When the second valve V2 is opened whilst the first valve V1 remains closed, the hot pressurise air, vapourised fluid and solids passes from the tubular passageway 910, through the side pipe 930, though the second valve V2 and exits the end of the side pipe 930 as it does so. The end of the side pipe 930 is connected to an entrance pipe of a separator 1400 (not shown) which is the same design as the separator described in the third embodiment with reference to Figure 6. As such, with the appropriate control of the valves V1, V2. pulses of hot air, vapourised fluid and solids can be emitted from the tubular passageway 910, through the side pipe 930 and into the entrance pipe of the separator 1400.

Figure 118 shows three graphs relating to the operation of the mechanical compressor 906 shown in Figure 11A in accordance with a first operating regime. Graph 1 shows the status of the second valve V2 versus time t with "0" indicating open and "C" indicating closed_ Graph 2 shows the status of the first valve V1 versus time t with "0" indicating open and "C" indicating closed. Graph 3 shows the pressure P inside of the tubular passageway 910 versus time t witp "AT" indicating atmospheric pressure.

When the first valve V1 is open ("0" in graph 2) and the second valve V2 is closed ("C" in graph 1), the pressure inside of the tubular passageway 910 remains at atmospheric pressure (see graph 3).

When both the valves V1, V2 are closed ("C" in graphs 1 and 2), the pressure inside of the tubular passageway 910 increases (see graph 3) due to the rotating propeller 900 driving air from the chamber 914 into the tubular passageway 910. As the pressure increases, the temperature of the ai-within the tubular passageway 910 also increases.

When the second valve V2 is opened ("0" in graph 1) whilst the first valve V1 remains closed ("C" in graph 2), the a r with vapourised fluid and solids is able to pass through the second valve V2, exit the tubular passageway 910, pass through the side pipe 930 and enter the entrance pie of the separator 1400 as a pulse, the pressure inside of the tubular passageway 910 decreasing rapidly (see graph 3) as it does so. By opening and closing the Valves V1, V2 sequentiaily as shown in graphs 1 and 2, a series of hot air pulse can be generated which can be fed into the separator.

Figure 11C shows three graphs relating to the operation of the mechanical compressor 906 shown in Figure 11A in accordance with a second operating regime. Graph 1 shows the status of the second valve V2 versus time t with "0" indicating open and "C" indicating closed. Graph 2 shows the status of the first valve V1 versus time t with "0" indicating fully open and "C" indicating fully closed. Graph 3 shows the pressure P inside of the tubular passageway 810 versus time t with "AT" indicating atmospheric pressure.

As can be seen in graph 2, the first valve 1 can be partially opened 950 allowing a pre-set amount of air to constantly exit the tubular passageway 910. The amount that the valve V1 can be opened can be adjusted so a maximum amount of pressure can build up within the tubular passageway 910. During the operation of the second regime the first valve remains partially open by a constant amount, the amount remaining fixed and being set to generate a pre-determine maximum pressure within the tubular passageway 910.

When second valve V2 is closed ("C' in graph 1), the pressure inside of the tubular passageway 910 rises until it reaches the pre-determined maximum pressure. (see graph 3).

When the second valve V2 is opened ("0" in graph 1), the air, vapourised fluid and solids is able to pass through the second valve V2, exit the tubular passageway 910, pass through the side pipe 930 and enter the entrance pipe of the separator 1400 as a pulse, the pressure inside of the tubular passageway 910 decreasing rapidly (see graph 3) as it does so. By opening and closing the second valve V2 sequentially as shown in graph 1, a series of hot air pulses with vapourised fluid and solids can be generated which can be fed into the separator 1400.

The use of two valves V1, V2 enables greater control of the size and frequency of the pulses of the hot air, vaporised fluid and solids independently of the control of the rate of rotation of the propellor 900.

Whilst in the seventh and eighth embodiment of the present invention have been shown using a propellor to generate the increased air pressure, it will be appreciated that other devices can be use instead of a propeller. For example, an impeller 1000 can be used to generate an air flow 1002 as shown in Figure 12.

Alternatively, a series of pulses of hot air can be generated using a pump 1100 comprising a bottom housing 1102 and a top housing 1104 interconnected by a set of bellows 1106 and which form a chamber 1108 as shown in Figure 13. A first valve V1 allows air into the chamber 1108 and a second valve V2 allows air to exit the chamber 1108 and enter a separator. The volume of the chamber can be increased and decreased by moving the upper housing linearly towards or away from the lower housing. By controlling the valves as the volume of the chamber 1108 increases and decreases, a series of pulse of hot air. Fluid with dissolve solids can be injected the chamber 1108 through an inlet 1300.

Figure 14 shows an alternative design of pump 1200. comprising a bottom housing 1202 and a top housing 1204 pivotally connected to the top housing 1202 and which are interconnected by a set of bellows 1206 and which form a chamber 1208. A first valve V1 allows air into the chamber 1208 and a second valve V2 allows air to exit the chamber 1208 and enter a separator 1400. The volume of the chamber 1208 can be increased and decreased by pivoting the upper housing towards or away from the lower housing. By controlling the valves as the volume of the chamber 1208 increases and decreases, a series of pulse of hot air for a separator can be generated. Fluid with dissolve solids can be injected the chamber 1108 through an inlet 1300.

In all eleven embodiments described previously, the temperature of the gas in the pressure chamber (compression chamber), when the gas exits the pressure chamber, when the air has been compressed and the pressure and temperature of the air has been increased, prior to be released, is equal to or greater than 100 degrees centigrade, and preferably is equal to or greater than 150 degrees centigrade, and preferably is equal to or greater than 175 degrees centigrade, and preferably is equal to or greater than 200 degrees centigrade, and preferably is equal to or greater than 250 degrees centigrade, and preferably is equal to or greater than 30) degrees centigrade, and preferably is equal to or greater than 350 degrees centigrade, and preferably is equal to or greater than 400 degrees centigrade, and preferably is equal to or greater than 450 degrees centigrade, and preferably is equal to or greater than 500 degrees centigrade, and preferably is equal to or greatar than 600 degrees centigrade, and preferably is equal to or greater than 750 degrees centigrade, and preferably is equal to or greater than 900 degrees centigrade, and preferable is equal to or greater than 1000 degrees centigrade, and preferably is equal to or greater than 1200 degrees centigrade, In al eleven embodiments described previously, th2 prEssure of the gas in the pressure chamber (compression chamber) when the gas exits the compression chamber (428), when the gas has been compressed and the pressure and temperature of the gas has been increased, is equal to or greater than double atmospheric pressure, and preferably is equal to or greater than treble atmospheric pressure, anc preferably is equal to or greater than fi ve times atmospheric pressure, and preferably is equal to or greater than ten times atmospheric pressure,. and preferably is equal to or greater than twenty times atmospheric pressure, and preferably is equal to or greater than thirti times atmospheric pressure and preferably is equal to or greater than fifty times atmospheric pressure.

In all eleven embodiments described previously, the frecuency at which the at least one mechanical comxessor (piston compressor) provides a series of pulses of compressed heated gas, vaporised fluid and solids to the at least one separator is equal to or greater than Dne time a second (kHz), and preferably is equal tc or greater than ten times a second (10HI) and preferably is equal to or greater than a hunched times a second (100Hz) and preferably is equal to or greater than two hundred tmes a second (200Hz) and preferably is equal to or greate-than five hundred times a second (500Hz) and preferably is equal to or greater than seven hundred times a second (700Hz) and preferably is equal to or greater than a thousand tiMes a second (10Hz).

Claims

Claims 1 A separation device for removing salt from a saline soluticn comprising: a mixer capable of mixing a gas with a fluid with dissolved solids; a mechanical compressor capable of compressing the gas to heat the gas to a temperature sufficient to vaporise the fluid cf the fluid with dissolved solids mixed in the gas; a separator to subsequently separate the vapourised fluid from the solids.
2 A separation device for removing salt from a saline soluticn comprising: 1) a mixer which is capable of mixing a fluid with dissolved solids with a gas; 2) a mechanical compressor which comprises: * a housing; * a pressure chamber formed within the housing; * a mechanical device for increasing the pressure of a gas within the pressure chamber; * at least one valve which is capable of allowing the gas to enter ancior exit the pressure chamber; * at least one timing device to operate the at least one valve; * wherein the mechanical device increases the pressure and temperature of the gas within the pressure chamber sufficiently to vaporise the fluid mixed with the gas, and; * at least one timing device operates the at least one valve, at predeterminee time periods, to enable tie at least one valve to allow the gas with vapourised fluid to exit the compression chamber when the gas has been compressed and the pressure and temperature of the gas has been increased to a temperature wnich is sufficient to vaporise the fluid; and 3) at least one separator wnich, when the fluid has been vapourised, separates the solids from the vapourised fluid and gas; wherein the mixer is capable of mixing the fluid with dissolved solids with the gas either prior to the gas entering the pressure chamber or when the gas is in the pressure chamber; and wherein the separator is eitler located within the pressure chamber of the mechantal compressor or located remotely from the mechanical comprEssor.
3 A separation device as claimed in claim 2 wherein the mixer comprises an inlet formed through the wall of the housing to enable the fluid with disso ved solids to enter the pressure chamber to mix with the gas within the pressure chamber.
4 A separation device as claimed in any of the previous claims wherein the separator comprises is a cyclonic sepa-ator.
A separation device as claimed in any of the previous claims wherein the separator comprises at least one filter which allows the vapourised fluid and gas to pass through the at least one filter whilst preventing the solids from passing through it.
6 A separation device as claimed in claim 5 wherein the at least one filter is either a simple filter or a complex filter.
7 A separat on device as claimed in any of the previous claims wherein the separator is located in the mechanical compressor.
8 A separation device as claimed as claimed in either of claim 7 wherein the separator is located remotely from the mechanical compressor wherein the at least one mechanical compressor provides the compressed heated gas, vapourised fluid and solids to the at least one separato-.
9 A separation device as claimed as claimed in either of claims 7 or 8 wherein the separator is located remotely from the mechanical compressor wherein the at least one mechanical compressor provides a series of pulses of compressed heated gas, vapourised fluid and solids to the at least one separator.
A separation device as claimed as claimed in either of claim S or 9 wherein the separator comprises a chamber and a filter and/or a cyclonic separation chamber mounted in the chamber.
11 A separation device as claimed in any of the previous claims wherein the gas is air and/or the fluid is wa7er and/or wherein the dissolved solids is a salt.
12 A separaticn device as claimed in any of the previous claims wherein the fluid with dissolved solids is salt water.
13 A separation device as in any of the previous claims wherein the mechanical compressor cla im 1 wherein the at least one valve allows the gas to exit the pressure chamber when the gas has been compressed and the pressure and temperature of the gas has been increased, and preferably, in the form of a pulse.
14 A separation device as claimed in any of the previous claims wherein there is at least one outlet through which gas can exit the pressure chamber (428); wherein, preferably, the at least one valve is connected to the at least one outlet (446).
A separation device as claimed in any of the previous claims wherein there is at least one inlet through which gas can enter the pressure chamber; wherein, preferably, the at least one valve is connected the at least one inlet.
16 A separation device as claimed in any of the previous claims wherein the mechanical compressor comprises a reciprocating dr ve mechanism to alter the volume of the pressure chamber; wherein, when the reciprocating drive mechanism changes the volume the of the pressure chamber, the least one timing device operates the at least one valve to enable the at least one valve to allow the gas and vapourised fluid to: 1) enter the pressure chamber when the volume of the pressure chamber is increasing or when the volume of the pressure chamber is at its max.mum; and/or 2) exit the pressure chamber when the pressure and temperature of the gas has been increased; and/or 3) exit the pressure chamber when the volume of the pressure chamber is decreasing or when the volume of the pressure chamber is at its minimum and the pressure and temperature of the gas has been increased.
17 A separation devfce as claimed wherein the pressure of the gas when it enters the compression chamber is substantially less than when it exits the compression chamber and the temperature of the gas when it enters the compression chamber is substantially less than when it exits the compression chamber.
18) A separation device as claimed in any of the previous claims wherein the at least one valve of the mechanical compressor is capable of connecting to a separator so that, when the gas, vapou-ised fluid, and solids exits the compression chamber (428), it enters the separator.
19 A separation dev'ce as claimed in any of the previous claims wherein the mechanical compressor is a piston compressor, wherein the piston compressor comprises: a cylinder block; a cylinder formed in the cylinder block; at least one piston slfdeably mounted within the cylinder; wherein a compression chamber is formed between the internal walls of the cylinder and at least one surface of tie at least one piston, the volume of the compression chamber being dependent on the position of the at least one piston within the cylinder; a reciprocating drive mechanism which reciprocatingly drives the at least one piston within the cylinder to change the volume the of the compression chamber; at least one valve which is capable of allowing a gas to enter and/or exit the compression chamber; at least one timing device to operate the at least one valve; characterised in that, when the reciprocating drive mechanism is reciprocatingly driving the at least one piston within the cylinder to change the volume the of the compression chamber, the least ore timing device operates the at least one valve, at predetermined time periods, to enable the at least one valve to: 1) allow the gas to enter the compression chamber in order for it to be compressed by the reciprocating movement of the at least one piston; and 2) allow the gas to exit the compression chamber when the gas has been compressed and the pressure and temperature of the gas has been increased.
20) A separation device as claimed in any of the previous claims wherein the mechanical device comprises a pro 3ellor or impeller, which, when rotated, increases the pressure of the gas within the pressure chamber.
21) A separation device as claimed in any one of the previous claims wherein a) the temperature of the gas in the pressure chamber when the gas exits the compression chamber 1428), when the gas has been compressed and the pressure and temperature of the gas has been increased, is equal to or greater than 100 degrees centigrade, and preferably is equal to or greater than 150 degrees centigrade, and preferably is equal to or greater than 200 degrees centigrade, and preferably is equal to or greater than 300 degrees centigrade, and preferably is equal to or greater than 400 degrees centigrade, and preferably is equal to or greater than 500 degrees centigrade, and preferably is equal to or greater than 750 degrees centigrade, and preferably is equal to or greater than 900 degrees centigrade, and preferably is equal to or greater than 1000 degrees centigrade; and/or b) the pressure of the gas in the pressure chamber when the gas exits the compression chamber (428), when the gas has been compressed and the pressure and temperature of the gas has been increased, is equal to or greater than double atmosaheric pressure, and preferably is equal too' greater than treble atmospheric pressure, and preferably is equal to or greater than five times atmospheric pressure, and preferably is equal to or greater than ten times atmospheric pressure,. and preferably is equal to or greater than twenty times atmospheric pressure, and preferably is equal to or greater than fifty times atmospheric pressure.
22) A separation device as claimed in any one of the previous claims wherein the frequency at which the at least one mechanical compressor provides a series of pulses of compressed heated gas to the at least one separator is equal to or greater than one time a second (1Hz), and preferably is equal to or greater than ten times a second (10Hz) and preferably is equal to or greater than a hundred times a second 0.Ct0Hz), and preferaoty is equal to or greater than two hundred times a second (200Hz) and preferably is equal to or greater than five hundred times a second (500Hz) and preferably is equal to or greater than seven hundred times a second (700Hz), and preferably is equal to or greater than a thousand times a second (10Hz).
23) A separation devize as claimed in any of the previous claims wherein the separator condenses the vapourised fluid after the solids have been removed and/or there is provided a separate condenser which condenses the vapourised fluid into a fluid once the solids have been removed:from the fluid.
24) A method of desalinating a salt solution using a separation device according to any of claims 1 to 24 wherein -.he method comprises the steos of: 1) mixing the water with a salt dissolved within it, preferably sea water, with a gas; 1) operating the separation device so that the salt is removed fro-n the vapourised water by the separator; and 3) condensing the water vapor.
25) A method of desalinating a salt solution using a separation device for removing salt from a saline solution comprising: a mixer; a mechanical compressor; a separator; 6. wherein a gas is mixed a fluid with dissolved solids in. the mixer; 7. wherein the mechanical compressor compresses a gas to heat the gas; 8. wherein the heated gas vaporizes the fluid; 9. wherein the separator separates the vapourised fluid from the solids; 10. condensing the vapourised fluid.