MULTIPLE-STAGE PUMP

Abstract: A pump system for pumping a first fluid from a source to a storage facility (126) comprising a multiple-stage small temperature differential heat-powered pump (124), a second fluid heater (123) operable to heat a second fluid to a fixed hot temperature, and a third fluid cooler (125) operable to cool a third fluid to a fixed cold temperature, wherein hot fluids and cold fluids are diverted into the multiple-storage small differential heat-powered pump, the pump is also useful as a compressor for utilization in a heating and cooling system which comprises separate hot and cold containers connected to flexible member within pressure chambers in each of a plurality of pumping stages.

Description: ILTIPLE-STAGE PUMP BACKGROUND OF THE It-JVEINTiα. This invention rel tes to a heat-pσwered pump and more particularly to a multiple-stage small temperature differential heat-powe pump and a generating system utilizing a plurality of multiple-stage smal temperature differential heat-powered pumps. Previous inventions have utilized a flexible diaphragm as the pumping element with a volatile liquid as a working fluid. The prior art is limited in the pressure and volurre of fluid that can be pumped when a vaporizable liquid is varied within set temperature limits. The use of a single vaporizable liquid in heat-pcwered hydraulic pumps operating bet_we fixed temperatures limits the output pressure capability to an extent tha such pumps are relegated to applications where lew pressure and pumping capacities are acceptable. Many desired applications require higher pres and higher flow rates, such as high-capacity irrigation systems, pumping water from a lower level to a higher level reservoir for muxicipal-type water systems, and the powering of a large hydraulic turbine electric generator combination for the inexpensive conversion of solar energy into electric power. In localities lacking elevated water storage facilities o when electric power is needed only during daylight hours, a generating sys as disclosed herein, might be preferable utilizing a plurality of multiple stage small temperature differential heat-pwered purrps. T_he present invention comprises a πailtiple-stage small temperature differential heat- powered pump which has the capability of a high output pressure when opera ing between fixed temperatures. The present invention can also be utilized to provide for a solar powered air cooling system or an earth-heat-powered air heating system. I the solar-powered air cooling system, heat which is noπrally lost can be used in a regenerating process to improve the efficiency of the air coolin system. In the earth-heat-powered air heating system, cold which is norma lost can be utilized to jjπprαve the efficiency of the air heating system. This invention provides for a pump which by utilizing multiple stages can elevate the output pressure and temperature to desired levels utilizing a plurality of designated fluids in varied states. The inventio is applicable to large installations, such as the powering of large electr generators, and is also applicable to smaller systems, such as heating and cooling small buildings. - jUEAl O PI SgyM-RY OF THE IMVEISITIO An object of the present invention is to provide a multiple- stage small temperature differential heat-powered pump operable to produce high output pressures utilizing fixed teπrroeratures. Another object of the present invention is to provide a generating system utilizing a plurality of multiple-stage small temperatur differential heat-powered pumps. A further object of the present invention is to place a plural of containers holding a plur lity of fluids into two conduits which altern hold hot and cold water in order to alternately vary the pressure of the plurality of fluids to the vapor pressure for a fixed cold temperature and the vapor pressure for a fixed hot temperature. Still another object of the present invention is to provide a multiple-stage small temperature differential heat-powered pump wherein each stage is separated by one of a plurality of check valves. A further object of the present invention is to provide a multiple-stage small temperature differential heat-powered pump wherein each stage has a pressure chamber including a flexible member containing the vapor of one of a plurality of fluids and wherein the fluid in the flexible msnber in one stage is being subjected to a hot temperature while the fluid in the flexible member in the next stage is subjected to a cold temperature with the temperatures in each flexible msnber alternating as the putrping operates. Another object of the present invention is to provide a πultip stage small temperature differential heat-pcwered pump with fluid heating means and fluid cooling means which enter an input fluid diverting means wherein a hot fluid and a cold fluid are alternately diverted into a plurality of conduits within which are containers holding a plurality of vaporizable fluids. Still another object of the present invention is to provide a generator utilizing a plurality of multiple-stage small temperature differential heat-powered pumps utilizing fluid heating means and fluid cooling means to provide a hot and cold fluid to an input fluid diverting means which diverts a hot and cold fluid alternately into a plurality of conduits within which are a plurality of containers holding a plurality of vaporizable fluids. C PI ^ IPO • * A further object of the present invention is to provide a multiple-stage small temperature differential heat-powered pump and a generating system utilizing a plurality of multiple-stage scπall temperat differential heat-powered pumps which can utilize solar energy in fluid heating means to provide for cctrinercial solar power production. Another object of the present invention is to provide vapor pressure control means which can utilize a separate cold container and h container for each flexible member. Still another object of the present invention is to provide a vapor pressure control means which can be utilized to provide for a plur of flexible members within a single pumping stage. A further object of the present invention is to provide a plura of flexible members within a single pumping stage, each provided by its vapor pressure control means. Another object of the present invention is to provide for solar means to be utilized to heat the hot container of a vapor pressure contr means. Still another object of the present invention is to provide a below ground location for the cold container of a vapor pressure control means. A further object of the present invention is to provide an evaporative cooler to conta n the cold container of a vapor pressure control means. Another object of the present invention is to provide a below ground location for the hot container of a vapor pressure control means. Still another object of the present invention is to provide for a solar-powered air cooling system. A further object of the present invention is to provide for an earth-heat-pσwered air heating system. These and other objects and features of the invention will be apparent from the following description and appended claims. OMPI Yfy , 1?0 Briefly, the specification discloses a pump systsn for pumping a first fluid from a source to a storage facility and a generating systsn for converting flow of a pressurized first fluid to electrical power. The pump system comprises a multiple-stage small temperature differential heat-powere pump. A second fluid heating means is operable to heat a second fluid to a fixed hot temperature. The hot fluid is diverted into the multiple-stage smalU. tsπperature differential heat-powered pump. A third fluid cooling mea is operable to cool a third fluid to a fixed cold temperature where it becom a cold fluid. The cold fluid is divertable into the multiple-stage small temperature differential heat-powered pump. The generating system comprises a plurality of multiple-stage small temperature differential heat-powered pumps utilized along with the second fluid heating means operable to heat a second fluid to a fixed hot temperature where it becomes a hot fluid and a third fluid cooling means operable to cool a third fluid to a f xed cold tsπperature where it becomes a cold fluid. The hot fluid and cold fluid are divertable into a plurality of multiple-stage small temperature differential heat-powered pumps. A hydraulic-to-_ιechanical power conversion means is operative to convert the flew of the pressurized first liquid to mechanic power. The input of the hydraulic-to-mechanical power conversion means is connected to the output of the plurality of the multiple-stage small tempera ture differential heat-powered pumps. The output of the hydraulic-to-mechan power conversion means is connected to the input of the plurality of multipl stage small tsrperature differential heat-powered pumps. A mechanical-to- electrical power conversion means is connected to the hydraulic-to-mechaiica power conversion means and is operative to produce electrical power. The hot fluid may be hot water and the cold fluid may be cold water. The second fluid heating means may utilize solar energy to heat the second fluid to a fixed hot temperature. The hot fluid and the cold fluid are pumped into an input fluid diverting means which controls the flow of the hot fluid and the cold fluid into the multiple-stage small tβnperature differential heat-power pump. The input fluid diverting means diverts the hot fluid and the colft fluid alternately into each one of a plural-L^y of conduits within the multiple-stage small temperature differential heat-powered pump. Eacn of th plurality of multiple-stage small tsηperature differential heat-powered pump cαrprises a plurality of pumping stages and a plurality of check valves. OMPI Cne of the plurality of check valves is located on the input an output of each multiple-stage small temperature differential heat-powere pump. A check valve is also located between each of the plurality of pum stages. Each of the plurality of pumping stages comprises a pressure cha operable to hold the first fluid. A flexible member within the pressure chamber operates, when ex to exert pressure against the first -fluid and to force the first fluid fr the pressure chamber through one of the plurality of check valves between pressure chamber and the next pressure chamber of the next subsequent pum 0 stage of the plurality of pumping stages or the output, if the pressure chamber is within the last of the plurality of pumping stages, when the pressure within the pressure chamber exceeds the next pressure in the nex pressure chamber or the output. The flexible msnber is connected to a co tainer which is.one of a plurality of containers. Each of the plurality containers holds one of the plurality of vaporizable fluids. When the container is subjected to hot fluid, the vaporizable fluid vaporizes caus the flexible msnber to expand. When the container is subjected to cold f the vaporizable fluid condenses, causing the flexible πvariber to contract. Each one of the plurality of vaporizable fluids which vaporizes into the flexible msnber has a higher vapor pressure, when heated to the fixed hot temperature, than the cold vapor pressure of the next one of th plurality of vaporizable fluids which vaporizes into the next flexible me within the pressure chambers or to the output, if the flexible msnber is within the last of the plurality of pumping stages. Each one of the plurality of containers is secured within one o the plurality of conduits. Each container is subjected alternately to th hot fluid and then the cold fluid. Each of the plurality of pumping stag has a flexible msnber connected to one of the plurality of containers. E one of the plurality of containers is secured within one of the plurality conduits and is subjected alternately to hot fluid and cold fluid. The next subsequent pumping stage of the plurality of pumping stages has a next flexible member connected to another one of the pluralit ■ of containers which is secured within another one of the plurality of con and is also subjected alternately to the cold fluid and the hot fluid at times opposite to the first of the plurality of containers. When one of t plurality of containers is subjected to the hot fluid, the another one of the plurality of containers is subjected to the cold fluid and vice versa. In the plura ity of pumping stages, when the first stage has a first flexible member connected to a first cont iner subjected to the hot fluid, the second stage would have a second flexible inember connected to a second container subjected to the cold fluid. Each odd-nι_mbered oontainer subjected to the opposite condition of each even-numbered container. When first stage has a first flexible msnber connected to the first container subjected to cold fluid, the second -stage has a second flexible member connected to the second container subjected to the hot fluid. Each odd- numbered cont iner is subjected to the opposite condition of each even- numbered contai er within the plurality of containers connected to the plurality of pumping stages. The first vaporizable fluid in the first contai er, which is connected to the first flexible msnber in the first pumping stage, has a cold vapor pressure lower than the pressure of the first fluid in the sour In the generating system, the first vaporizable fluid in the first contain which is connected to the first flexible inember in the first pumping stage has a cold vapor pressure lower than the pressure of the output of the hydraulic-to-^αec_hanical power conversion means. The second vaporizable fluid in the second container, which is connected to the second flexible member in the second pumping stage, has a cold vapor pressure lower than the hot vapor pressure of the first vaporiz fluid in the first container. When the first container is subjected to th fluid and when the second container is subjected to the cold fluid, the pressure within the first pumping stage is greater than the pressure withi the second pumping stage and the first fluid will move through the one of the plurality of check valves between the first pumping stage and the seco pumping stage into the second pumping stage. The plurality of conduits may comprise a first conduit and a sec conduit. The output fluid diverting means is operable to control the flow the hot fluid from the multiple-stage small temperature differential heat- powered pump back to the second fluid heating means and to control the fle of the cold fluid from the multiple-stage small temperature differential h powered pump back to the third fluid cooling means. The input fluid diver means comprises an inlet gate with a first inlet gate position and a secon inlet gate position. When the inlet gate is in the first inlet gate posit the hot fluid is diverted into the first conduit and the cold fluid is div into the second conduit. When the inlet gate is in the second inlet gate position, the h fluid is diverted into the second conduit and the cold fluid is diverted the first conduit. The output fluid diverting means comprises an outlet with a first outlet gate position and a second outlet gate position. Wh the outlet gate is in the first outlet gate position, the hot fluid is diverted frcm the first conduit back to the second fluid heating means an the cold fluid is diverted from the'second conduit back to the third flui cooling means. When the outlet gate is in the second outlet gate positio the hot fluid is diverted frcm the second conduit back to the second fluid heating means and the cold fluid is diverted from the first conduit back the third fluid cooling means. A gate control means is connected to one the plurality of multiple-stage small temperature differential, heat-pcwere pumps and operates to change the inlet gates and the outlet gates simul¬ taneously frcm one gate position to another. Each of the plurality of che valves may comprise a plurality of hinged members. The generating system may have two multiple-stage small temperat differential heat-pcwered pumps. In the even-numbered pumping stages for each of the two multiple-stage snail temperature differential heat-powered pumps, the eveα-nu bered flexible msribers within the even-numbered pressur chambers are connected to the even-numbered containers which are located i the same conduit with the odd-numbered containers which are connected to t odd-numbered flexible msribers within the odd-numbered pressure chambers of the other multiple-stage small temperature differential heat-powered pump. The container for the first vaporizable fluid is connected to th first flexible member and the container for the t_hird vaporizable fluid is connected to the third flexible member in the first multiple-stage small temperature differential heat-powered pump and are secured in the first conduit along with the container for the second vaporizable fluid connecte to the second flexible msnber in the second multiple-stage stall tsrperatu differential heat-powered pump. The container for the first vaporizable fluid connected to the first flexible msnber and the container for the thi vaporizable fluid connected to the third flexible msnber in the second multiple-stage small temperature differential heat-powered pump are secure in the second conduit along with the container for the second vaporizable fluid connected to the second flexible member in the first multiple-stage small temperature differential heat-pcwered pump. In the generating system, the first vaporizable fluid in the fir multiple-stage small temperature differential heat-powered puπp may be identical to the first vaporizable fluid in the second multiple-stage smal temperature differential heat-powered pump. Each numbered vaporizable fl connected to the same numbered stage in each of the two multiple-stage sm tβnperature differential heat-powered pumps is identical for each similar stage of the two multiple-stage snail -temperature differential heat-pcwer pumps. Each succeeding stage, of course, has a different vaporizable flui with different pressure properties for the fixed hot and cold tβcperature She plurality of multiple-stage small temperature differential heat-powered pumps may be two or a greater plurality, if desired, and if sufficient fluid heating means and fluid cooling means are available to support the desired plurality of multiple-stage small tβnperature differe heat-powered pumps. 3Jte invention is a cooling system, a heating system, and a pump system. The ccoling systeπvcools an enclosure,cααprising a ccπpressαr, condensing means, and an evaporating means. The ccπpressor utilizes a pump system comprising a multiple-stage pump for pumping a first fluid through the ultipler-stage pump, raising the temperature and pressure of the first fluid, de condensing means is connected to he putrp system through which the first fluid flows.. The first fluid is condensed and he is rsnoved. The evaporating means is within the enclosure and connected the pump system and the condensing means. The evaporating means is opera to cool the enclosure. Tbe multiple-stage puπp cαrprises a plurality of stages and a plurality of check valves. Oie of the plurality of check valves is locat on the input and output of the multiple-stage puπp and between each of th plurality of pumping stages. Each of the plurality of pumping stages corrprises a pressure chamber which is operable to hold the first fluid. A flexible member within the pressure chamber is operable, wh expanded by a vapor from a second fluid, to exert pressure against the first fluid. The first fluid is forced from the pressure chamber through one of the plurality of check valves between the pressure chamber and the next pressure chamber of the next subsequent pumping stage of the plurali of pumping stages or the output. If the pressure chamber is within the l of the plurality of pumping stages, it will be the output. A flexible member is connected to a vapor pressure control means virich is operative cause the flexible member to expand or contract at a given time. The vapor pressure control means comprises a cold container connected to the flexible member and is operative to keep the second flui cold, and a hot container connected to the flexible msnber and is operati to keep the second fluid hot. A cold container control means is connecte to the cold container and is operative to open or close the connection between the cold container and the flexible member. A hot container control means is connected to the hot cont iner and is operative to open or close the connection between the hot cont ner and the flexible member A vapor pressure control sensing means is connected to the flexible membe and is operative to sense the condition of the flexible member and to ope or close the cold container control means and the hot container control means acα_α * d__ngly. The vapor pressure control sensing means may comprise a magnet secured onto the flexible msnber, an upper magnetic proximity switch, and a lower magnetic proximity switch. The upper magnetic proximity switch is secured within the pressure chamber and is operative to be activated when the flexible member is enlarged. The lower magnetic prcxxilmity switch is secured within the pressure chamber and is operative to be activated when the flexible msnber is deflated. A valve command generator is connected t the upper magnetic proxiiity switch and the lower magnetic proximity switc and is operative to open and close the cold container control means and th hot container control means when receiving the appropriate indication of the flexible member being enlarged or deflated. A condensate pump may be connected between the cold cont iner and the hot container and is operative to pump the second fluid from the cold container to the hot container. The condensate pump control means is connected between the cold container and the condensate pump and is operat to sense the liquid level of the second fluid in the cold container to acti the condensate puπp. The hot container may be secured within a solar collector. The cold container nay be secured below the ground level. The condensing mean may be secured within the solar collector, along with the hot container, in order to remove the heat from the first fluid and to transfer the heat to the second fluid within the hot container, thereby creating a regenerat ing system ixvcreasing the efficiency of the solar collector and the coolin system. ■ * fE OMP lir The pressure chamber may comprise a plurality of flexible msriber connected to a single vapor pressure control means. The pressure chamber may also comprise a plurality of flexible members, each connected to a different vapor pressure control means. The flexible member in each of t plurality of pumping stages may be connected to a vapor pressure control means which can exparei or contract the flexible eπber utilizing vapor fr a first vaporizable fluid which has * a higher heated pressure than the col temperature vapor pressure of a second vaporizable fluid used within the next flexible msmber within the next ptnping stage, or the output if the flexible member is within the last of the plurality of pumping stages. The solar collector may contain a plurality of hot dontainers, each containing a different vaporizable fluid and secured to a diff rent flexible msnber, which is secured within a different pumping stage within the multiple-stage pump. • The heating system cαπprises a cαπpressor, a cordensing means within the enclosure, and evaporating means. The condensing means heats the enclosure. In the heating system, the cold container may be secured within an evaporative cooler and the hot container secured below ground level. The evaporating means may be secured within the evaporative coole along with the cold container, in order to remove heat from the evaporati cooler, thereby to remove the heat from the second fluid within the cold container, thereby creating a regenerating system increasing the efficien of the evaporative cooler and the heating system. The evaporative cooler may contain a plurality of cold containers, each containing a different vaporizable fluid and secured to a different flexible member which is secured within a different pumping srtage within the multiple-stage pump. The pump systsn pumps a first fluid and ccnprises the ultiple- ϊtage pump with a plurality of ≤stages, and a plurality of check valves. The plurality of pumping stages each have a pressure chamber and a flexib msnber. A vapor presj__ure control means is connected to the flexible memb and is operative to caus_e the flexible member to expand or contract. The vapor pressure control means comprises a cold container, a hot container, a cold container control means, and a hot container control means. A vap pressure control sensing means is connected to the flexible member. - i BRIEF DESCRIPTION OF THE DRflWIEJGS The invention will be more fully understood frcm the follow detailed description and appended cl ims when taken with the drawings i which: FIG. 1 is a perspeσtive view of a solar-powered multi-stage pumping systsn used for filling a reservoir 126 and generating electrici FIG. 2 is a schsratic display of the pumping sequence for heat-powered pump system 244. FIG. 3 is a schematic repressentatiαn of heat-powered pump system 244. FIG. 4 is a top view of heat-powered pump system 244. FIG. 5 is a sectional view through section 5-5 of check valv assembly 13 in FIG. 4. FIG. 6 is a partial sectional view at section 6-6 of second conduit 43 in FIG. 4. . FIG. 7 is a partial sectional view at section 7-7 of firsϊt conduit 42 in FIG. 4. FIG. 8 is an end elevational view of the discharge end of heat-powered pump systsn 244. • FIG. 9 * is an end elevational view of the intake end of heat- powered pump systsn 244. FIG. 10 is a graphic representation showing the relationship between the pounds pres_sure per sϊquare inch gauge and the stage utilized with a specific vaporizable fluid and teπperature applied thereto for th various stages in the pumping sequence. FIG. 11 is a schematic representation of gate control means FIG. 12 is a lateral sectional view through input fluid dive ing means 147 at inlet gate 65. FIG. 13 is a sectional view of input fluid diverting means 1 taken at section 13-13 of FIG. 12 FIG. 14 is a partial isometric view of heat collector condui 61 of fluid heating means 123. FIG. 15 is a sectional view of heat collector conduit 61 of fluid heating means 123 taken at section 15-15 of FIG. 14. FIG. 16 is a cross-sectional view of cooling conduit 151 whi may be utilized as fluid cooling means 125. FIG. 17 is a schsratic representation of heat-powered genera system 245. FIG. 18 is a schematically repressented view of heat-powered generating systsn 245. FIG. 19 is a graphic representation showing the relationship between the pounds pressure per square inch gauge and the sϊtage utilized with the sspecific vaporizable fluid and tsrperature applied thereto for various stages in the pumping ssequences within the heat-powered generating system 245. • . FIG. 20 is a sectional view of check valve 13 at section 20-20 of FIG. 5. FIG. 21 is a schematic drawing of an individual hot container and c container utilized to heat and cool a second fluid. FIG. 22 is a schematic diagram of a solar collector utilized for heating a second fluid and a cold ground container utilized for cooling a se fluid. FIG. 23 is a schematic diagram of an evaporative cooler utilized fo cooling a second fluid and a hot ground container utilized for heating a second fluid. FIG. 24 is a schematic diagram of a plurality of expandable members ' being .supplied with vapor from a single vapor pressure control means. FIG. 25 is a schematic diagram of a plurality of expandable members, each expandable msnber being supplied from a different vapor pressure control means. FIG. 26 is a schematic diagram of a sso ar-powered air cooling system. FIG. 27 is a graphic representation showing the relationship between the pounds pressure per square inch gauge and the stage utilized with a speci ic vaporizable fluid and tsπperature applied thereto for the various stages in the pumping sequence of the solar-powered air cooling systsn of FIG. 26. FIG..28 is a schsratic diagram of an earth-heat-powered air heating system. TIG. 29 is a graphic representatiωi s_howi_iy the ieiu Lonship between the pounds pressure per square inch gauge and the stage utilized with a specific vaporizable fluid and temperature applied thereto for the various stages in the pumping sequence of the earth-heat-powered air beating systsn of FIG. 28. O PI DETAIIED DESCRIPTICN Referring now to the drawings, FIG. 1 is a perspective view o a solar-powered multi-stage pumping systsn used for filling a reservoir 1 and generating electricity. The reservoir 126 is shown located in high o mountainous land 157. The multiple-stage small temperature differential heat-powered pump 124 is shewn located in flat land 156. Fluid heating means 123 is utilized to heat a fluid. The fluid heating means 123 shown is a conduit-type solar collector utilizing conduit 61. Fluid cooling me 125, for this illustration, is the river 125 which is also the source of the fluid taken in through inlet pipe 70. Connecting conduit 149 is the inlet conduit for the cold fluid far the system. Qannecting conduit 148 is the outlet connecting conduit carrying the cold fluid from the system back to the river 125. Pipe 34 carries the pressurized fluid 35 up to th elevated storage means or reservoir 126. Fluid ssupply pipe 246 supplies pressurized fluid to generating ϊtation 153. Discharge pipe 247 discharg fluid frcm generating station 153 back into the cold fluid ssupply, which is the river 125. Extending from generating srtation 153 are electrical wires 130 carrying electricity to an electrical load 152 (not sshown) . FIG. 1 is merely illustrative of one prospective possibility for utilizat of the heat-powered pumping systsn 244 of the pressent invention. FIG. 2 is a schsratic display of the pumping sequence for hea pcwered pump systsn 244. Heat-pcwered pump system 244 comprises pumping stages 1, 2, 3, 4, 5, and 6. Pumping sstage 1 cxxπprisses a flexible msnbe 22 within a pressure chamber 16.. Flexible member 22 contains a vapor 28. Pumping stage 2 cαmprisses a flexible member 23 within pressure chamber 17. Flexible msnber 23 contains vapor 29. Pumping stage 3 comprises a flexibl member 24 within a pressure chamber 18. Flexible msriber 24 contains a vapor 30. Pumping stage 4 comprises a flexible msnber 25 within a pressur chamber 19. Flexible member 25 contains a vapor 31. Purrping stage 5 ccm- prises a flexible msnber 25 within a pressure chamber 20. Flexible member 26 contains a vapor 32. Puπping stage 6 comprises a flexible msnber 27 within a pressure chamber 21. Flexible member 27 contains a vapor 33. In heat-powered pump system 244, fluid 7 is being pumped frcm a fluid source 127 to an elevated sstorage means 126. The fluid 7 is pumpe through connecting means or pipe 8 and through check valve 9 into purrping stage 1. The fluid 7 then passes through check valve 10 into pumping stag 2. The fluid 7 then passes through check valve 11 into pumping stage 3. The fluid 7 then passes through check valve 12 into pumping ≤rtage 4. ϊhe fluid 7 then passes through check valve 13 into purrping sstage 5. The flui 7 thai passes through check valve 14 into pumping sstage 6. The fluid 7 then passes through check valve 15 and through connecting means or pipe 34 to the elevated storage means 126. The fluid within pipe 34 becomes pressurized fluid 35. Flexible member 22 contains vapor 28 frcm fluid or liquid "A" in container 44. Flexible iαsriber 23 contains vapor 29 from fluid or liqui "B" in container 47. Flexible member 24 contains vapor 30 from fluid or liquid "C" in container 45. Flexible member 25 contains vapor 31 frαn fluid or liquid "D" in container 48. Flexible msnber 26 contains vapor 32 frcm fluid or liquid "E" in container 46. Flexible msnber 27 contains vapor 33 from fluid or liquid "F" in container 49. Pipe 36 with flexible section 136 connects container 44 for fluid or liquid "A" to flexible msnber 22. Pipe 37 connects contai er 45 for fluid or liquid "C" to flexible member 24. Pipe 38 connects container 46 for fluid car liquid "E" to flexible snber 26. Pipe 39 connects contai 47 for fluid or liquid "B" to flexible member 23. Pipe 40 connects contai 48 for fluid or liquid "D" to flexible msriber 25. Pipe 41 connects contai 49 for fluid or liquid "F" to flexible msnber 27. Containers 44, 45, and 46 are in a firsst conduit 42. Containe 47, 48, and 49 are in a ssecαnd conduit 43. Gate control means 132 is connected by cable 50 to container 44. Pumping stages 1, 2, 3, 4, 5, and are enclosed within pump body 131. FIG. 3 is a schsratic representation of heat-pcwered pump syst 244. Fluid 7 is taken frαn fluid source 127 through inlet pipe 70 which i equivalent to the connecting means or pipe 8 and into the multi-stage smal temperature differential heat-powered pump 124. The pressssurized fluid 35 flews frαn the multiple-sϊtage saπall terrperature differential heat-pcwered pump 124 through pipe 34 to elevated sstorage means 126. The other fluid flow shown in FIG. 3 is the flew of fluid to operate the multiple-sϊtage ssmall temperature differential heat-pcwered pump 124. Fluid heating means 123 heats a fluid. The hot fluid flows through a hot fluid pump 69 with a motor speed control 128 and tdrough connecting conduit 70 to input fluid diverting means 147. The input fluid diverting means 147 diverts the hot fluid into the appropriate conduit, either first conduit 42 or sseccnd conduit 43 which extend within the multiple-stage small temperature differential heat-powered pump 124. Th heated fluid will be utilized by the multiple-stage small temperature differential heat-powered pump 124 and will enter the output fluid divert means 146. The previously hot fluid will then be returned by cx__mectir_g conduit 78 to the fluid heating means 123. Fluid cooling means 125 cools a fluid. The cold fluid flows through the cold fluid pump 68 and through connecting conduit 149 to inpu fluid diverting means 147. The input fluid diverting means 147 diverts t cold fluid into the appropriate conduit, either firsst conduit 42 or secon conduit 43 which extend within the multiple-stage small tsrperature differential heat-pcwered pump 124. The cold fluid will be utilized by t multiple-sstage small teπperature differential heat-powered pump 124 and w enter the output fluid diverting means 146. The previously cold fluid wi then be returned by connecting conduit 148 to the fluid cooling means 125 The expandable members disscusssed herein may be flexible bladders, diaphra bellows, or similar flexible msribers in which vaporized fluids may exert pressure in order to expand the area inside the flexible members so that pre≤ssure is exerted againsst the firsst fluid within the contai er within which the flexible msribers reside. The gate control means 132 is connected to the multiple-sstage small tβrrperature differential heat-pcwered pump 124 by wire 139 and wire The gate control means 132 is connected to hot fluid pump 69 by wire 142. The gate control means 132 is connected to cold fluid pump 68 by wire 141. The gate control means 132 is connected to input fluid diverting means 14 by wire 143. The gate control means 132 is connected to output fluid diverting means 146 by wire 144. The pressurized fluid 35 in elevated sstorage means 3126 may be utilized by generating station 153 to handle electrical load 152. The generating sstation 153 is connected to the electrical load 152 by wire 13 The generating station 153 may comprise a low level _yd_aτ_lic-to-mechanic power conversion means 154 and a mechaι_ical-to-electrical power conversio means 155. FIG. 4 is a top view of heat-powered pump system 244. The inp fluid diverting means 147 ccmprisses inlet gate 65. The output fluid dive ing means 146 comprises outlet gate 62. The inlet gate 65 can be placed into basically two positions, inlet gate position 66 and inlet gate positi 67. The outlet gate 62 can be placed into basically two positions, outlet OMPI gate position 63 and outlet gate position 64. When inlet gate 65 is in position 66, outlet gate 62 is in position 63. When inlet gate 65 is in position 67, outlet gate 62 is in position 64. To help explain the fluid path flow in FIG. 4, arrow 171 is utilized to indicate the hot fluid path with outlet gate 62 in position 63 and inlet gate 65 in position 66. Arrow 172 indicates the cold fluid path with outlet gate 62 in position 63 and inlet gate 65 in position 66. Arro 173 is utilized to indicate the hot fluid path with outlet gate 62 in position 64 and inlet gate 65 in position 67. Arrow 174 is utilized to indicate the cold fluid path with outlet gate 62 in position 64 and inlet gate 65 in position 67. With inlet gate 65 in position 66 and outlet gate 62 in possiti 63, the hot fluid will flα* through connecting conduit 79 past motor speed control 128 and hot fluid puπp 69, and through inlet gate 6S in position 6 through conduit section 71, and into first conduit 42 within which are containers 44, 45, and 46. The hot fluid will then flow through conduit section 72 into outlet gate 62 in position 63 and then into connecting conduit 78, which will return the hot fluid to fluid heating means 123. The cold fluid will enter frcm fluid cooling means 125 through connecting conduit 149, passt cold fluid pump 68, and into inlet gate 65 in position 6 The cold fluid will be diverted into ≤second conduit 43 within which are containers 47, 48, and 49. The cold fluid will then enter outlet gate 62 in position-63 and is diverted to connecting conduit 148 to be returned to fluid cooling means 125. When the hot fluid is in firsst conduit 42, the cold fluid is in ssecond conduit 43. With inlet gate 65 in position 67 and outlet gate 62 in positi 64, the hot fluid will flew through connecting conduit 79, passt motor spee control 128 and hot fluid pump 69 and through inlet gate 65 in position 67 and then into second conduit 43 within which are containers 47, 48, and 49 The hot fluid will then flow into outlet gate 62 in position 64, and then into connecting conduit 78 which will return the hot fluid to fluid heatin means 123. The cold fluid will enter frcm fluid cooling means 125 through connecting conduit 149, past cold fluid puπp 68, and into inlet gate 65 in position 67. The cold fluid will be diverted into conduit ssection 71 a then into firsst conduit 42, within which are cont iners 44, 45, and 46. The cold fluid then passes into conduit section 72 and thsi enters outlet gate 62 in position 64 and is diverted to connecting conduit 148 to be CMPI returned to fluid cooling means 125. When the cold fluid is in first con 42, the hot fluid is in second conduit 43. FIG. 5 is a sectional view through section 5-5 of check valve assembly 13 in FIG. 4. Check valve 13 is a check valve assembly between puπping stage 4 and pumping stage 5 and is shown as illustrative of a typ of check valve assembly that may be utilized in the present invention. Check valve assembly 13 cαπprisses an upper hinged msnber 159, a middle hinged msriber 160, and a lower hinged msrber 161. Upper hinged msnber 159 is connected by hinges 162 and 163. Middle hinged msnber 160 is connected by hinges 164 and 165. lower hinged member 161 is connected by hinges 166 and 167. Upper hinged member 159 opens and closes upper opening 168. Middle hinged member 160 opens and closses middle opening 16 Lower hinged member 161 opens and closses lower opening 170. Hinged membe 159, 160, and 161 are of the "sswinging door" variety for simplicity and reliability and, in the open position, a irdnimum of resistance is offered to the flow of fluid. A plurality of hinged members is utilized sso that in the open position the hinged msribers do not extend into the pressure chamber .sufficiently to interfere with the extended bladder. To insure that the hinged members 159, 160, and 161 closse automatically in the absence of a pressure differential across the chamber wall, the pump body 131 may be tilted so that the output end is higher than the input end. A number of hinged mβnbers desired may be utilized in each check valve asse The input fluid diverting means 147 is an input fluid diverti means 147 for any fluid or liquid that may be used. The output water div ing means 148 is an output fluid diverting means 148 for any fluid or liq that may be used. FIG. 5 sshows an example of a check valve assembly 13 which ma be uti ized. Any check valve assembly desirable to the user may also be utilized. FIG. 6 is a partial sectional view at section 6-6 of second conduit 43 in FIG. 4. Second conduit 43 contains container 47 for fluid o liquid "B", container 48 for fluid or liquid "D", and cont iner 49 for fluid or liquid "F". Container 47 may be .supported by support members 189 and 190. Container 48 may be .supported by ssupport msribers 191 and 192. Container 49 may be .supported by ssupport members 193 and 194. Second con duit 43 may be supported fcy conduit support 180 which is secured to the plain or flat land 156. Second conduit 43 holds fluid 196 which may be ho or cold depending on the cycle of the heat-powered pu p systsn 244. FIG. 7 is a partial sectional view at ssectiαn 7-7 of firsst conduit 42 in ETG. 4. First conduit 42 contains cont iner 44 for fluid or liquid "A", container 45 for fluid or liquid "C", and container 46 for fluid or liquid "E". Container 45 for fluid or liquid "C" may be ssupporte by ssupport members 185 and 186. Container 46 for fluid or liquid "E" may be supported by support msribers 187 and 188. Container 44 for fluid or liquid "A" may be .supported by ssupport guide 181 on ssupport rod 183 and ssupport guide 182 on support rod 184. Cable 50 is connected onto containe 44 for use with gate control means 132. The first conduit 42 and the sseccnd conduit 43 are elevated to inssure that the fluid flows downward and empties out of the first conduit and the second conduit 43 when the gate control means 132 causes the gates to change positions. This elevation insures that when the cold fluid puπp 68 has stopped ircroentarily and the gate positions are changed, the cold fluid will drain frαn the conduits prior to the ajplication of hot fluid. This feature insures that there is no residual cold fluid which would have to be heated by the inxxning hot fluid. Firsst conduit 42 holds fluid 196 which may be hot or cold depending on the cycle of the heat- pcwered pump ≤sy≤stem 244. FIG. 8 is an end elevational view of the discharge end of the heat-powered pump system 244. Connecting trough 149 connects the fluid cooling means 125 to the input fluid diverting means 147. Output pipe 34 carries the pressssurized fluid 35 to the elevated storage means 126. Conduit support 179 supports first conduit 42. Conduit support 180 suppor second conduit 43. Connecting conduit 79 leading from fluid heating means 123 is shown carrying hot fluid through hot fluid puπp 69 and into the heat-powered pump system 244. Various pipes 36, 37, 38, 39, 40, and 41 carrying various fluids are sshown. FIG. 9 is an end elevational view of the intake end of heat- powered pump system 244. Ccα ecting conduit 78 returning hot fluid frαn output fluid diverting means 146 to fluid heating means 123 is shown. Conduit section 72 connects to first conduit 42 and to outlet gate 62 (not shown). Puπp body 131 connects to pipes 36, 37, 38, 39, 40, and 41 holdin various vaporized fluids extending to either firsst conduit 42 or second conduit 43. Pipes 36, 37, and 38 extend to first conduit 42. Pipes 39, 40, and 41 extend to second conduit 43. Connecting means or pipe 8 brings fluid 7 from fluid .source 127 (not shown) into the pump body 131. FIG. 10 is a graphic representation shewing the relationsship between the pounds pressure per square inch gauge and the stage utilized with a specific vaporizable fluid and temperature applied thereto for the various stages in the pumping .sequence. As shewn previously in FIG. 2 and FIG. 4, the various purrping sections each contain a pressure chamber within which is a flexible membe Each flexible msnber is connected to a different fluid within a diff rent container in one of two conduits. When the conduit in which a container placed is supplied with hot fluid, the fluid in the container tends to vaporize. The vapor is carried through a pipe into the flexible msnber. The flexible msnber expands as the volume of vaporized fluid increases. H e flexible msnber may expand to εsuch an extent as to virtually fill the pressure chamber within which it is located. The pressure that is appl ed by the expanding flexible member against the fluid that is already in the pressure chamber, forces that fluid against the check valves located en ea side of the pressure chamber. As the pressure within the pressure chamber is greater than the pressure in the next highesst numbered presssure chamber then the fluid within the pressure clamber will be forced through the chec valve into the next highest numbered pressure chamber. As can be sseen clearly in FIG. 2, the present system operates by having the flexible msnber deflated in one charriber, while being inflated in the next chamber, thereby pusshing or purrping the fluid through the pump body 131 toward the elevated sstorage means 126. As an example as seen in FIG. 2, fluids or liquids "A", "C", and "E" are in the firsst conduit 42 and, when that conduit contains cold fluid, the fluids or liquids are condenssed and the flexible msribers in purrping stages 1, 3, and 5 are deflated. Fluids or liquids "B", "D", and "F" in second conduit 43 have hot fluid which is vaporizing thosse fluids o liquids and causing the flexible msribers in pumping stages 2, 4, and 6 to be inflated. The inflated flexible member 23 in pumping stage 2 would force fluid or liquid through check valve 11 into purrping stage 3. The inflated flexible msnber 25 in pumping stage 4 would force fluid or liquid through check valve 13 into pumping s>tage 5. The inflated flexible msnber 27 in pumping stage 6 would force fluid or liquid through check valve 15 into pipe 34 where the pressurized fluid 35 will be carried to the elevate sstorage means 126. In the alternative, if the cold fluid was rsroved frcm the firs conduit 42 and hot fluid placed in firsst conduit 42, while at the ssame tim the hot fluid was removed from second conduit 43 and cold fluid placed therein, the flexible members in the purrping sstages would be in the opposi condition. The flexible msribers in puping sstages 1, 3, and 5 would be inflated and would force fluid or liquid through the next check valve to the following stage. The flexible members in pumping stages 2, 4, and 6 would be deflated and those stages would be filled with fluid or liquid frcm the prior stages. FIG. 10 shows a graphic repressentation of the relationsship between the pressure produced into the various stages. FIG. 10 assumes a situation where the cold fluid tsrperature is 70°F and the hot fluid tsrpe ture is 130°F and assumes the following to be approximately accurate: at 70°F the pounds pressure exerted by "Freαn 113" vapor is—9.7 P.S.I.G.; at 130 β F the pounds pressure exerted by "Freαn 113" vapor is 4 P.S.I.G.; at 70°F the pounds pressure exerted by "Ereon 11" vapor is 0 P.S.I.G.; at 130°F the pounds pre≤sssure exerted by "Freon 11" vapor is 28 P.S.I.G.; at 70°F the pounds pressure exerted by "Ereαn 21" vapor is 10 P.S.I.G.; at 130°F the pounds pressure exerted by "Freon 21" vapor is 50 P.S.I.G.; at 70°F the pounds pressure exerted by "isso butane" vapor is 31 P.S.I.G.; at 130°F the pounds presssure exerted by "isso butane" vapor is 97 P.S.I.G.; at 70°F the pounds pressure exerted by "Freon 12" is 70 P.S.I.G.; at 130°F the pounds pressure exerted by "Freon 12" is 180 P.S.I.G.; at 70°F the pounds presssure exerted by "Freon 502" is 150 P.S.I.G.; and at 130°F the pounds presssure exerted by "Freon 502" is 350 P.S.I.G. Alsso assumed is that the column of fluid in pipe 34 is apprcQ___mately 600' high having a back pressure of app_rαximately 259 P.S.I.G. Therefore, by utilizing the pressent system of multiple-sstages with small temperature differentials, the fluid or liquid is moved from a pressure of 0 P.S.I.G. to the back pressure of the 600' column of fluid, 259 P.S.I.G. The fluid in the lasst pumping sstage is prevented from prsnatur exiting the lasst check valve 15 by the back presssure of the fluid residing in the output pipe 34. This pressure is dependent upon the height in whic the fluid is to be pumped. This back presssure holds the output check valve 15 closed except during the high teπperature part of the cycle when the last stage using "Freon 502" develops a pressure of 350 P.S.I.G. OMPI In FIG. 10, fluid or liquid "A" is graphically shown as bein "Freon 113", fluid or liquid "B" is graphically shown as being "Freon 11 fluid or liquid "C" is graphically sshown as being "Freon 21", fluid or liquid "D" is graphically shown as being "iso butane", fluid or liquid " is graphically shown as being "Freon 12", and fluid or liquid "F" is graphically shown as being "Freon 502". To indicate the operation of the heat-pcwered pup system 24 fluid 7 in connecting means or pipe 8 at ground level would have a press of 14.7 absolute or 0 P.S.I.G. Therefore, the fluid source side of check valve 9 would stand at 0 P.S.I.G. Assuming that in the beginning of the cycle cold fluid flows through firsst conduit 42 and hot fluid flows through sseccnd conduit 43, the cold fluid in firsst conduit 42 would cause the vapor pressure of flui or liquid "A" to be at -9.7 P.S.I.G. Therefore, the fluid 7 would flow through pipe 8 and fill pressure chairber 16. The gate cx_ntrol means 132 would then be activated to change the flow of hot and cold fluid so that hot fluid flowed through firsst conduit 42 and cold fluid flowed through second conduit 43. The fluid αr liquid "A" (Freαn 113") would then rise to a vap presssure of 4 P.S.I.G. T e flexible msnber 23 in pumping stage 2 would b deflated and when the system has been operating, would have a pressssure of 0 P.S.I.G. The fluid within the purrping sstage 1 would then be forced by the high pressure through check valve 10 into purrping sstage 2. As the system continues operation, when the hot and cold fluid change in the conduits, the liquid will be pumped to the next highest numbered stage at a high pressure. When the fluid in sseccnd conduit 43 is hot, fluid or liquid "B" (Freon 11") would have a vapor presssure of 28 P.S.I.G. which would be greater than the cold vapor pressure of 10 P.S.I.G. of the fluid or liquid "C" (Freon 21") in pumping stage 3. When the hot and cold flui in the conduits are again clanged, the fluid in purrping sstage 3 would be .subjected to a vapor pressure of 60 P.S.I.G. and would flow through check valve 12 into purrping stage 4 which has fluid or liquid "D" ("isso butane") at a cold vapor pressure of 31 P.S.I.G. When the hot and cold fluid in the conduits are again changed, the fluid within pumping stage 4 would be subjected to a vapor pressure o 97 P.S.I.G. and will be forced through check valve 13 into pumping stage which has a fluid or liquid "E" ("Freαn 12") at a cold vapor pressure of 70 P.S.I.G. Whan the hot and cold fluid in the conduits are again changed, the fluid within puπping stage 5 will be ssubjected to a vapor pressure of 180 P.S.I.G. and will be forced through check valve 14 and into puπping stage 6, which has fluid or liquid "F" ("Freαn 502") at a cold vapor pressure of 150 P.S.I.G. When the hot and cold fluid in the conduits are changed again, the fluid within puπping stage 6 will be ssubjected to a vapor pressssure of 350 P.S.I.G. and will be forced through check valve 15 and into pipe 34 which has a back presssure of 259 P.S.I.G. FIG. 10 is simply illustrative of the use of the present invention for six specific fluids or liquids at one specific cold tsrpera ture and one .specific hot temperature. The principles of the present invention may be utilized with any number of fluids or liquids as long as the hot vapor pressure of any given sstage is greater than the cold vapor presssure of the next larger numbered sstage. The preceding stage must always reach a higher pressure than the .subsequent stage sso that the flui or liquid will be pushed through the check valve into the subsequent stag As illustrated in FIG. 2 and FIG. 4, fluids or liquids "A", " and "E" are in the ssame firsst conduit 42 and are always s__π ltaneou__ly subjected to either cold or hot fluid. Fluids or liquids "B", "E", and " are also in the ssame second conduit 43 and are always simultaneously subjected to either cold or hot fluid. FIG. 11 is a schematic representation of gate control means 13 Gate control means 132 ccmprisses a cable 50.secured to one of the contain in first conduit 42 and second conduit 43. Container 44 which is in firss conduit 42 is illustrated as was previously shown in FIG. 7. Cable 50 wraps around pully 51 and is anchored in rocker bar at cable anchor 60. Rocker bar 52 rotates about pin 53. A spring 54 is attached to ground anchor 145 from movable bracket 55 , which is movable rocker bar 52. Movable bracket 55 is placed on rocker bar 52 in a manner that the weight of the contai er 44, when empty, is approximately equal the opposing force of the rocker arm mechanism together with the tension spring 54, sspring 54 is in its contracted position. When container is empty, rocker bar 52 is in the lower po≤sitiαn shown in solid lines in FIG. 11. Magnet 56 is adjacent to lower reed switch 57 and upper reed switch 58. Lower reed switch 57 and upper reed switch 58 are magnetic proximity switches. When the magnet 56 is positioned close to the lower reed switch 57, a signed is sent through wire 140 to control logic mechan 59. When the magnet 56 is positioned close to the upper reed switch 58, signal is sent through wire 139 to control logic mechanism 59. When the vaporized fluid or liquid "A" is cooled and returned to the container 44, cont iner 44 will increase in weight due to the cond sation of the vaporized fluid or liquid "A" in cont ner 44. The weight will pull on cable 50 through pully 51 and cable anchor 60, and rocker ba 52 will rise causing magnet 56 to be in proximity with upper reed sswitoh at the time that the container 44 is approximately full. A ssignal is the transmitted through wire 139 to control logic mechanissm 59. Control logi inechanism 59 would then turn off cold fluid pump 68 and hot fluid pump 69 and energize gate motor 137 through wire 143 and gate motor 138 through wi 144. The gate motors would sswitch the gates 62 and 65 to a different position where the gates will rsrain until the control logic mechanisn 59 again receives a signal to sswitch the gate poεsitions. After the gates are switched, the pumps are again .started and cold fluid would be diverted through the conduit which previously had held hot fluid, while hot fluid would be diverted through the conduit that previously held cold fluid. When the hot fluid causes the fluid or liquid "A" in container 44 to vaporize to ssuch an extent that conta er 44 becomes light to such a point that it is virtually empty, the rocker bar 52 will be lowered so tha magnet 56 is in pixsxiiriity with lcwer reed sswitch 57 causing a signal to pass via wire 140 to control logic mechanism 59. The control logic mechan 59 would then again pass signals to the gate motors and to the pumps in order to change the cycle of the pumps operation. Wire 143 is connected between control logic mechanissm 59 and gate motor 137. Wire 144 is connected between control logic mechanism 59 and gate motor 138. Wire 141 is connected between control logic mechanissm 59 and cold fluid pump 68. Wire 142 is connected between control logic mechanissm 59 and hot fluid pup 69. Gate control means 132 is illustrative of one method of deter¬ mining when the vaporizable fluid in a container has virtually completely vaporized or has been virtually completely condenssed back within the con¬ tainer. Other methods of detei ning that condition are within the ssccpe the present invention and can be utilized herein. f OMPI * FIG. 12 is a sectional view at inlet gate 65. Inlet gate 62 works in ssimilar fashion to inlet gate 65 and has been previously explaine in FIG. 4. Inlet gate 65 has a gate pivoting sshaft 197 which, upon direct by the gate control means 132, changes inlet gate 65 to either position 66 or position 67. Position 66 is shown in FIG. 12 in solid lines. Position 67 is εshcwn in FIG. 12 in broken lines. Outlet gate 62 has a gate pivoting shaft 248 which is similar the gate pivoting shaft 197 of inlet gate 65. FIG. 13 is a sectional view of input fluid diverting means 147 taken at section 13-13 of FIG. 12. Gate motor 137 is shown in position to turn gate pivoting shaft 197 in order to place inlet gate 65 in either inlet position 66 or inlet position 67. Wire 143 connects gate motor 137 to the α_aτtrol logic mechaiiissm 59 of gate control means 132. FIG. 13 indicates that FIG. 12 can alsso be noted as being a sectional view at section 12-12 of FIG. 13. FIG. 14 is a partial iscmetric view of heat collector conduit of fluid heating means 123. Conduit 61 has a top gl zing 75 which is translucent to allow light to enter the conduit 61. FIG. 15 is a sectional view of heat collector conduit 61 of fluid heating means 123 taken at .section 15-15 of FIG. 14. Conduit 61 is formed by treated wood 73 and is lined with styrofoam or other ssheet-type insulation 74. The insside .surface liner 76 of ccciduit 61 which is expossed to fluid may be a ssheet of black polyethylene, other plastic film, or sane other type of lining material. The top glazing 75 may be a layer of corrogated translucent fiberglass-type glazing. Top glazing 75 provides visible light t__ans_mission and infrared blockage capabilities necesssary for efficient solar heating of the fluid within conduit 61. Conduit 61 is part of a contin.-ous loop system where fluid is circulated and raised in temperature as it passes through the systsn. The fluid heating means 123 may be a so ar heating conduit, such as conduit 61 which extends for any desired distance in order to heat a desired volume o fluid to its desired temperature. However, the fluid heating means may be any desired or desirable method utilizing any dessired configuration of hea ing fluid or other liquids to be utilized in the heat-powered pump system 244. Conduit 61 holds heated fluid 195. ■ I ΕE O PI • 1/ Ww1iPp FIG. 16 is a cross-sectional view of cooling conduit 151 whic may be utilized as fluid cooling means 125. Any convenient or inexpensiv fluid cooling means desired or available may be utilized with the present invention. FIG. 1 illustrates a river utilized as fluid cooling means 12 a source for the cold fluid. In areas where there is no ssuch convenient fluid source, another method of cooling fluid may be util zed, ssuch as evaporative conduit-type cooling conduit 151. Conduit 151 has a frame 119 and a lilning 120 which waterproof cooling conduit 151 in the ssame manner than conduit line 76 waterproofed conduit 61. Differing from conduit 61, the insulation is not utilized between the frame 119 and the ning 120. Fluid 122 flows within the cooling conduit 151. Above the cooling conduit 151 is a slanted roof 121 which is opaque and is dessigned to shield the fluid from the ssuns rays. Cpaque roof 121 is ssupported by high support bracket 202 and lower ssupport bracket 203. A plurality of brackets 202 and 203 may be required depending upon the total length of conduit 151. Support brackets 202 and 203 are designed so that air may flew below the roof 121 to promote evaporation frαn fluid 122 in the cooling conduit 151. Many other types of cooling means may be utilized wi the present invention which may be much more desirable and convenient than cooling conduit 151. FIG. 17 is a schematic representation of heat-powered generati system 245. The heat-pcwered generating system 245 operates on the basic principles herein utilizing small temperature differential multiple sstages These principles are utilized to form a heat-pcwered generating system 245 Fluid heating means 123 provides fluid through hot fluid pu p with motor sspeed control 150 through connecting conduit 79 to the input fluid diverting means 205. The input fluid diverting means 205 diverts th hot fluid to either the firsst multiple-sstage .small temperature differentia heat-powered pump 134 or the second multiple sstage small teπperature differential heat-powered pump 135. The hot fluid is then directed into t output fluid diverting means 204 where it is diverted to connecting condui 78 and back to the fluid heating means 123. Fluid is cooled in the fluid cooling means 125, then passes through cold fluid pump 82, and into the input fluid diverting means 205. The cold fluid passes frcm input water diverting means 205 into either the OMPI the first multiple-sstage small temperature differential heat-pcwered puπp 134 or the second multiple-stage small temperature differential heat-power puπp 135. The cold fluid then passes into the output fluid diverting mean 204. The cold fluid is diverted through connecting conduit 148 back to th fluid cooling means 125. The fluid heating means 123 and the fluid cooling means 125 simply provide hot and cold fluid to be utilized by the multiple stages within the heat-pcwered generating sy≤stem 245. The heat-powered generatin system 245 has a working fluid ssysstsn which is primed and which theoretica will not require the addition of any further fluid. This is the fluid whi passes through the first raultiple-sstage small tsrperature differential heat-powered pump 134, through connector 110, and through the sseccnd multiple-sstage ssmall temperature differential heat-powered pu p 3135, throu connector 111, through inlet pipe 112 to the hydrau^c-to-mechanical power conversion means 115. From the hydrau3_ic>-to-mechanical power converssion means 13L5, the fluid passes through outlet pipe 97 to pass back to first multiple-sstage small temperature differential heat-pcwered pu p 134 via connector 100 αr to the sseccnd multiple-sstage small tsπperature differenti heat-pcwered puπp 135 via connector 101. A gate control means 206 is similar to gate control means 132 may be utilized to control gates within the input fluid diverting means 20 and the output fluid diverting means 204. Control wire 209 extends frcm gate control means 206 to input water diverting means 205. Control wire 2 extends between gate control means 206 and hot fluid pump 81. Control wir 212 extends between gate control means 206 and cold fluid pump 82. (_ontro wire 210 extends frcm gate control means 206 to output fluid diverting mea 204. Control wires 207 and 208 extend frαn the sseccnd multiple-stage smal tsrrperature differential heat-powered puπp 135 to the gate control means 2 The gate control means 206 may be operated frαn any stage within either the firsst multiple-sstage small temperature differential heat pcwered puπp 134 or the sseccnd multiple-sstage small temperature differenti heat-pcwered puπp 135. Connector 99 is connected from inlet pipe 112 to inlet hydraul accu u later 113. Connector 98 extends frαn outlet pipe 97 to outlet lydraulic accumulator 117. The b-ydrau άc-to-mechaπdcal power converssion means 115 drives a ιrκ_cla_ ical-to-electrical power conversion means 116 which is connected by wire 129 to electrical load 133. OMPI FIG. 18 is a .schematically represented plan view of heat- po-ered generating system 245. Within heat-pcwered generating system 245 are purrping sstages 213, 214, and 215 which form the firsst multiple-sstage small tsrperature differential heat-powered pump 134, and pumping stages 216, 217, and 218 which form the second multiple-stage small tsrperature differential heat-pcwered pump 135. Pumping stage 213 has a pressure chamber 219 within which is expandable msnber 225. Pumping stage 214 has a pressure chamber 220 within which is an expandable msnber 226. Pumping stage 215 has a pressu chamber 221 within which is an expandable member 227. Purrping stage 216 has a pressure chamber 222 within which is an expandable member 228. Purrping stage 217 has a pressure chamber 223 within which is an expandabl msnber 229. Pumping sstage 218 las a pressure chamber 224 within which is an expandable inember 230. Expandable msnber 225 contains vapor 231. Expandable msriber 226 contains vapor 232. Expandable msriber 227 cont ins vapor 233. Expan able member 228 contains vapor 234. Expandable member 229 contains vapor 235. Expandable member 230 contains vapor 236. Conduit 89 holds container 92 for fluid car liquid 1, container 91 for fluid or liquid 2, and container 90 for fluid or liquid 3. Condui 93 holds container 96 for fluid αr liquid 1, container 95 for fluid or liquid 2, and container 94 for fluid car liquid 3. The vapor 231 in expandable member 225 passses through pipe 237 from container 92. The vapor 232 in expandable member 226 passes through pipe 241 from container 95. The vapor 233 in expandable member 227 passes through pipe 239 frcm container 90. The vapor 234 in expandable msnber 22 passes through pipe 240 from container 96. The vapor 235 in expandable msnber 229 passes through pipe 238 frαn container 91. The vapor 236 in expandable msriber 230 passes through pipe 242 from container 94. Pipe 240 has a flexible portion 243 which allows utilization of a form of gate control means 206. In the operation of the heat-powered generating system 245, cold fluid enters through connecting conduit 149 from fluid cooling means 125. Hot fluid enters frcm fluid heating means 123 through connecting corrluit 79. Inlet gate 93 is similar to inlet gate 65. Inlet gate 93 has an inlet gate position 84 and an inlet gate position 85. Outlet gate 86 is similar to outlet gate 62. Outlet gate 86 has an outlet gate position and an outlet gate position 88. Depending upon which position inlet gate 83 and outlet gate 86 are in, either hot fluid or cold fluid will flow in conduits 89 and 93. Whenever one of those conduits has hot fluid, the oth will have cold fluid. Arrow 175 indicates the hot fluid path with the gates in positions 84 and 87. Arrow 176 indicates the cold fluid path with the ga in positions 84 and 87. Arrow 177 indicates the hot fluid path with the gates in positions 85 and 88. Arrow 178 indicates the cold fluid path with the gates in positions 85 and 88. As shown by arrows 175 and 178, hot fluid and cold fluid may flow through conduit sections 77 and 80 durin their journey through conduits 89 and 93. FIG. 18 is taken at a position in time when hot fluid had been flcwing through conduit 89 and cold fluid had been flowing through conduit 93. Fluid or liquid 1 in container 92 has vaporized and vapor 231 has enlarged expandable member 225. Fluid or .Liquid 3 in contai er 90 has vaporized and vapor 233 has enlarged expandable member 227. Fluid αr liqu 2 in container 91 has vaporized and vapor 235 has enlarged expandable memb 229. Fluid αr liquid 1 in container 96 has cooled and vapor 235 las condensed reducing the ssize of expandable msriber 228. Fluid or liquid 2 i container 95 has cooled and vapor 232 has condensed reducing the size of expandable member 226. Fluid or liquid 3 in container 94 has cooled and vapor 236 las condensed reducing the ssize of expandable msriber 230. The pressssure in pressure chamber 219 expands greater than the pressure in pressure chamber 220, thereby opening check valve 103 which is between puπping sstages 213 and 214. The pressure in pumping sstage 214 does not exceed the presssure within puπping sstage 215, therefore, check valve 104 between puπping sstages 214 and 215 remains closed. The pressure in pumping stage 215 exceeds the pressure in cont iner 110, thereby openin check valve 105 which is between pumping sstage 215 and connector 1510. Fluid then flows through cont iner 3_10 and through inlet pipe 112 to the hyd_aιιlic-t_c-_nechanical power conversion means 115. Frcm the hydraulic-to mechanical power converssion means 115, the fluid flews through outlet pipe 97 and towards puπping stage 216 which has a lower pressssure, thereby the pressure frαn the oncoming fluid is greater than the lower pressure within the purrping sstage 216. Therefore, this opens the check valve 106 between the pumping stage 101 and pumping stage 216. The pressure within pumping stage 216 is less than the pressure within pumping stage 217, thereby check valve 107 which is between purrping stages 216 and 217 does not open. The pressure within purrping stage 217 is greater than the pressure witiiin purrping stage 218, thereby check valve 108 which is betwe pumping stages 217 and 218 is open, allowing the fluid to flow frcm purrpi stage 217 into purrping stage 218. The pressure in pumping stage 218 is less than the fluid pressure within connector 111, thereby the check valv 109 which is between pumping stage 218 and connector 111 is closed. When expandable inember 228 has contracted to its desired sπal amount, the gate control means 206 will automatically causse the gates to switch to positions 85 and 88. This switch in gate positions will cause hot fluid to flow through conduit 93 and cold fluid to flow through condu 89. This change in tsrperature will cause the expanded expandable msriber to contract and the contracted expandable members to expand.- This causses the check valve 105 to close and check valve 109 to open allowing for continuous flow of fluid through connector 111 to inlet pipe 112 and utilizes the fluid that was stored within pumping sstage 218, while the fluid that was previously stored within purrping stage 215 was being pumpe through inlet connector 110 through inlet pipe 112. During the transition period when the heat exchangers or containers 90, 91, 92, 94, 95, and 96 are changing in temperature, the input to the hydraulic-to-meclanical power conversion means 115 could mαnentarily drop. To smooth out presssure fluctuation at the input and th output of the turbine or hyάraulio-tao-mechanical power conversion means 1 hydraulic accumulator 113 and hydraulic accumulator 117 are utilized. Th accumulators 113 and 117 may be tanks filled with cαrpressed gas and a rubber bladder filled with fluid in cαrmunicatiαn with pipe 1512. The acα ._ators 113 and 3_17 significantly reduce any momentary pressure drop and, thereby reduce the possibility of speed fluctuations in the hydraulic to-^rechanical power conversion means 115. Other methods of reducing the momentary pressure drop or reducing speed variations may be used, if desir The accumulator 113 acts to smooth the inlet pressure to the turbine or hydraulic-to-mechanical power conversion means 115. Inlet hydraulic accumulator 113 has a flexible msnber 15L4. Outlet hydraulic accumulator 117 has a flexible msnber 118. Very briefly, the heat-powered generating system 245 provides a steady flow of water to the turbine or hydraulic-to-meclanical power converssion means 115 by providing a bursst of fluid frαn the first multipl stage small tsrperature differential heat-pcwered puπp 3L34, followed by a bursst frαn the ssecond irailtiple-stage small teπperature differential heat- powered puπp 135, and so forth. Extending frαn turbine 115 is a mechanica to-electrical power conversion means 116 which is connected to an electric load 1533 via connecting wire 129. FIG. 19 is a graphical representation sshowing the relationship between the pounds pressssure per square inch gauge and the sstage utilized with the specific vaporizable fluid and temperature applied thereto for various stages in the pumping sequences within the heat-powered generating systsn 245. FIG. 19 is illustrative of either the firsst multiple-stage sma teπperature differential heat-powered puπp 134 or the sseccnd multiple-stag small tsπperature differential heat-pcwered pump 135. However, remember that when the hot fluid flows through one of the conduits 89 or 93, that cold fluid fows through the other conduit, thereby causing the oppossite condition in the various similar stages. For the purposes of FIG. 19, the cold fluid or water tsrperature is ass≤sumed to be 70°F and the hot fluid or water temperature.is assumed to be 130 β F. For example, utilizing fluid αr liquid 1 as "Freon 12", -when puπping stage 213 is at the hot vapor pressure of 180 P.S.I.G., the puπpin sstage 216 wild, be at the cold vapor pressure of 70 P.S.I.G. Utilizing "Freon 115" as fluid or liquid 2, when the puπping stage 214 is at the col vapor pressure of 3U.0 P.S.I.G., the pumping stage 217 would be at the hot vapor pressure of 275 P.S.I.G. Utilizing "Freon 13B1" as fluid or liquid when the puπping sstage 215 is at the hot vapor presssure of 429 P.S.I.G., the purrping stage 218 would be at the cold vapor presssure of 197 P.S.I.G. The principles of these pumping stages are the same principles as previously illustrated and discussed in FIG. 10. A key fact of importa is that the hot vapor pressure of a stage usst exceed the cold vapor press of the next stage in order to obtain flow through the check valves between the stages. Since the back pressure to the power conversion means 115 is equal to the input pressure on either puπping stag 213 or pumping sstage 216, whichever has an open check valve and the lower pressure, then tee back pressure of the turbine or lydraulic-to-mechanical power conversion means 3L3L5 would be equal approximately to 70 P.S.I.G. ' The turbine 115 has an input pressure of approximately 429 P.S.I.G. and, therefore, would have a pressure head of approximately 359 P.S.I.G. Many other fluids or liquids may be utilized in the same αr a different plurality of stages which are of similar nature and which conform to the criteria of the present invention. FIG. 20 is a sectional view of check valve 13 at .section 20-20 of FIG. 5. Upper hinged msnber 159 opens and closes upper opening 168. Middle hinged member 160 opens and closses middle opening 169. lower hinged member 161 opens and closes lower opening 170. Check valves 102, 103, 104, 105, 106, 107, 108, and 109 are utilized in the heat-pcwered generating systsn 245 and may be of ssimilar nature to the check valve 113 and other check valves within pu p body 131 and are utilized in the same way. A plurality of hinged members may be utilized along with any other desired type of check valves to satisfy the desire of the user. The present invention can also be utilized as a multiple-stage pump cατ ressor for utilization in the heating and cooling system which coπprises separate hot and cold containers connected to flexible members witiiin pressure chambers in each of a plurality of pumping stages. FIG. 21 is a schematic drawing of an individual hot container and cold container utilized to heat arai cool a second fluid. The cold container 269 and the hot conta ner 268 provide gas within flexible member 255. Shown in FIG. 21 is an entire pumping mechanissm 249 which includes the pumping stage 250 and the vapor pressure control means 251. The purrping stage 250 has a body 252 containing a chamber 455 within which is a flexible msnber 255. Check valve 253 allows movement of fluid into the chamber 455. Check valve 254 allows movement out of the chamber 455. The vapor pressure control means 251 is controlled by a vapor pressure control sensing means. In FIG. 21, the vapor presssure control .sensing means c rprisses a magnet 256 which is secured onto flexible member 255, and magnetic proximity switches 257 and 258. Upper magnetic proximity sswitch 257 serves to indicat that the flexible msnber 255 is enlarged as the magnet 256 nears the upper magnetic proximity sswitch 257. When the flexible member 255 is deflated, the magnet 256 will ns_ar the lower magnetic proximity sswitch 258 indicating the deflated state of the flexible member 255. When the flexible msriber 255 is inflated, a signal will pass throug the upper magnetic proximity sswitch 257 through control wire 259 to the valve c rmand generator 260 within vapor pressure control means 251. When the flexible member 255 is deflated, a signal will pass through the lower magnetic proximity switch 258 through control wire 265 to the valve command generator 260 within vapor pressure control means 251. The valve command generator 260 wii, depending on the • appropriate situation, open and close cold control valve 261 and hot control valve 262. Vapor will flow from the hot container 268 i_hrough the hot vapor line 264, through hot control valve 262, and through flexible member inflation pipe 266 in a vapor state to enlarge flexible member 255. When the flexible msriber 255 reaches an inflated positio to the extent that the upper magnetic proximity sswitch 257 is activated by the magnet 256 and a signal is sent to the valve cαrmand generator 260 through control wire 259, the hot control valve 262 will close and the cold control valve 261 will open, allowing the high pressure vapor within the flexible member 255 to pass through flexible member inflation pipe 266 and through cold control valve 261, through cold fluid line 263, and into cold container 267, where it is condensed to a liquid. In order to keep a proper fluid balance in cold container 267 and hot container 268, a condensate purrp ssucticn line 273 is connected between cold container 267 and condensate purrp 271. A condensate purrp disscbarge line 274 is connected between condensate purrp 271 and hot container 268. The condensate puπp 271 may be controlled by a control wire 272 which may indicate the level of fluid within cold cont er 267. Cold container 267 may have a flow indicator 269 indicating flow throxjgh the cold container 267. Hot container 268 may have a flow indicator 270 which indicates flow through the hot container 268. FIG. 22 is a schematic diagram of a ssolar collector utilized for heating a second fluid and a cold grour_d container utilized for cooling a second fluid. - FIG. 22 sshows puπping stages and controls 275 vϊhich may be a ssingle stage and control as shown in FIG. 21, or a plurality of sstages and controls. Solar collector 276 acts as the hot container 268 of FIG. 21, and cold cont ner 277 acts as the cold container 267 of FIG. 21. Condensate purrp 278 acts the sane as condensate pup 271 of FIG. 21. - * £UREΛ OMPI - " Piping section 279 connects the purrping stages and controls 27 to the cold ground container 277. The piping section 280 connects the ss collector 276 to the pumping stages and controls 275. The piping sectio connects the cold ground container 277 to the condensate pump 278. The piping section 282 connects the condensate puπp 278 to the solar collect 276. The cold ground container 277 is located within the ground 283. T solar collector 276 is located above'the ground 283 utilizing the ssolar to act as the hot container. FIG. 23 is a schematic diagram of an evaporative cooler 285 and a hot ground container 286 utilized for heating and cooling a second fluid. FIG. 23 shows pumping sstages and controls 284 which may be a single stage and control as shown in FIG or a plurality of stages and controls. An evaporative ooler 285 is above ground 292 and is connected puπping stages and controls 284 by piping section 289. The hot ground container 286 is connected by piping section 288 to purrping stages and controls 284. Condensate pup 287 is connected by piping section 290 to hot ground container 286 and by piping ssection 291 to evaporative cooler In FIG. 22, the container within the ground provides the cold temperature. In FIG. 23, the container within the ground provides the h temperature. These temperatures are relative temperatures which are dependent upon the fluid being utilized. FIG. 24 is a schematic diagram of a plurality of expandable ms being supplied with vapor frαn a single vapor pressure control means. Va pressure control means 305 is shown supplying flexible members 295, 296, 297 of pumping stage 293. Pumping stage 293 has a body 294 containing a chamber 456. Check valve 298 allows flow of a fluid into chamber 456. valve 299 allows flow of a fluid out of chamber 456. A magnet 300 is shown secured to flexible member 295 which act part of the vapor-pressure control sensing means to control the vapor pr control means 305. When the flexible member 295 is inflated, the upper proximity switch 301 will send a signal through control wire 303 to the pressure control means 305. When the flexible member 295 is deflated, a will be sent through lower magnetic proximity switch 302 through control 457 to the vapor pressure control means 305. 2he vapor pressure control sensing means may be any type of vapor pressure control sensing means. OMPI The magnet and the magnetic proximity switch concept shown herei may be utilized, along with any other type of control .sensing means. When there is a plurality of flexible members controlled by one vapor pressure control means as shown in FIG. 24, the magnet could be .secured to any of t flexible members. The vapor pressure control means 305 controls the flexi members 295, 296, and 297 through piping 304. FIG. 25 is a schematic diagram of a plurality of expandable members, each expandable member being supplied frαn a different vapor press control means. Pumping stage 306 is shown with body 307 comprising a cham 458. Within chamber 458 are flexible members 308, 309, and 310. Check va 311 allows flew of a fluid into chamber 458. Check valve 312 allows flow a fluid out of chamber 458. Flexible meπber 308 is supplied by vapor pres control means 320 through piping section 317. Flexible member 309 is supp by vapor pressure control means 321 through piping .section 318. Flexible member 310 is supplied by vapor pressure control means 322 through piping section 319. Magnet 313.secured to flexible member 308 forms part of the vapo pressure control .sensing means, along with upper magnetic proximity sswitc 314 and lower magnetic prαxJLmity switch 315, similar to those previously discussed. Upper magnetic proximity sswitch 314 provides an input signal through control wire 316 to the vapor pressure control means 320, 321, an 322. Lower magnetic proximity switch 315 provides a signal through contr wire 459 to the vapor pressure control means 320, 321, and 322. FIG. 26 is a schematic diagram of a solar-powered air cooling system 323. The solar-powered air cooling system 323 is shown for use in providing cooling within building 341. Compressor 324 is shown having fo stages, compressor stages 325, 326, 327, and 328. Compressssor stage 325 contai s flexible member 334. Compressor stage 326 contains flexible mem 335. Compressor stage 327 contains flexible member 336. Cαipressor stag 328 contains flexible member 337. Check valve 329 is at the input of cαrpressor sstage 325. Check valve 330 is between compressor stages 325 a 326. Check valve 331 is between compressor stages 326 and 327. Check va 332 is between compressor sstages 327 and 328. Check valve 333 is at the output of compressor stage 328. Solar collector 344 is sshown coπprising hot containers 346, 347, 348, and 349 and condenser coil 345. Cold containers 355, 356, 357, and are contained below ground 350. Evaporator coil 340 is located within th b ui l ding 341. /* E The solar-pcwered air cooling system 323 basically operates as does the system shown in FIG. 22, based en the principles previously dis¬ cussed in the specification. Features, ssuch as the vapor pressure control sensing means and other features previously disscusssed, are not sshown within FIG..26 in order to simplify the drawings. The temperature-pressure-fluid relationships within ccmpresssor 324 are detailed wit_hin FIG. 27. The output frαn compressor 324 passes through piping section 339 and through the ccndensser coil 345 within solar collector 344. The output then passes through receiver 343 and pressure operated expansion valve 342, through the evaporator coil 340 a«i back through piping section 338 at a lowered pressure into the input of the ccπrpressor 324. Flexible msnber 334 is .supplied from cold container 355 through piping section 359 and cold control valve 460. Flexible member 334 is also supplied frαn hot container 349 through piping .section 371 and hot control valve 464. Condensate puπp 351 is connected to cold container 355 by piping section 363 and to hot container 349 ty piping section 367. Flexible member 335 is supplied frcm cold container 356 through piping section 360 and cold control valve 461. Flexible member 335 is also supplied frcm hot container 348 through piping section 372 and hot control valve 465. Condensate pump 352 is connected to cold container 356 by piping ssection 364 and to hot container 348 by piping section 368. Flexible msnber 336 is .supplied fr n cold container 357 through piping section 361 and cold control valve 462. Flexible member 336 is also supplied frαn hot container 347 through piping ssection 373 and hot control valve 466. Condensate pump 353 is conriected to cold container 357 by piping section 365 and to hot container 347 by piping ssection 369. Flexible inember 337 is supplied from cold container 358 through piping ssection 362 and cold control valve 463. Flexible member 337 is also supplied from hot container 346 through piping ssection 374 and hot control valve 467. Condensate puπp 354 is connected to cold container 358 by piping ser-Hn 366 and to hot container 346 by piping ssection 370. In the solar-pcwered air cooling system 323, a four-stage pump is shown basically replacing a mechanical c rpressor. The high temperature for the hot containers may be derived frcm any type of solar coliector 344. The ssolar collector 344 may be an insulated vat covered by glazing and filled with water acting as a heat exchange med um. Immersed within the water would be the four hot containers 346, 347, 348, and 349. ^ E OMPI The cold containers 355, 356, 357, and 358 are placed below ground 350 so as to dissipate heat to the surrounding earth and maintain a basically constant cold teπperature relative to the tsrperature of the solar collector. For purposes of illustration, the cold temperature is assumed to be 70°F and the hot temperature is assumed to be 130°F. The result of the cαrpressssor-type sir- coraiitioning process is the production of a relatively high and lew tsrperature at the condenser coil and evaporator coil, respectively. The low teπperature of the evaporator coil 340 is utilized for cooling. : In the present system, the high temperature of the condenser coil may be utilized to be fed back into the solar collector 344 to aid in heating the hot containers 346, 347, 348, and 349. The high tsrperature of the condensser coil 345 would normally be discharged into the atmosphere as waste heat; therefore, the pressent system saves and utilizes that energy in a regenerating process. By utilizing the regenerating prccesss, the size of the ssolar collector 344 may be reduced. In the present ssysstem when utilizing the fluids designated in FIG. 27, the high teπperature gas flowing through piping section 339 out of compressor 324 would flow through a heat exchanger in the solar collector, raising the terrperature within the solar collector and cooling the gas. The condensed fluid would be collected in receiver 343 and applied to a presssure- operated expansion valve 342 and would enter the evaporator coil 340 where the cooling effect is achieved as in a conventional air conditioning system. The pressure-operated expansion valve 342 may be adjusted to provide an evaporator coil pressure of approximately +7 P.S.I.G. The gas exiting the evaporator coil 340 at this pressure will flow back to the input of cαrpressor 324 and ater the firsst compressor stage 325 through the check valve 329. The firsst cαrpressor stage 325 has a flexible msriber 334 with an internal vapor pressure of approximately 0 P.S.I.G. causing the flexible member 334 to contract. The puπping cycle then operates as previously discussed in the specification. FIG. 27 is a graphic representation showing the relationship between the pounds pressure per ssquare inch gauge and the .<?tage utilized with a specif vα uj.izable liquid -___d terrperature applied thereto for the various ssta y w .___ the purrping sequence of the solar-powered air cooling systsn of FIG. 26. The first fluid purrped through the cαrpressor is assumed to be isso-butane, for thi example, but may be any appropriate fluid with a corresponding plurality of second fluids which follow the principles taught herein. — FIG. 27 assumes the situation where the cold temperature is 70°F and the hot tsrperature is 130°F and assumes the following to be approxima accurate: at 70°F the pounds pressure exerted by "FRECN 11" is 0 P.S.I. at 130°F the pounds pressure exerted by "FRECN 11" is 28 P.S.I.G.; at 70°F the pounds pressure exerted by "FRECN 21" is 10 P.S.I.G.; at 130°F the pou pressure exerted by "FRECN 21" is 50 P.S.I.G.; at 70°F the pounds pressure exerted by "ISO BUTANE" is 31 P.S.I.G,; at 130°F the pounds pressure exert by "ISO BUTANE" is 97 P.S.I.G.; and at 70°F the pounds pressure exerted by "FRECN 12" is 70 P.S.I.G.; at 130°F the pounds pressure exerted by "FRECN is 180 P.S.I.G. The action of the cαpresssor 324 is similar to the puπpin action previously discussed herein and shewn and disscusssed, for example, i FIGS. 10 and 19. FIG. 28 is a schematic diagram of an ea__thr-heat-powered air heati system 375. The earthrheat-powered air heating system 375 utilizes the hea of the earth assumed to be 60°F to heat the hot containers 397, 398, 399,40 402, and 403. The cold containers 415, 416, 417, 418, 419, 420, and 421 ar located in an evaporative cooler 422 in which their heat is radiated to the environment and a cold container tsrperature of approximately 40°F is assum If the air temperature drops, the efficiency of the system actually increas since the temperature differential between the hot and cold containers increases. Cαrpressαr 376 cαrprisses compressor stages 377, 378, 379, 380, 38 382, and 383. Check valve 384 is at the input of cαrpressor stage 377. Ch valve 385 is between compressor stages 377 and 378. Check valve 386 is between cαrpressαr sstages 378 and 379. Check valve 387 is between compress stages 379 and 380. Check valve 388 is between ccπpressαr stages 380 and 3 Check valve 389 is between cαπrpresssor stages 381 and 382. Check valve 390 between cαrpressαr stages 382 and 383. Check valve 391 is at the output of compressor sstage 383. The output of cαπrpre≤ssor 376 flcjws through piping section 429, through condenser coil 394 and receiver 395, and through pipin section 430 and into evaporator coil 424 within evaporative cooler 422, and back through piping section 428 and into the input of cαπpresssor 376. Flexible irember 481 is supplied frαn cold container 415 through piping section 444 and cold control valve 392. Flexible msnber 481 is also supplied from hot container 403 through piping ssection 437 and hot control valve 474. Condensate pump 408 is connected to cold container 415 by pipin section 451 and to hot container 403 by piping section 404. Flexible member 482 is supplied frαn cold container 416 through piping section 443 and cold control valve 468. Flex ble msnber 482 is als supplied from hot container 402 through piping section 436 and hot contro valve 475. Condensate pump 409 is connected to cold container 416 by pip section 450 and to hot container 402 by piping ssection 405. Flexible member 483 is supplied from cold container 417 through piping section 442 and cold control-valve 469. Fl xible member 483 is al supplied from hot container 401 through piping section 435 and hot contro valve 476. Condensate pump 410 is connected to cold cont iner 417 by pip section 449 and to hot container 401 by piping section 406. Flexible msnber 484 is strpplied frcm cold container 418 through piping ssection 441 and cold control valve 470. Flexible member 484 is al .supplied frαn hot container 400 t±rough piping ssection 434 and hot contro valve 477. Condensate pump 4311 is connected to cold container 418 by pip section 448 and to hot container 400 by piping ssection 407. Flexible member 485 is supplied frαn cold container 419 through piping .section 440 and cold control valve 471. Flexible member 485 is al supplied from, hot container .399 through piping ssection 433 and hot contro valve 478. Condensate pump 412 is connected to cold container 419 by pip section 447 and to hot container 399 by piping ssection 452. Flexible inember 486 is supplied frcm cold container 420 through piping ssection 439 and cold control valve 472. Fl xible member 486 is al supplied frcm hot cont ner 398 through piping ssection 432 and hot contro valve 479. Condensate pump 413 is connected to cold cont ner 420 by pip section 446 and to hot container 398 by piping ssection 453. Flexible msnber 487 is supplied frαn cold container 421 through piping section 438 and cold control valve 473. Flexible msnber 487 is al supplied from hot cont iner 397 through piping ssection 431 and hot contro valve 480. Condensate pump 414 is connected to cold conta er 421 by pip section 445 and to hot container 397 by piping ssection 454. The ressult of the cαmpresssor-type heating process is the produc of a relatively high and ow teπperature at the condenser coil and evapor coil respectively. The high teπperature of the condenser coil 394 is utilized for heating. In the present system, the low tsrperature of the evaporator coil 424 may be utilized to be fed back into the evaporative c 422 to aid in cooling the cold containers 415, 416, 417, 418, 419, 420, a The low tsrperature of the evaporator coil 424 would normall discharged into the atmosphere as waste cooling; therefore, the presen saves and utilizes that energy in a regenerating process. By utilizin regenerating process, the efficiency of the evaporative cooler 422 may increassed. By use of the regenerating process, the evaporator coil 42 utilized to aid in cooling the evaporative cooler 422. If the evapora cooler 422 utilizes a water bath, " then the water bath tsrperature can reduced by the evaporator coil 424, increasing the efficiency of the evaporative cooler 422. TO inssure that the teπperature of the evaporator coil 424 is always below the water teπperature within the evaporative cooler 422, differential teπperature expansion valve 423 is utilized. Temperature sensor 425 may be placed within the evaporative cooler 422 and connect by control wire 426 to the differential temperature expansion valve 42 A control wire 427 may be alsso connected frαn the output piping sectio • the evaporator coil 424 to the differential temperature expansion valv The differential teπperature expansion valve 423 is operative, when re ing the proper signal, to meter the gas or.fluid flowing therethrough t a constant temperature below the teπperature within the evaporative co 422. By utilizing this process, the regenerating portion of the systs always rsnoves heat from the evaporative cooler 422 and lowers its temp ture. The gas or fluid flowing back to the input of the carpressor is always above the pressure of the cold container 415 of the first compre stage 377, insuring entrance of the gas or fluid into the first ccπprεss stage 377. The condensser coil 394 is utilized for heat within building 3 The hot containers 397, 398, 399, 400, 401, 402, and 403 are located be ground 396. All details regarding the total syεstem for providing the eart heat-pcwered air heat g sysstsn 375 have not been sshσwn for simplicity poses. She key features that have been illustrated are that a _&xltiple stage puπp, as discussed herein, has been utilized instead of a mechan cαrpressor and that wasste cold teπperature has been utilized to increass the efficiency of the earth-hβat-powered air heating system 375 in a re erating process. -S JRE -OMPI FIG. 29 is a graphic repressentation showing the relationsship between the pounds pressure per ssquare inch gauge and the stage utϋized with a specific vaporizable fluid and temperature applied thereto for the various stages in the pumping -sequence of the earth-heat-powered air heating system of FIG. 28. FIG. 29 is a FIG. similar to FIGS. 10, 19, an 27, previously discussed. In FIG. 29, a cold temperature is presumed to be 40°F and a hot temperature is presuned to 60°F. A pressure of 35 P.S. is presumed from the output of the regenerator to the input of the system FIG. 29 assumes the .following to be approximately accurate: at 40°F the pounds presssure exerted by "METHYL CHLORIDE" is 28 P.S.I.G.; at 60°F the pounds pressure exerted by "METHYL OJLORIEE" is 46 P.S.I.G.; at 40°F the pounds pressure exerted by "FRECN 12" is 37 P.S.I.G.; at 60°F the pounds presssure exerted by "FRECN 12" is 56 P.S.I.G * ; at 40°F the pounds pressure exerted by "FRECN 500" is 45 P.S.I.G.; at 60°F the pounds presssure exerted by "FRECN 500" is 70 P.S.I.G.; at 40°F the pounds pressu exerted by "FRECN 115" is 59 P.S.I.G.; at 60°F the pounds pressure exerte by "FRECN 115" is 88 P.S.I.G.; at 40°F the pounds pressure exerted by "FREON 502" is 80 P.S.I.G.; at 60°F the pounds pressure exerted by "FRBON 502" is 140 P.S.I.G.; at 40°F the pounds presssure exerted ' by "KULΣ_NE-13 * is 123 P.S.I.G.; at 60 β F the pouαis pressure exerted by "KDLENE-131 H ^ is 150 P.S.I.G.; at 40 β F the pounds pressure exerted by "FREON 13B1" is 146 P.S.I.G.; and at 60 β F the pounds presssure exerted by "FRECN 13B1" is 180 P.S.I.G. The action of the compressor 376 is similar to the pumping action previously discussed herein and shown and discussed, for example, FIGS. 10, 19, and 27. The firsst fluid pumped through the compressor is a to be FRECN 12, for this example, but may be any appropriate fluid, with corresponding plurality of sseccnd fluids which follow the principles taug herein. The containers utilized within each stage may be individually designed to perform as an appropriate heat exchanger to obtain the desire degree of vaporization or condensation of the fluid enclosed within the h exchanger. The plurality of stages of each multiple-stage snail te perat differential hsaat-pαwered pump may be considered by terrninology usage as being a first stage, followed by a second stage, followed by a third stag followed by a fourth stage, followed by a fifth stage, followed by a sixt stage, etc. The first, third, and fifth stages would be considered odd- numbered stages. The second, fourth, and sixth stages would be considere even-numbered sstages. Each of the containers holding the various fluids is actually a heat exchanger which can be tailored in size for each puπping stage in manner that each of the flexible msribers within the various pumping stage will be properly enlarged or contracted at the proper time for the cycle 5 change with the ireximum efficiency and utilization of the pressure differ tials. The systsn is designed to be in synchronization. The bladders, which are filling with vapor, reach -their maximum at the same time that t ' bladders that are contracting reach their miiimum. Each of the container may be designed as a heat exchanger to be of ssuch size and to retain such 10 qualities as a fluid-to-fluid heat exchanger so as to aid in the ssynchrcn zatiαn of the entire system. In both the pump systsn and the generating systsn, the system can operate frαn any two sources of hot and cold fluid. Any desired sour of hot and cold fluid can be ussed. A solar collector of any form can be 15 utilized. A solar pond could be utilized under the proper circumstances. Each different vaporizable fluid has a different vapor pressu versus tsrperature relationsship. By selecting the correct vaporizable fluid for the heat exchangers or container of each stage, the hydraulic pressure caussed by the heat exchanger being at the high temperature for a 20 given even-numbered sstage can be made higher than the hydraulic pressure in the .subsequent, odd-numbered sstage when its heat exchanger is at the le tsrperature. Fluid wili flow frcm any even-numbered sstage to the next od numbered stage even though the odd-numbered sstage contains a vaporizable fluid with a higher vapor pressure for a given terrperature. 25. The first fluid, which may be water, is incrβnentally elevated in pressure stage-by-stage to the pressure of the lasst stage and then it exits the multiple-stage small temperature differential heat-powered puπp. The plurality of puπping stages has the capability of utilizing the snail tsrperature differential heat ssource to pump a fluid greatly beyond the 30 vapor pressure differential of a single vaporizable fluid. The output pressure of the multiple-stage snail tsrperature differential heat-pcwered puπp is limited only by the high teπperature vapor presssure of the vapori¬ zable fluid used in the last stage allowing its application for very high pressure requirements. 5 The present invention may be utilized for pumping fluid from a stream or other ssurface source to an elevated location .suitable for storag of fluid. The sstored fluid would then descend through a pipe and power a conventional hydraulic turbine electric generator combination for commercia electric power production. The sstored fluid may be utilized to power the turbine at night and during intervals of low ssolar flux if solar energy were the source of heating the hot fluid for the system. The elevated location may be a reservoir and the reservoir output may be ussed for irriga tion purposes or for lydro-electric power. The containers may be heat exchangers of the fluid-to-fluid variety. The purpose of the heat exchangers is to transfer heat from the fluid in the conduit to the fluid within the container and vice versa. The container is designed so that when an amount of fluid is vaporized, enough gas is generated to inflate the flexible msnber to nearly the ssize of the pressure chamber in the pumping sstage. The pressent invention enables the generation of significant mechanical power frαn snail teπperature differen¬ tials and can be utilized to take advantage of energy frαn solar collectors This invention provides a heat operated pump which can achieve high output pressure pumping capacity. This invention is capable of easily converting large amount of low teπperature differential thermal energy into hydraulic borssepwer which can then be utilized to power a hydraulic turbine electric generator combination. The systems herein can offer a practical method of converting solar elergy into cheap electrical power and do much to make solar energy a practical alternative to fossil fuels. The pump systsn may puπp fluids which include liquids or gases. heating means may utilize fluids which may be liquids or gases. The cooli means nay utilize fluids which may be liquids or gases. Any cαrbination o liquids or gases may be ut l zed for the fluid pumped or the fluid ussed in the heating means or the fluid used in the cooling means. The pump system may compress refrigeration-type gas. The pump can be ussed as the compress in a heat pump. After cαrpresssion, the condensation and evaporation of th gas may be used as heating and cooling means. The heat p rp for cooling o heating may utilize the condenssation or evaporation of the gas for heating and cooling means rather than a inechanical or electrical input to a compressαr. While the invention has been described with reference to .specifi srbαliments, the description is iliύsstrative and is not to be ccnsstrued as limiting the sscope of the invention. Various modifications and changes ma occur to t±osse sskilled in the art without departing frαn the spirit and scope of the invention as defined by the appended claims. OMPI

Claims: I claim: 1. A pump systsn for purping a firsst fluid from a source to a output facility comprising: a. a multiple-stage small temperature differential heat-powered pump; b. a second fluid heating means operable to heat a second fluid to a hot teπrperature, where it becαnes a hot fluid which is divertable into said multiple-stage small tsrperature differential heat-pcwered purrp; c. a third fluid cooling means operable to cool a third fluid to a cold temperature where it becomes a cold fluid which is divertable into said multiple-stage small temperature differential heat-powered puπp; d. a fluid diverting means wit in which ssaid hot fluid and ssaid cold fluid are purrped, said fluid diverting means controls the flow of ssaid hot fluid and said cold fluid into said multiple- sstage small tsrperature differential heat- powered purrp; e. a plurality of conduits within which ssaid input fluid diverting means diverts said hot fluid and said cold fluid; f . ssaid multiple-sstage small tsrperature differential heat-powered puπp comprising: (1) a plurality of pumping stages j. and (2) a plurality of check valves, one of ssaid plurality of check valves being located on the input and output of ssaid multiple-sstage small temperature differential heat-powered pu p and between each of ssaid plurality of purrping stages; OMPI g. each of said plurality of pumping sstages cαrprising: (1) a pressure chamber operable to hold said firsst fluid; and (2) a flexible msriber within ssaid pressure chamber operable, when expanded, to exert pressure against said first fluid and to force said first fluid -from ssaid pressure chamber through the one of said plurality of check valves between ssaid presssure clamber and the next pressure chamber of the next .subsequent puπping stage of said plurality of pumping sstages or ssaid output, if ssaid pressure chamber is within the lasst of said plurality of pumping sstages, when ssaid pressure within said pressssure chamber exceeds the next pressure in ssaid next presssure chamber or ssaid output; h. each of said flexible msnbers, is connected to a contei which is one of a plurality of containers, each said container holding one of a plurality of vaporizable fluids, whereby when ssaid cont iner is subjected to ssaid hot fluid, ssaid one of said plurality of vaporizable fluids vaporizes causing said flexible msnber to expand and, when said container is subjected to said cold fluid, ssaid one of ssaid plurality of vaporizable fluids condenses caussing ssaid flexible msnber to contract; and i. each ssaid container of ssaid plurality of cont iners is sseσured wit in one of said plurality of conduits whereby each said container is subjected alternately to said hot fluid and said cold fluid. 2. A pu p systsn according to claim 1 wherein said hot fluid ater and ssaid cold fluid is cold water. 3. A pump systsn according to claim 1 wherein said second flu heating means utilizes solar energy to heat said second fluid to ssa hot teπperature. 4. A pu p systsn according to claim 1 wherein said input flui diverting means diverts said hot fluid and ssaid cold fluid alternat into one of a plurality of conduits within said multiple-stage smal tsrperature differential heat-powered purrp. 5. A puπp systsn according to claim 1 wherein each said one o said plurality of vaporizable fluids which vaporizes into said flex inember has a higher vapor pressure, when heated to ssaid hot tsrpera than the cold vapor pressure of the next said one of ssaid plurality of vaporizable fluids which vaporizes into the next flexible member within ssaid next pressure chamber or to said output, if said flexib msnber is within said last of said plurality of pumping stages. 6. A pump system according to claim 5 wherein ssaid input flui diverting means diverts said hot fluid, and said cold fluid alternate into each one of a plurality of conduits within said multiple-sstage small temperature differential heat-pcwered pump. 7. A pump system according to claim 6 wherein each of said plu of pumping sstages has said flexible member connected to said one of plurality of containers and said one of ssaid plurality of containers secured within said one of ssaid plurality of conduits and is subjec alternately to said hot fluid and said cold fluid, the next .subseque purrping stage of said plurality of puπping sstages has a next flexibl msnber connected to another one of said plurality of containers whic is secured within another one of said plurality of conduits and is subjected alternately to said cold fluid and said hot fluid at times opposite to said one of said plurality of containers; whereby when said one of ssaid plurality of containers is subjected to said hot fluid, said another one of ssaid plurality of containers is subjected to said cold fluid, and vice versa, so that ssaid plurality of puπping sstages when the first stage las a first flexible member connected to a first container subjected to ssaid hot fluid, the second stage has a second flexible msnber connected to a second cont iner ssubjected to said cold fluid, with each odd-numbere container being subjected to the opposite condition of each even- nurrbered container, and when ssaid firsst sstage has said first flexibl member connected to ssaid firsst contai er subjected to ssaid cold flui said second stage has said second flexible member connected to said second container subjected to said hot fluid with each odd-numbered cont iner being subjected to the opposite condition of each even- numbered container within said plurality of containers' connected to said plurality of pumping stages. 8. A pu p sysstem according to claim 7 wherein said firsst vapor zable fluid in ssaid firsst container, which is connected to ssaid firs flexible member in said first pumping sstage, has a cold vapor pressu lower than the pressure of said firsst fluid in ssaid source. 9. A purrp system according to claim 8 wherein said second vapo zable fluid in ssaid second container, which is connected to ssaid second flexible member in ssaid second pumping sstage, has a cold vapo pressure lower than the hot vapor pressure of said first vaporizable fluid in ssaid first container; whereby when said firsst container is subjected to said hot fluid and when said second container is subjected to s id cold fluid the pressure within ssaid first puπping stage is greater than the pressure within ssaid second puπping sstage and ssaid firsst fluid will move through the one of said plurality of check valves between said first pumping stage and said second purrping stage into said second puπping sstage. 10. A purrp system according to claim 1 wherein said plurality of conduits comprises a first conduit and a second conduit. 11. A pump systsn according to claim 10 further comprising an output fluid diverting means operable to control the flew of said h fluid from said multiple-sstage small temperature differential heat- pcwered purrp back to said second fluid heating means and to control the flew of said cold fluid frαn ssaid multiple-stage small tsrperat differential heat-pcwered pu p back to said third fluid cooling mea 12. A pump systsn according to claim 10 wherein said input flu diverting means cαrrprises an inlet gate with a first inlet gate pos and a ssecond inlet gate position wherein when said inlet gate is in said first inlet gate position, said hot fluid is diverted into ssai first conduit and said cold fluid is diverted into ssaid second cond and when ssaid inlet gate is in said second inlet gate position, sai hot fluid is diverted into said second conduit and said cold fluid i diverted into said first conduit. 13. A purrp systsn accca_ding to claim 11 wherein ssaid output flu diverting means comprises an outlet gate with a first outlet gate position and a ssecond outlet gate position wherein when said outlet gate is in said firsst outlet gate position, ssaid hot fluid is divert frcm said first conduit back to said second fluid heating means and said cold fluid is diverted frαn ssaid second conduit back to ssaid third fluid cooling means, and when said outlet gate is in said seco outlet gate position, ssaid hot fluid is diverted frcm said second conduit back to said second fluid heating means and said cold fluid diverted frαn said first conduit back to ssaid third fluid cooling me 14. A purrp system according to cl im 13 wherein ssaid input flu diverting means comprises an inlet gate with a firsst inlet gate pos and a ssecond inlet gate position wherein when said inlet gate is in said first inlet gate position, said hot fluid is diverted into ssai first conduit and ssaid cold fluid is diverted into ssaid second cond and when ssaid inlet gate is in said second inlet gate position, sai hot fluid is diverted into ssaid second conduit and ssaid cold fluid diverted into ssaid first conduit. 15. A pump system according to claim 14 further comprising a g control means connected to said ιr_αltiple-stage small temperature differential heat-powered pump and operative to change said inlet g and ssaid outlet gate .simultaneously frαn one gate position to anoth 16. A puπp system according to claim 1 wherein each of ssaid plurality of check valves comprises a plurality of hinged msnbers. 17. A generating system for converting flew of a first fluid electrical power comprising: a. a plurality of. multiple-sstage small temperature differential heat-powered pumps; b. a second fluid heating means operable to heat a ssecond fluid to a hot teπperature, where it becomes a hot fluid which is divertable into said plurality of multiple-stage small tsrperature differential heat-pcwered pumps; c. a third fluid cooling means operable to cool a third fluid to a cold teπperature where it becomes a cold fluid which is divertable into ssaid plurality of multiple-sstage small teπperature differential heat-pcwered pumps; OMPI d. a hydraulic-to-mechanical power conversion means operative to convert the flow of ssaid first fluid to mechanical power with the input to said power conversion means connected to the output of said plurality of multiple-stage small tsrperature differential heat-powered pumps and the output of said hydraulic-to- mechanical power conversion means connected to the input of ssaid plurality of multiple- stage samall temperature differential heat- powered pumps; and e. a mec__-urάcal-to-electrical power conversion means connected to said ydraulic-to-mechanica pcwer conversion means and operative to produce electrical power. 18. A generating system for converting flow of a firsst fluid to electrical power comprising: a. a plurality of multiple-sstage s ali temperature d fferential heat-powered pumps ccxnprising: (1) a plurality of check valves; and (2) a plurality of pumping stages, with one of said plurality of check valves being located on the input and output of ssaid each of said plurality of pumping stages, cαrrprissing: (a) a pressure chamber operable to hold said firsst fluid; and (b) a flexible msnber within said pressure chamber operable, when expanded, to exert pressure against said first fluid and to force said firsst fluid frαn said pressure chamber through the one of said plurality of check valves between said pressure chamber and the next presssure chamber O PI of the next .subsequent puπping stage of said plurality of pu ping stages or ssaid output, if said presssure chamber is within the last of ssaid plural ity of 5 purrping stages, when ssaid pressure within ssaid pressure chamber exceeds the next presssure in ssaid next pressure chamber αr said output; b. a second fluid heating means operable to heat a 10 s cond fluid to a hot tsrperature, where it becαnes a hot fluid which is divertable into ssaid plurality of multiple-stage small temperature differential heat-pcwered pumps; c. a third fluid cooling means operable to cool a 15 third fluid to a cold terrperature, where it becomes a cold fluid which is divertable into ssaid plurality of multiple-sstage small temperature differential heat-powered pumps; d. a _ydraι_lic-t_o-mechaι_ical. power conversion means 20 operative to convert the flow of said firsst fluid to mechanical power with the 'input to ssaid bydrau ic-to-irechanical po*er conversion means connected to the output of said plurality of πultiple-stage small teπperature differential 25 heat-pcwered pumps and the output of said lydraulic-tc-mechanical power converssion means connected to the input of ssaid plurality of multiple-stage small teπperature differential heat-powered pu ps; 30 e. a π__clanical-to-electrical power conversion means connected to ssaid lydraulic-to-mechanical power conversion means and cperative to produce electrical power; f. wherein each of said flexible msnbers is connected to a container, which is one of a plurality of containers, each holding one of a plurality of vaporizable fluids whereby whan said cont iner is subjected to said hot fluid, said one of ssaid plurality of vaporizable fluids vaporizes causing said flexible member to expand and, when said container is subjected to said cold fluid, said one of said plurality of vaporizable fluids condenses causing said flexible member to contract; and g. wherein each said one of said plurality of vaporizable fluids which vaporizes into said flexible member has a higher vapor presssure, when heated to said hot tsrperature, than the cold vapor pressure of the next ssaid one of ssaid plurality of vaporizable fluids which vaporizes into the next flexible msnber within said next pressure chamber or to said output, if said flexible msnber is within ssaid last of said plurality of pumping sstages. 19. A generating system for converting flow of a firsst fluid t electrical power comprising: a. a plurality of multiple-stage small temperature differential heat-powered pumps; b. a second fluid heating means operable to heat a sseccnd fluid to a hot teπperature, where it becomes a hot fluid which is divertable into said plurality of multiple-sstage small tsrperature differential heat-powered pumps; c. a third fluid cooling means operable to cool a third fluid to a cold temperature, where it becomes a cold fluid which is divertable into said plurality of multiple-sstage small temperature differential heat-powered pumps; O d. a hyd_aulic-~t_o-mec_anical power conversion means operative to convert the flow of said first fluid to mechanical power with the input of ssaid hydraulic-to-mecfaanical power conversion means 5 connected to the output of said plurality of im ltiple-sstage small teπperature differential heat-powered pumps and the output of said hydraul io-to-mechan ica , power conversion means connected to the input of said plurality of 10 imiltiple-sstage smal l teπperature differential heat-pcwered pumps; e. a mecl_anical-to-electrical power converssion means connected to said hyd_auHc-to-_r©chanical power conversion means and operative to produce 15 electrical power; f . wherein ssaid hot fluid and ssaid cold fluid are purrped into an input fluid diverting means which controls the flow of said hot fluid and said cold fluid into ssaid plurality of ira l ti le-sstage small 20 tsrperature differential heat-powered pu ps; g. wherein said input fluid diverting means diverts ssaid hot fluid and ssaid cold fluid alternately into αie of a plurality of conduits within ssaid plurality of multiple-sstage small temperature 25 differential heat-powered pumps; . h. wherein said plurality of conduits cαrpri≤ses a first conduit and a second conduit; and i. wherein said input fluid diverting means cαπprisses an inlet gate with a firsst inlet gate position and 30 a second inlet gate position wherein when ssaid inlet gate is in said firsst inlet gate position, said hot fluid is diverted into ssaid first conduit and ssaid cold fluid is diverted into ssaid second conduit, and when said inlet gate is in said second inlet gate 35 position, said hot fluid is diverted into said second conduit and ssaid cold fluid is diverted into said firsst conduit. 20. A pump system for pumping a firsst fluid frαn a source to a output facility cαr rising: a. a multiple-stage pump comprising: (1) a plurality of purrping stages; and (2) a plurality of check valves, one of said plurality of check valves being located on the input and output of said multiple- stage pu p and between each of ssaid plurality of pumping sstages; b. each of said plurality of purrping stages cαrprising: (1) a pressure chamber operable to hold ssaid first fluid; and (2) a flexible member within ssaid pressure chamber operable, when expanded, to exert pressure against said firsst fluid and to force said first fluid frαn said pressure chamber through the one of ssaid plurality of check valves between said pressure chamber and the next pressure chamber of the next sub≤sequent puπping stage of ssaid plurality of puπping stages or said output, if said pressure chamber is within the last of said plurality of pumping stages, whan said pressure within said pressure chamber exceeds the next pressure in said next pressure chamber cr ssaid output; c. each of said flexible members, is connected to a contai which is one of a plurality of containers; and d. a plurality of vaporizable fluids, one of said plurality of vaporizable fluids contained within each one of said plurality of containers, whereby each said container holds one of said plurality of vaporizable fluids and when ssaid container is subjected to a hot tem ture, ssaid one of said plural ty of vaporizable fluids vaporizes cau said flexible member to expand and when ssaid container is subjected a cold temperature, said one of ssaid plurality of vaporizable fluids condenses causing said flexible member to contract. O PI 21. A pump systsn according to claim 20 wherein each said one of ssaid plurality of vaporizable fluids which vaporizes into said flexible member has a higher pressure, when heated to said hot tsrpera¬ ture, than the cold pressssure of the next ssaid one of said plurality of -vaporizable fluids which vaporizes into the next flexible member within said next pressure chamber or to said output, if said flexible member is within said last of said plurality of pumping sstages. 22. A pump system according to claim 20 further cαrprising terrperature alternating means operative to change the temperature to which each said container is subjected frαn said hot teπperature to ssaid cold teπperature and from ssaid cold tsπperature to ssaid hot tsrperature, simultaneously so that the one of said plurality of vaporizable fluids which determines the state of each said flexible msnber within ssaid pressure chamber of each of ssaid plurality of purrp¬ ing stages will be at a different temperature than the one of said plurality of vaporizable fluids which determines the state of the next ssaid flexible member within the next subsequent said pressure chamber of said plurality of puπping sstages. 23. A cooling sysstem for cooling an enclosure cαrprising: a. a cαrpressor utilizing a puπp system cαrprising 5 a multiple-stage pump utilizing a plurality of small temperature differential heat-operated pumping stages for purrping a first fluid through said multiple-stage purrp raising the tsrperature and pressure of said first fluid; Q b. condensing means within said enclossure connected to said puπp system through which said firsst fluid flows, which condenses said firsst fluid and removes heat from said firsst fluid, thereby heating said enclosure; and 5 c. evaporating means connected to ssaid pump sysstem and ssaid condensing means. OMFI \VIPO 24. A heating system for heating an enclossure conprising: a. a compressor utilizing a puπp sysstem conprising a multiple-stage pump utilizing a plurality of ssπall teπperature differential heat-operated 5 pumping stages for pumping a first fluid through said multiple-sstage purrp raising the temperature and pressure of said first fluid; b. condensing means within said enclosure connected to ssaid pump system through which ssaid first fluid 10 flows, which condenses said first fluid and removes heat frαn said firsst fluid, thereby heating ssaid enclossure; and c. evaporating means connected to said purrp syβtem and said condensing means. 15 25. A puπp system for purrping a firsst fluid cαrprising: a. a multiple-stage pu p ccmprissing: (1) a plurality of pumping stages; and (2) a plurality of check valves, one of ssaid. plurality of check valves being located on 20 the input and output of said multiple-stage purrp and between each of said plurality of pumping stages; . b. each of ssaid plurality of pumping stages cαrprising: (1) a pressure chamber operable to hold said 25 first fluid; and (2) a flexible member within said pressure chamber operable, when expanded by a vapor from a second fluid, to exert pressure against said first fluid and to force said firsst fluid frαn said _ 30 ,' pressure chamber through the one of said plurality of check valves between said pressure chamber and the next pressure chamber of the next subsequent pumping stage of said plurality of pumping stages or said output, if said pressure chairber is within 35 the last of said plurality of puπping stages, when said pressure within ssaid pressure chamber exceeds the next pressure in ssaid next pressure chamber or said output; and /-^\JRE OMPI c. a vapor pressure control means connected to said flexible msnber and operative to cause said flexible member to expand or contract at a given time, said vapor pressure control means cαrprising: 5 (1) a cold container connected to said flexible msnber and operative, by use of a cooling means, to keep said second fluid cold; (2) a hot container connected to said flexible member and operative, by use of a heating means, to keep said I® second fluid hot; (3) a cold container control means connected to said cold cont i er operative to open or close the connection between ssaid cold container and said flexible msnber; a (4) a hot container control means connected to said hot " container operative to open or close the connection between said hot container and said flexible member. 20 26. A sysstem according to claims 23 or 24 wherein said multiple stage purrp comprises a plurality of check valves, one of said plurality of check valves being located on the input and output of said multiple-stage purrp and between each of said plurality 25 of pumping stages. OMP v IP 27. A systsn according to claim 26 wherein each of said plurality of pumping stages comprises: a. a pressure chamber operable to hold ssaid first fluid; and b. a flexible member within ssaid pressure chamber operable, when expanded by a vapor from a second fluid, to exert pressure against said first fluid and to force said firsst fluid frαn said pressure chamber through the one of said plurality of check valves between said pressure chamber and the next pressure chamber of the next .subsequent puπping stage of said plurality of puπping stages or said output, if said pressure chamber is within the last of said plurality of pumping stages, when ssaid pressure within said pressure chamber exceeds the next pressure in said next pressure chamber or said output. 28. A systsn according to claim 27 wherein each of ssaid flexible msnbers is connected to^ a vapor pressure control means which is operative to cause said flexible member to expand or contract at a given time. 29. A system according to claim 28 wherein said vapor pressure control means comprises: a. a cold container connected to ssaid flexible msnber and operative, by use of a cooling means, to keep ssaid ssecond fluid cold; b.' a hot container connected to said flexible msnber and operative, by usse of a heating means, to keep ssaid second fluid hot; c. a cold container control means connected to ssaid cold container operative to open or close the connection between ssaid cold cont iner and ssaid flexible member; and d. a hot container control means connected to said hot container operative to open or close the connection between ssaid hot container and said flexible msnber. 30. A systsn according to claims 29 and 23, 24, or 25 further cαmprissing a vapor pressure control senssing means connected to ssaid flexible msnber and operative to ssense the condition of ssaid flexibl member and to open or close said cold container control means and sa hot container control means accordingly. 31. A system according to claims 30 and 23, 24, or 25 wherein s vapor pressure control ssensing means cxxπprisses: a. a magnet .secured onto ssaid flexible member; b. an upper magnetic proximity switch secured within said pressure chamber and operative to be activated when said flexible member is enlarged; c. a lcwer magnetic proximity sswitch .secured within ssaid pressssure chamber and operative to be activated when said flexibl msriber is deflated; and d. a valve cαrmand generator connected to said upper magnetic p_xκ__mity sswitch and ssaid lower magnetic proximity sswitch and operative to open and close said cold container control means and said hot conta ner control means when receiving the appropriate indication of ssaid flexible member being enlarged or deflated. 32. A system according to claims 29 and 23, 24, or 25 further conprising a condenssate pump connected between ssaid cold container a ssaid hot container and operative to puπp said second fluid frαn said cold container to said hot container. 33. A system according to claims 32 and 23, 24, αr 25 further comprising a condensate purrp control means connected between ssaid co cont iner and said conde sate pu p and operative to sense the level said second fluid in ssaid cold container and to activate ssaid conden pump. OMPI 34. A system according to claims 29 and 23 or 25 wherein said container is secured within a ssolar collector. 35. A systsn according to claims 34 and 23 or 25 wherein said c container is secured below ground level. 36. A systsn according to claims 34 and 23 wherein said conden ing means is secured within said solar collector, along with said h contai er, in order to remove said heat frαn ssaid firsst fluid and transfer said heat to said second fluid within said hot container, thereby creating a regenerating sysstem increasing the efficiency of ssaid solar collector and ssaid cooling system. 37. A system according to claims 29 and 24 wherein ssaid cold container is secured within an evaporative cooler. 38. A system according to claims 37 and 24 wherein ssaid evapora ting means is secured within said evaporative cooler, along with sai cold container, in order to remove ssaid heat frαn ssaid evaporative c and, thereby to remove ssaid heat frαn said second fluid within ssaid cold container, thereby creating a regenerating systsn increasing th efficiency of said evaporative cooler and said heating means. 39. A system according to claims 28 and 23, 24, or 25 wherein s pressure chamber cαnprisses a plurality of flexible members connected to a single vapor pressure control means. 40. A systsn according to claims 28 and 23, 24, or 25 wherein ss pressure chamber comprises a plurality of flexible members, each con to a different vapor pressure control means. /" B ORE f OMPI 41. A systsn according to claims 27 and 23, 24, or 25 wherein s flexible msnber in each of said plurality of purrping stages is conne to a vapor presssure control means which can expiand αr contract said flexible msriber utilizing vapor from a firsst vaporizable fluid whic has a higher heated pressure than the cold teπperature vapor presssur of a second vaporizable fluid used within the next flexible msriber within the next puπping sstage,- αr to said output, if said flexible merber is within the lasst of said plurality of puπping stages. 42. A system according to claims 34 and 23, 24, or 25 wherein ss solar collector contains a plurality of ssaid hot containers, each containing a different vaporizable fluid and .secured to a different flexible member which is secured within a different purrping stage within said multiple-sstage pump. 43. A system according to claims 37 and 24 wherein ssaid evapora tive cooler contains a plurality of said cold containers, each cont ing a different vaporizable fluid and .secured to a different flexibl member which is secured within a different purrping sstage within ssaid multiple-sstage pump. CMP

Inventors: BURNHAM FRANCIS L, BURNHAM, FRANCIS, L.
Applicants: ORANGEBURG TECHNOLOGIES INC, ORANGEBURG TECHNOLOGIES, INC.
Application year: 1982
Main classification: F04B25
IPC codes: F04B25, F04B41