WO2013186785A1

WO2013186785A1 - Smart fluid displacement systems and methods and their innovative applications

Info

Publication number: WO2013186785A1
Application number: PCT/IN2013/000026
Authority: WO
Inventors: Sumbramaniam UDHAYAMARTHANDAN
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-01-14
Filing date: 2013-01-15
Publication date: 2013-12-19
Anticipated expiration: 2014-07-14

Description

SMART FLUID DISPLACEMENT SYSTEMS AND METHODS AND THEIR

INNOVATIVE APPLICATIONS

Field of invention : The invention is related to systems of · novel hydraulic Ram pumps, used for displacement of fluid collected into the system. More specifically it works like an automatic reciprocating ram pump capable of displacing fluid during pressure stroke and filling in during reversal motion of the ram, enhanced by buoyancy lift. The systems evade the use of direct electricity or fuel power and work best as gravitational energy extractor / converter devices.

Back ground and prior art of the invention : A pump is a device used to move fluids, such as gases, liquids or slurries. A pump displaces a volume by physical or mechanical action. Pumps alone do not create pressure; they only displace fluids, causing a flow. Adding resistance to flow causes pressure. Pumps fall into two major groups, positive displacement pumps and roto dynamic pumps. Their names describe the method for moving a fluid. FIG. PA PMP.12 shows the schematic diagram of a commonly followed distant pumping systems of water from extraction source, consisting of water source S, Base Collection Tank BCT, pump set (PMP-Si), connected to uphead conduction pipe line Li, delivering water into first stage uphead collection tank ICT, optional overhead tank OHT_b (shown in dotted lines). The capacity of the pump is set based on hydraulic head to be pumped up and efficiency. Pumps consume round the clock energy during operation. The major drawbacks of existing pumping systems are ; Lack of self activation and working, need for a prime mover drive (manual, mechanical, electrical motors or IC engines), efficiency factors, huge power / energy costs, wear and tear of components, difficulties in handling huge quantities like hydropower plant outlet water, flood / rain water diversions, etc and system failure in case of power cuts or fuel shortages. But none of the prior art inventions provide a solution to the. above problems and does not describe a method and system compared to the present invention.

Summary of the invention : Novel hydraulic ram systems, comprising- of fluid source, bottom collection tanks, floating ram connected with hollow air float, fluid loading unit, infeed & exit lines using direct or indirect fluid loading methods based on piston or plunger or plunger with telescopic seal coupling mechanisms. An apex fluid supply tank is the extra part of indirect fluid loading ram systems. The plunger mechanism being the most preferred system, due to lower friction and better efficiency than piston mechanism. The downward vertical movement of the ram causes displacement of entrapped fluid in collection tank and the upward reversal movement of ram enhanced by buoyancy uplift of airfloat on release of water or pressure, leading to filling in of fluid into bottom collection tank. This reciprocating ram pumps operate by mere gravitational energy and total weight of ram with fluid loaded into ram, and automatic buoyancy lift by Air float. Thus gravitational energy can be best harnessed using smart fluid displacement systems. Archimedes principle of floating and immersion, Pascal's law of pressure equilibrium in hydraulic machine systems, law of conservation of energy, are best applicable to these ram systems. By virtue of its immense potential, these rams find vast innovative applications in hydropower generation for instant fluid recycling back to source, , mass water transport without direct electricity / fuel power, hydro ship propulsion and hydraulic machines like cranes.

Objectives of the invention : The primary objective of the main invention is to lift water to higher altitudes by mere use of forces of nature, without the need for direct input energy. The smart fluid displacement systems and methods, unlike traditional pumping up operations, best make tactical use of gravity and antigravity forces feasible in fluid systems and air floats, thereby drastically reducing direct input power requirement. The secondary objectives are instant recycling of water back to source after hydropower generation, major reduction of direct pumping power required, mass water transport, major fuel reduction in ship propulsion using new concept called hydro ship and application to cranes in harbours and ships.

Disclosure of the Invention: The various embodiments, mechanisms, working principles and working of the smart fluid displacement systems and methods and their innovative applications are described in relation to the drawings. Throughout the description, fluid and water are considered as synonymous terms. Two exclusive chapters viz., I) Smart fluid displacement system and methods II) Innovative applications of smart fluid displacement systems and methods are disclosed.

I) Smart Fluid Displacement Systems & Methods : Pumping of fluid is a major service activity in water transportation and fluid delivery from source to end use points. This invention on Smart Fluid Displacement Systems and Methods describes novel systems of Rams fitted with Air floats, floating on entrapped fluid inside a cylinder / tower, uses downward gravitational energy of fluid loaded into the system for pressure stroking to displace entrapped fluid by immersion principle. The reversal upward antigravity motion of Ram being enhanced by release of fluid (load) supported by rising level of fluid and buoyancy floating forces. This reciprocal movement calls for no direct electrical / fuel energies, facilitates harnessing of gravitation energy via fluid and Air float behavior to do useful work. Plurality of such Rams are feasible based on a) Indirect fluid loading b) Direct fluid loading applying piston, plunger and plunger with telescopic seal coupling mechanisms, a) Indirect fluid loaded system : Indirect fluid loaded system using piston mechanism. FIG.SFD(IPS)-1 shows the vertical cross sectional view of a three units operated indirect fluid loaded system using piston mechanism. Whereas, alternate two units are sufficient, the third extra unit is meant for emergency breakdown services.

Construction: Referring to unit 1 of FIG.SFD(IPS)-1, the system comprises of a bottom fluid collection tank Ei connected with exit line ELj fitted with exit valve EiV] leading to conduction line CL, conducting fluid to destined end point of discharge. Floating on the cushion fluid in Ei is the hydraulic fluid loading unit Fi comprising of bottom Hollow Air float Hi A fitted with piston rings (PS), to which upper intermediate linkage cylinder IML, for storage of preloaded weight / fluid density addition to the ram, and fluid loading tank FT) above, the total vertical system (F,) being supported by guiders (Gd) for vertical movement. The fluid from source (S) is conducted via infeed line IF, into either via top infeed line TIF into the Ram (F,) or bottom infeed line BIF into bottom collection tank Ej. In case of top infeed line TIF, the infeed pipe is bored into the wall of Ei (sealed leak proof) further enters into slot space (SP) in IML, connected via flange and expandable hose (EH) fixed to top surface of hollow air float, linked to drain pipe DP bored radially via hollow air float body (leak proof), the bottom extended below H]A bottom and fitted with drain valve DV. The role of expandable hose EH is critical to have continuity of fluid flow from source S into the downward moving Ram. This circuit is meant for draining down fluid from source S via hollow air float top into bottom collection tank. Similarly the fluid from source S can also be drawn into Ei by bottom infeed line BIF via valve IiVi. The infeed options being case specific, based on effective release and rising level of fluid in E, . Placed above the level of Ei is the Apex fluid supply tank Gi fitted with clearing pump CP] attached with pipe line with foot valve FV contacting fluid in FT_t. Apex fluid supply tanks Gi /G₂/G₃ are supplied with fluid from S by pump FP via piping and exclusive valves. Fluid from Gi can flow into FTi via flexible hoses fitted with control valves. The purpose of clearing pump CP] is to clear up fluid from FT) via foot valve FV during upward stroke of Ram F,. The respective exit lines ELi(unit 1) / EL₂ (unit 2) / EL₃ (unit 3) lead upwards to the required head of lift leading to downward conduction line CL meant for discharging of displaced fluid to distained end point. Similar configurations are applicable to unit 2 and unit 3 also.

Working cycle: Unit 1 is shown with bottom downward stroke of floating Ram F[ in Ei. During downward pressure stroke in unit 1, Inlet lines from source S (TIF or BIF) are closed, fluid is allowed to flow into FT] from Gi by gravity through flexible hose FH, causing increase in density / weight of Ram Fi to overcome the buoyancy floating equilibrium force, leading to immersion of Fi into pre stored fluid in E) (referring unit 2 position). The scrapping action of pistons PS, fitted to hollow air float Hi A, develop pressure in the entrapped space between Hi A bottom and Ei. Exit valve EjVi being open, the hydraulic pressure developed due to the moving down Ram Fi lead to pressurized exit of fluid via exit line EL], up into conduction line CL leading to distained end point of discharge at a head of 'h'. The weight of Ram, pre stored fluid weight in IML are designed to overcome frictional resistance of piston PS. The float buoyancy capacity of HiA is based on volume of hollow air space in order to enhance reversal of F, on release of fluid load from FT] back to G_\. That means the buoyancy floating equilibrium of F] prior to fluid loading in FT) is disturbed by way of density addition of the Ram by fluid loading in FT,, leading to downward movement pressure stroke of Fi in E, causing fluid displacement equivalent to volume of fluid loaded into FTj. Unit 2 is shown with upward reversal stroke of floating Ram F₂ in E₂. During upward lifting pressure stroke in unit 2, Inlet lines from source S (TIF or BIF) are opened, fluid is allowed to flow back into G₂ from FT₂ by pumping action of CP₂ via foot FV, causing decrease in weight of Ram F₂ leading to floating reversal of F₂ over fluid in E₂ (referring unit 2 position). The simultaneous pumping up of fluid from FT₂ to G₂ and entry of inflowing fluid from source in E₂ either via TIF or BIF lead to upward reversal lift of Ram F₂ in E₂ and reaches the topmost feasible point. This is the filling stroke of fluid into unit 2. During which time exit valve E₂V₂ in line EL₂ is closed. As inflow fluid into E₂ is filled into E₂ causing fluid level rise in E₂ and simultaneous lifting up of Fi, the density of the same being progressively reduced due to fluid clearance from FT₂ to G₂. In this stroke, the volume of fluid transferred from FT₂ to G₂ and filled in fluid into E₂ or same. In a similar way, alternate cycles in unit 1 and unit 2 or unit 3 result in continuous displacement of fluid from source S which is alternatively fed into respective individual Rams. The major drawbacks of indirect fluid loaded system using piston mechanism are 1) losses due to piston friction 2) Slippage losses of piston 3) difficulty of designing larger size piston rings and uniform boring of bottpm collection tank inner walls 4) Extra energy required for pumping up fluid from fluid loading tank to Apex fluid supply tank and source to Apex fluid supply tanks 5) Extra constructional cost of structures, 6) poor efficiency 7) possible struck of disturbances of piston elements during movement and wear and tear of contact surfaces and 8) higher maintenance cost. That leads to the development of indirect fluid loaded system using plunger mechanism (without piston) being described next.

In case of indirect fluid loaded piston systems, the fluid pumping energy to Apex fluid supply tank Gi can be eliminated by way of keeping the level of Gl below infeed fluid supply line. Accordingly, the tank capacity of E], volume of Fi can be progressively increased to render extra hydraulic pressure to lift water through exit line EL.

Indirect fluid loaded system using Plunger mechanism. FIG.SFD(IPL)-2 shows the vertical cross sectional view of a two units operated indirect fluid loaded system using plunger mechanism. The major difference in this system being the absence of piston elements, rising of displaced fluid via annular space between Ram surface and the bottom collection tank extending upwards upto the delivery end head. Indirect fluid loading and unloading, charging fluid into Ei/E₂ from source are similar to piston mechanism.

Construction: Referring to unit 1 of FIG.SFD(IPL)-2, the system comprises of a bottom fluid collection tank E_] having raised up level upto delivery head level 'h', fitted with overflow tray OFT_! encircumferencing the top portion having outlet -lines leading to conduction line CL conducting fluid to destined end point of discharge. Floating on the cushion fluid in E, is the hydraulic fluid loading unit F,, comprising of bottom Hollow Air float H_] A without piston elements, connected to upper intermediate linkage IML for pre loaded weight / fluid storage for density addition to the ram, above which fluid loading tank FT] is placed. Ram Fi moves via reciprocally guiders (Gd). The fluid from source (S) enters the Ram via infeed line IF], top infeed line TIF connected to expendable hose EH, coupled to hollow air float H]A top, drain pipe DP fitted with drain valve DV. The role of expandable hose EH is critical to have continuity of fluid flow from source S into the downward moving Ram. Bottom infeed line BIF can also be used for filling fluid into Ei from source S. Slot space SP in Ram F_} takes care of free movement of Fi against horizontal pipe line TIP. FT] is connected to Apex fluid supply tank Gi via flexible hosing FH, pumping up from FT, to Gi is rendered by pumps CP] via foot valve FV. The apex fluid supply tanks G₁/G2 G3 are fed with fluid from source S via feed pump FP. Similar configuration is applicable to unit 2 also

Working cycle: Downward pressure stroke; unit 1 position shows the downward pressure stroke of Ram Fi into bottom collection tank Ei. When fluid is released down from Gj via FH into FTi, the floating buoyancy equilibrium is disturbed by addition to the weight of Fi causing descending downward movement, leading to displacement of equal volume of fluid loaded into FTi via fluid exit slit (FES) / annular space to overflow into OFTi and further by gravity flow via conduction line CL and to end point of discharge. The discharge continues till reaching the pre determined point of H|A bottom into E, and stops on emptying of G*. The total hydraulic load required to develop pressure is determined by the combined effect of material weight of F_\, weight of pre stored fluid weight in IML and weight of loaded water in FT_! per cycle.

Upward filling stroke : Referring to position of unit 2, the upward filling stroke of Ram F₂ into bottom collection tank E₂, when fluid is pumped up from FT₂ into G₂ by pump CP_2i the release of fluid load into F₂ and simultaneous inflow of fluid from source S into E₂ causes fluid level rise in E₂, leading to upward reversal of Ram F₂ in E₂. This filling stroke continues till all the fluid from FT₂ is cleared up into G₂. The filled in volume in E₂ is equivalent to cleared up fluid volume from FT₂ to G₂. The alternate up and down reciprocal movement of plunger Ram in bottom collection tank lead to continuous displacement of fed in fluid from source S to end use point at a head level of 'h' .

The major advantages of indirect fluid loaded using plunger mechanism are 1) absence of friction and friction losses during displacement 2) avoiding of wear and tear of contact elements 3) smoother functioning and 4) improved efficiency factor. The major disadvantages being the increased structural costs of bottom collection tanks and indirect fluid loading components. The depth of bottom collection tanks need to be almost double compare to required fluid lift head 'h' apart from cushion fluid storage depth.

b) Direct fluid loaded system - The draw backs of additional structural and construction cost of apex fluid supply tanks, additional pumping energy for feed fluid supply from source to apex fluid supply tanks, FT! to Gi etc and tall structural costs of bottom collection tanks and Rams can be overcome using direct fluid loaded system, which avoids apex fluid supply tanks. Direct fluid loaded system using piston mechanism; FIG.SFD(DPS)-3 shows the vertical cross sectional view of a two units operated direct fluid loaded system using piston mechanism. In this system, the apex fluid supply tanks are eliminated and loading of Ram is taken care by direct entry of inflow fluid from source S. Construction: Referring to unit 1 of FIG.SED(DPS)-3, the system comprises of a bottom fluid collection tank Ei connected with exit line ELi fitted with exit valve EjV], extending upward to the required hydraulic lift head 'h", leading into conduction line CL delivering fluid to end point of discharge. The ratio of inner surface area of E) and inner cross sectional area of exit line EL, gives the mechanical advantage (fluid lift factor). Floating on the cushion fluid in Ei is the hydraulic fluid loading unit F, comprising of bottom Hollow Air float HjA fitted with piston rings (PS), to which upper intermediate linkage cylinder IML for storage of pre loaded weight / fluid to add density to the ram, and top placed fluid loading tank FT], the total vertical system (F,) being supported by guiders (Gd) for vertical movement. Drain pipe DP connects bottom of FT, extends downwards through IML, bottom hollow air float H, A and further down into E, fitted with drain valves DV. The fluid loading takes place under closed condition of drain valves DV and fluid release from FT_! takes place by opening of drain valves DV, downward via drain pipe DP. Placed above the level of FT, is the infeed line IF_t from fluid source S via header 'Hd' and control valve IV_! . The required pressure for displacement of entrapped fluid in Ei is enhanced by the total weight of Ram F_b pre stored fluid in IML and loaded fluid weight into FTi which is equivalent to displacement volume. Weight of Ram F] arid pre-stored fluid in IML are designed in consideration of frictional losses by piston and efficiency factor which is always higher than plunger mechanism based smart fluid displacement systems. The volume of hollow air float H,A has a bearing on reversible upward movement of Ram Fj. Similar conditions apply for unit 2 also. The need for very tall structures of bottom collection tanks and Rams can also be minimized , applying Brahmas' press principle. Working cycle: (Downward pressure stroke) Referring unit 1, under opened conditions of exit valve EiV) in exit line ELi, the fluid loading tank FT]is loaded with fluid falling via gravity from source S via infeed line IF) via opening of Infeed valve IV| causing additional weight to ram F_1; leading to disturbance to floating equilibrium of Fi in E] . The hydraulic pressure developed below Hi A, piston PS into Ei causes pressurized displacement of entrapped fluid in Ei via exit line ELi, delivered into conduction line CL leading to distained end use point. On reaching pre-determined down ward position of Fi in E,, fluid loading into FT^s stopped by controls.

Upward filling in stroke: Referring to unit 2, under closed conditions of exit valve E₂V₂ in exit line EL₂, the fluid from tank FT₂ is released into drain pipe DP by opening of drain valves DV, The falling fluid via gravity from FT₂ raises the level of entrapped fluid in E₂ , and simultaneous release of fluid from FT₂ resulting in loss of weight / density of F₂ cause upward buoyancy lift of F₂ in E₂ and continues till complete release of fluid from FT₂ into E₂. The volume of filled in fluid in E₂ is exactly equal to volume of fluid released from FT₂. During the upward filling stroke, infeed line IF₂ is closed. The alternate reciprocal movement of Rams F_\/ F₂ into E) E₂ results in continuous displacement of fluid from source S to higher head 'h' end use destination. The major advantages of direct fluid loaded piston system are 1) Simplicity of construction, reduction of weight of structures and parts, elimination of Apex fluid supply tanks. The disadvantage being efficiency losses due to friction, wear and tear of piston elements and difficulty of fabrication of bored inner cylinder surface and piston engineering on a larger scale. Direct fluid loaded system using plunger mechanism; FIG.SFD(DPL)-4 shows the vertical cross sectional view of a two units operated direct fluid loaded system using plunger mechanism. In this system, the apex fluid supply tanks are eliminated and loading of Ram is taken care by direct entry of inflow fluid from source S. Absence of piston elements lead to smoother working and improved efficiency of displacement.

Construction: Referring to unit 1 of FlG.SFD(DPL)-4, the system comprises of a bottom fluid collection tank Ei extending upwards till the distained delivery head level 'h' . Encircumferencing the top open portion of Ei is overflow trough unit OFTi, discharging out fluid from Ei falling into conduction line CL, discharging displaced fluid to distained end point. Floating on the cushion fluid in Ei is the hydraulic ram unit Fi comprising of bottom Hollow Air float HiA without piston elements, connected to upper intermediate linkage IML for storage of pre loaded weight / fluid to add density to the ram Fi, above which fluid loading tank FTi is placed. The Ram surface walls -further extend above the level of OFT_! as per stroke length criteria required. Ram F, reciprocates vertically via guiders (Gd). The fluid from source (S) enters the Ram via infeed line IF_1; top infeed line TIF connected to expandable hose EH, coupled to top surface of FT^ Slot space SP in Ram Fj takes care of free movement of F] against horizontal pipe line TIF without hindrance. Drain pipe DP fitted with drain valve DV connects bottom of FTi passes radially downward through IML, further into hollow air float ¾A and further extends into Ej . Drain pipe DP facilitates transport of fluid from FT, into Ei without interfering into IML stored fluid. The role of expandable hose EH is critical to have continuity of fluid flow from source S into the downward moving Ram. Bottom infeed line BIF can also be used for service operation. The hydraulic pressure required for rising of entrapped fluid in Ei via fluid exit slit FES / annular space between E, and F, is pre-designed based on material weight of Ram F,, pre-stored weight /fluid IML and loaded fluid in FT_]. Volume of displaced fluid from Ei is exactly equal to volume of fluid loaded into FTi from source S via TIF. Similar configuration is applicable to unit 2 also.

Working cycle: Downward pressure stroke; unit 1 position shows the downward pressure stroke of Ram F, into bottom collection tank Ei. When fluid is released down from source S via line IFl.TIF into FT_b through expandable hose EH, the floating buoyancy equilibrium of the Ram F, is disturbed by addition to the weight of F] causing descending downward movement, the immersion of F] in stored fluid in E, leading to displacement of equal volume of fluid loaded into FT] via annular space FES to overflow into OFT] and further by gravity flow via conduction line CL to destined end point of discharge. The discharge continues till reaching the predetermined point of H] A bottom into E, and stops on complete filling into FT_! by closing of fluid supply from source S.

Upward filling stroke : Referring to position of unit 2, the upward return stroke of Ram F₂ into bottom collection tank E₂ is enhanced by release of fluid from FTi downward via drain pipe DP, under opened state of drain valves DV reaching down into E₂. Simultaneous action of fluid release cum weight reduction of FT₂ and rising level of released fluid into E₂ causes upward buoyancy lift of F₂ into E₂. The upward reversal motion gets stopped on completion of release of fluid from FT₂ in to E₂ by closure of drain valves DV. The filled in volume in E₂ is equivalent to cleared up fluid volume from FT₂ which is also the displacement volume. The alternate up and down reciprocal movement of plunger Ram in bottom collection tank lead to continuous displacement of fed in fluid from source S to end use point at head of 'h'. The major advantages of direct fluid loaded system using plunger mechanism are 1) major reduction of friction and friction losses during displacement 2) avoiding of wear and tear of contact elements 3) smoother functioning 4) improved efficiency factor 5) simplicity of construction and reduction of components 6) Use of weight of flowing in fluid into systems without indirect loading externally. The major disadvantages being the increased structural costs of bottom collection tanks and increased length of Rams. The depth of bottom collection tanks need to be almost double compared to require fluid lift head 'h' apart from cushion fluid storage depth.

In case of direct fluid loaded piston or plunger mechanism applied Rams , the fluid released transfer from upper hydraulic fluid loading tank FT] to bottom collection tank i via hollow air float H)A can be configured as a single larger pipe or evenly spaced multiple small size pipe. Higher the dia of drain pipe DP faster will be the released of fluid from FTi

Direct fluid loading system using plunger mechanism with telescopic seal coupling : The main drawing FIG.SFD(DPL-TSC)-5 shows the vertical cross sectional view of a two units operated direct fluid loaded system using plunger mechanism with telescopic seal coupling placed between inner surface of bottom collection tank and outer surface of Ram . This is a modification of direct fluid loaded system using plunger mechanism by way of simplification and major reduction of structural heights.

Construction: Referring to unit 1 of FIG.SFD(DPL-TSC)-5, the system comprises of a bottom fluid collection tank Ei extending upwards just above the feed in line TIF from source S. Floating on the cushion fluid in Ei is the hydraulic fluid loading unit F, comprising of bottom Hollow Air float HiA without piston elements, connected to upper intermediate linkage IML for storage of pre loaded weight / fluid to add density to the ram, above which fluid loading tank FTi is placed. The top surface of FT] is closed and connected with expandable hose EH coupled to top infeed line TIF of infeed line IF] from source S. To the bottom of FTi is connected drain pipe DP fitted with drain valves DV at top and bottom which extends radially through intermediate linkage IML, hollow air float H]A and further below. The inner surface of bottom collection tank is fitted with upper inner orifice 10 to which fastened is a circular telescopic seal coupling / a flexible diaphragm , the bottom of which is fastened to outer orifice 00 of Ram F,. This telescopic seal coupling (TSC) blocks the fluid movement under pressure not to pass beyond level of 10 to move into the annular space area between Τχ/Εχ . During downward movement of Ram F] in Ej, the telescopic seal coupling (TSC) extends downwards and helps to prevent fluid entry above inner orifice 10 of E]. The hardness of outer surface of Telescopic seal coupling can be made harder to withstand pressure by metal discs / hard polymer discs embedment over the flexible diaphragm material surfaces. Connected to the inner body of the Ram are the exit lines ELi originating from bottom of Hi A fitted with control valve CV and extend upwards via hollow air float Hi A, IML, FTi and further leading to upper conduction line CL, and CL discharging fluid to end point destination. he widened width of Ej and Ram F] and the provision of inner exit lines EL, leading to conduction line CL facilitates scope of delivery of pressurized fluid through inner of the Ram Ei via opening of control valve CV instead of fluid raise via annular space (FES) between Fi and Ej. Thus reducing major structural height demands of Erand F] unlike direct fluid loaded plunger system. Conveniently the exit lines EL] can be attached to bottom collection tank Ei walls for simplification.

Working cycle: Downward pressure stroke; unit 1 position shows the downward pressure stroke of Ram F_| into bottom collection tank E]. When fluid is released down from source S via line IF], TIF into FT_h through expandable hose EH, the floating buoyancy equilibrium of the Ram F] is disturbed by addition to the weight of Fj causing descending downward movement. Drain valves DV being closed, the entrapped fluid in Ei below H[A is pressurized and as the telescopic seal coupling blocks the rise of fluid above its boundary, the control_, valves CV being opened, fluid raises through inner exit line EL] upwards on falls into conduction line CL, making fluid discharge to above head 'h' above infeed source level S. If the outer exit option line ELi can also applied as per case specific. The mechanical advantage is determined based on the ratio of surface area of cross section of ram both Hi A to total cross section of exit line ELi. As fluid is completely loaded into FTi from source S, infeed line IF, and drain valve DV are closed. By this time an equal volume of fluid from E_1; equivalent to loaded fluid volume in FT_! is discharged up into upper conduction line CL and delivered to end use point.

Upward filling stroke : Referring to position of unit 2, the upward return stroke of Ram F₂ into bottom collection tank E₂ is enhanced by release of fluid from FT] downward via drain pipe DP, under opened state of drain valves DV leading down into E₂. Simultaneous action of fluid release cum weight reduction of FT₂ and rising level of released fluid into E₂ causes upward buoyancy lift of F₂ into E₂. Under closed condition of control valve CV of exit lines EL₂. The upward reversal motion of F₂ gets stopped on completion of release of fluid from FT₂ into E₂ by closure of drain valves DV. The filled in volume in E₂ is equivalent to cleared up fluid volume from FT₂ which is also the displacement volume. The alternate up and down reciprocal movement of plunger Ram with telescopic seal coupling in bottom collection tank lead to continuous displacement of fed in fluid from source S to end use point at a head of 'h'. Apart from the major advantages of direct fluid loaded system using plunger mechanism, the telescopic seal coupling based direct plunger Rams facilitate drastic reduction of heights of vertical structures of bottom collection tanks and floating Rams. This system is the best featured version of smart fluid displacement systems and methods, by way of simplicity of construction, trouble free working, reduced structural costs and best working efficiency.

Indirect fluid loaded system with telescopic seal coupling mechanism: In case of indirect fluid loaded smart fluid displacement system, instead of plunger mechanism, the plunger with telescopic seal coupling can be effectively for major reduction of costs of vertical structure. Features of FIG.SFD(IPL)-2 for indirect fluid loading system part and FIG.SFD(DPL-TSC)-5 for plunger -with telescopic seal coupling can be incorporated. The exit line in this case can be preferably from exterior wall of bottom collection tank leading to conduction line CL and end point of discharge.

Salient Design Aspect Considerations:

Bottom collection Tank: The bottom collection tanks are designed to withstand heavy hydraulic pressure exerted by the Ram movement (piston or plunger or plunger with telescopic seal coupling ) by suitable reinforcement and support structures. Preferably the circular cross section configuration is used, compared to other geometrical shapes. The fluid exit lines ELi from bottom collection tank Ei are configured based on lift head ('h'), hydraulic pressure stability during pressure stroke , total cross sectional area based on flow Q sec rate as single or multiple. Size of bottom collection tank volume (cross sectional geometry, cross sectional area - width / length, height, cushion fluid support volume, stroke volume and length of hydraulic fluid loading unit, option on piston or plunger or plunger with telescopic seal coupling mechanism. Discharge volume of fluid per stroke dependent factor on volume and height of hollow air float, upper fluid loading tank, retention volume (Qsec multiplied by retention time) in bottom collection tank, hydraulic head of displacement and density of fluid handled. The number of units used for displacement applications depends on Q sec flow rate, emergency / service units, construction costs etc. The direct fluid loaded plunger based smart fluid displacement systems offer lowest friction. The direct fluid loaded smart fluid displacement system applying plunger with telescopic seal coupling (TSC) features lowest construction costs of structure.

Hollow Air Float: The hollow air float component is a critical feature of the invention, being responsible for the automatic antigravity reversal motion on release of upper loaded fluid into bottom collection tank. It is a sealed housing filled with air at normal atmospheric pressure. The construction material can be of Polyvinyl chloride (PVC), High Density Polyethylene (HDPE), Fibre Reinforced plastic (FRP) or Steel or suitable other polymeric material (poly carbonates etc), non corrosive surface coated (to avoid saline water corrosivity). The hollow air float is to be attached to the bottom piston and upper vertical pole unit via proper holding mechanisms. In order to bear the compression stress during downward loading stroke and relief stress during upward unloading stroke, the hollow air float needs external metal plate reinforcement or combined external and internal reinforcement. This is mainly intended to protect bursting / cracking out of hollow air float unit from compressive stress as well as relief stress during operation. The hollow air floats can also be of a multiple (double, Triple or multiple) three dimensional units stacked and bound as per requirement. The internal / external surface support reinforcements, thickness of hollow air float, specific volume, weight are based on compressive pressure load on hollow air float apart from total fluid head weight of the unit, which are decisive factors for expulsion of displaced fluid out from bottom collection tank. The volume of hollow air float unit bears a relation to that of the volume equivalent / combined weight of the ram (material weight of ram, weight of load in IML and weight of fluid loaded in fluid loading tank) so that, reversal buoyancy lift of ram is feasible. Minimum weight, maximum strength, stress and load bearing capacity of the total structure is to be engineered. The piston elements can be single layer or multi layers to give balance of vertical movement. Coming to the piston material part, it can be chosen from vast raw materials like rubber, synthetic rubber, polyurethane, polyamide, polyester, polypropylene etc. Corrosion resistance, hardness, dimensional stability, abrasion resistance, non cracking tendency, strength, wear and tear life are to be taken into consideration.

Intermediate linkage: The intermediate linkage IML connects hollow air float Hi A and bottom of hydraulic fluid loading tank FT] is a common feature of indirect or direct fluid loaded smart fluid displacement systems. It also houses the dead weight / standard fluid storage meant for increasing the density of the Ram during the downward movement. The Hydraulic fluid loading tank FTj is designed in proportional volume of displacement fluid (weight w) from bottom collection tank during the Rams (Fj)downward pressure stroke. Energy requirement of displacement quantity fluid from bottom collection tank during pressure stroke to a head of 'h' for a given efficiency of pumping (η) by normal pumping is as followed.

Equation : 1

Weight of water(w) x 9.81(gravity) x head(hi)

Pumping energy required in Newton meter (Nm) =

Efficiency of pumping (η)

It is obvious that a particular charge volume of fluid need to be displaced to a higher head during each stroke by the action of the Ram and bottom collection tank. This is a achieved by the combined action of components of the Ram(F_!) during the pressure stroke which is enhanced by increasing the density of Ram during downward pressure stroke. The factors involved in the energy exerted by the Ram on the entrapped fluid surface is designed by the formula Equation :2 (Based on direct plunger mechanism)

Wj+ w₂ +w x Stroke length of Ram (h₂)

Work done on Ram for a given displaced fluid = Nm weight (w) to a head of 'h^in Newton Meters Efficiency of Ram action (η₂)

(Dead weight of Ram(W_[) , Standard Weight of fluid in IML (w₂), Weight of fluid loaded in FT_! (w))

By equating equations 1 & 2, based on the dead weight of Ram, Standard weight of fluid in IML, the effective stroke length of h₂ can be determined. The right hand side factors of the equation 2, can be balanced by choosing any two factors and finding the third factor equating to equation 1. In case of the plunger systems (direct or indirect fluid loading), the efficiency of Ram pressurization is estimated higher due to the absence of piston elements and hence is best preferred. In case of Piston system ( direct or indirect fluid loading), the efficiency is estimated much lower than plunger due to friction contact of piston surface and bottom collection tank inner surfaces. In order to compensate of the frictional loses , the dead weight of the Ram, quantity of fluid loaded in IML in consideration of reduced efficiency of the piston Ram can be proportionately increased compared to plunger system. The plunger system is the best preferred mechanism due to the practical limitations of such a large area piston. Compared to direct plunger, the direct plunger with telescopic sealed coupling TSC is expected to give superior efficiency due to ease of operation, reduction of structural costs, construction material and simplicity etc. The fluid loading displacement by immersion of the Ram in bottom collection tank, confirms to Archimedes principle

• When a body floats on water, it displaces equivalent weight of water.

• When a body sinks in water it displaces equivalent volume of water.

The -hydraulic pressure exerted over the entrapped surface fluid into the bottom collection tank is equalent to hydraulic pressure developed in the exit line (EL in case of direct loading systems or fluid exit slit (FES) gap between bottom collection tank inner surface and outer surface of the Ram, which confirms Pascal's Law of equilibrium of pressure in closed hydraulic circuit systems. ^'Excepting for the energy requirement of operation of valves and controls, the input energy for displacement is based on mere forces of nature (dead weight, acceleration due to gravity and weight of fluid loaded into fluid loading tank FTi). Gravitational energy supported by flowing in fluid weight are instrumental for downward automatic movement of the Ram. The reversal anti-gravity upward movement of the Ram is enhanced by mere fluid weight released into the system, the raising level of fluid in Bottom collection tank E^'i during filling stroke, the buoyancy reversal lift of hollow air float are instrumental in natural reverse movement of the Ram for upward stroke. This novel reversal automatic movement of the Ram forms the heart of energy source of smart fluid displacement systems and methods. Such a phenomenon happening in the operation of controlled lowering (immersion) and upward lifting of sub-marine ships in open sea is a non-obvious energy source. Critically in this case, a sub-marine equivalent floating Ram is placed in closed well (bottom collection tank) compared to open sea and its descending pressure energy is utilized. Direct fluid loading systems are much efficient than indirect fluid loading systems due to the extra pumping energy requirement between FT) to G]. In case of direct fluid loaded systems, the plunger mechanism gives better efficiency than piston mechanism. The ultimate superior system is the direct plunger based system using telescopic sealed coupling mechanism and hence it is the most preferred system amongst the six systems disclosed in this invention of smart fluid displacement systems and methods. Guiders : Towards vertical unshattered movement of the ram into bottom collection tanks, the vertical guiding mechanisms are very crucial. Guiders fixed to body of bottom collection tank are grounded fixers can be wheels or balls or curved studs made of abrasion resistance materials guided by tracks or grooves or rack and pinion systems. The friction aspects of the guider should also be bare minimum.

Corrosion proof materials for fluid contact surfaces, pipes, valves need important considerations while handling saline and effluent waters.

II. Innovative applications of Smart Fluid Displacement systems and methods By virtue of the extensive advantages of smart fluid displacement systems and methods, multitude of innovative applications are feasible, which are described in detail in the following applications in relation to the drawings. The broader classifications of innovative applications in the fluid related dynamic systems are, II a) Continuous Hydro power generation application II b) Ship propulsion application II c) Pumping / Mass water transport application II d) Hydraulic machines applications like Cranes.

Ila) Innovative applications of Smart Fluid Displacement Systems and Methods Applications for continuous hydro power generation Whereas, the indirect piston, plunger and direct piston type rams are less efficient and structural cost involving, even though being applicable, preferably the direct plunger and direct plunger with telescopic seal coupling mechanism are best preferred' for hydro power application. The smart fluid displacement systems and methods fluid applications to hydro power plants to instantly return water back to source after power generation. FIG.SFD(HP AP)-6 shows the vertical cut view of combined configuration of 1) a Dam based hydro power plant with natural head / pumped storage hydro power plant having tail race. 2) Artificially from downward high head formed new class hydro power plant, by using direct plunger based smart fluid displacement system units. The hydro power plant unit consists of fluid intake line IL, connected with fish protection device FP, leading to an intermediate forebay IFB, the penstock PS to take fluid downwards, leading to turbine unit TU coupled with alternator. By increasing the penstock head for a given Q sec flow rate of water, the power generated can be proportionately increased based on the formula.

Power generated = Density of water(p) x Acceleration due to gravity x Q sec (m³ /sec) x Head (mtrs) x in Kilo Watts . Efficiency^)

Water is taken from source S, used for power generation and is let down into draft tube DT by gravity next to the draft tube is the downward infeed line leading to plunger based smart fluid displacement system via infeed line IF and header Hd. The alternate reciprocal action of the ram Ft and F₂ lead to delivery of collected water from hydro power plant, to uphead overflow trough and water is delivered back to forebay or at source S via conduction line CL. In a similar way, in case of existing normal head based hydro power plant, the water after power generation can be let down into the plunger based smart fluid displacement system unit, pressurized and delivered back to source S from OFT) and conduction line CL. Thus the existing dam / barrage / run of river / pumped storage hydro power plants can be made to continuously working mode using smart fluid displacement system and methods, making best user of recycled storage water in dam / barrage without being lost to sea. FIG.SFD(HP AP)-7 shows the application of direct fluid loaded smart fluid displacement system using telescopic seal coupling (TSC). As mentioned in the previous application based direct plunger, the application scope of continuous mode of running of existing normal head based Dam / Barrage / run of river / pumped storage hydro power plants as well as artificially increased down head penstock based hydro power plants, with the advantage of minimized structural construction costs.

FIG.SFD(HP AP)-8 a shows the vertical cut view of hydro power plants constructed within reservoir (Dam / barrage / lake / sea etc) applying direct fluid loaded smart fluid displacement system using plunger mechanism. Such schemes are applicable where land areas are insufficient or unsuited for power plant construction. Places like Mid Sea, Island areas etc. can be preferably built with this type of within reservoir hydro power plants applying smart fluid displacement systems. Instead of permanent under water structures, the support structures of the hydro power plant can be constructed on a floating ring structure also. Water is withdrawn via a forebay line IFB and extraction lines EL/2 taken downwards for the required fluid head upto turbine unit TU for power generation, the falling water from turbine is displaced uphead or downhead back to source by alternate downward stroke of respective hydraulic fluid loading ram units (F^) in the respective bottom collection tank (E₁/E₂), the pressurized .water via annular space FES, over flow trough (OFT] / OFT₂) is delivered back to source via conduction line CL. Such structures find use in offshore explorations, marine life research stations etc. and reduces fuel consumption to a great extent saves environment.

FIG.SFD(HP AP)-9 shows the vertical cut view of the hydro power plants constructed within reservoir (Dam / barrage / lake / sea etc) applying direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling mechanism. In this case, water is withdrawn via a forebay line IFB & extraction line E)/EL₂ taken downwards for the required fluid head upto turbine unit TU, the falling water from turbine unit is alternatively conducted into bottom collection tank E_\/E₂, the downward plunger action of F]/ F₂ displaces entrapped fluid in E₁/E₂ via fluid exit slit (FES), overflow trough (OFTi/OFT₂) and conducted back to source via conduction line (CL) via exit line ELi/EL₂ either as over head discharge above reservoir level via conduction line CL or as bottom delivery into the reservoir via bottom exit lines (BEL). The structural costs of the direct plunger with telescopic seal coupling are at the minimum most.

Raised head tower based, Dam less continuous hydro power plants applying smart fluid displacement systems. FIG.SFD(HP AP)-10 shows the configuration of a raised head tower based, Dam less continuous hydro power plant applying direct fluid loaded smart fluid displacement system using plunger mechanism. In this case, water from any source S (Dam / Barrage / Run of river, pumped storage dam, running rivers, Canals, Lakes, large scale water storage points, sewage effluent treatment plants, sea coasts) is drawn from source via intake line IL, intermediate fore bay IFB, conducted down head by gravity flow alternately into floating rams Fi / F₂ based in bottom collection tank Ei / E₂, the pressurization causes pre stored fluid in Ei / E₂ to get discharged fluid up head via fluid exit slit FES into high head tower (OT), thus forming a high head (h) above fluid source level above the ground as per requirement. On filing of the high head tank (OT), the water from OT is released via penstock (C/3), used for hydro power generation from turbine unit TU, coupled to the alternator, and the free falling water from draft tube (DT) is conducted back to source (S) intermediate fore bay (IFB) or as per convenience. The Q sec flow rate of withdrawal water from source (S) flowing rate of water into smart fluid displacement system units, up head discharge rate out from smart fluid displacement system and out put Q sec from OT for power generation and discharge rate back to intermediate falling IFB are kept equal by control valves.The novel feature of this type of recycled hydro power plant is that, the water into the flow circuit is responsible for^' power generation, without the need for Dam / Barrage, thus saving major civil costs and saves environment / ecological disasters of hydro power plants. FIG.SFD(HP AP)-11 shows the raised head tower based hydro power plant applying direct fluid loaded smart fluid displacement system using telescopic seal coupling (TSC) mechanism. The construction and working are similar to the previous description excepting for simplification of structures and up head discharge from smart fluid displacement system via exit lines EL to conduction line CL leading to up high head tower OT.

Summary of advantages of application of smart fluid displacement systems to hydro power plant : The major advantages are 1) continuous scope of operation of existing power plants, 2) salvation of drawbacks of existing hydro power generation technologies and facilitation of a) Instant water recycling back to source after power generation without direct electricity or fuel power) (b) capability to use any water source Dam / Barrage Run of river, canals, lakes, mass water discharge points, sewage / effluent treatment plants, sea coasts by artificial down head /up head formation, (c) Avoiding Dam / Barrages, save major civil costs by simplification, preserving environmental / eco systems disasters of hydro power plants (d) shortest gestation periods of hydro power projects (e) application to base / peak load flexible services (f) Minimization of hydro power costs (g) Retro fitting of existing hydro, conversion scope of Thermal (Coal, Gas, Fuel, Biomass), Nuclear and even wind mill prime mover to equal capacity hydro prime movers without losing generation value (h) Site flexibility to all geographies (i) facilitation of hydro power as a permanent sustainable energy source for the long term future of plant earth , solving power cuts, crisis and climate change issues.

II b) Innovative applications of smart fluid displacement systems and methods for pumping uses.

Pumping of water from extraction source to distant destinations rPumping is a very essential activity in industrial, agricultural, power generation, mass water transport for domestic and other services in fluid handling. Modern pump systems are efficiency based which are run by prime mover energy sources like, manual, electrical, fuel based IC engines, wind, solar etc. The innovative applications of Smart Fluid Displacement Systems are discussed, which eliminate the use of direct electric power and achieve pumping action by fluid behavior to gravity and antigravity phenomenon.

Application of smart fluid displacement systems and methods for mass water transport :The indirect / direct fluid loaded systems of smart fluid displacement systems using piston or plunger or plunger with telescopic seal coupling mechanisms are best applicable to mass water pumping without direct electrical or fuel energy. The direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling is given a demonstration of mass water transport applications from source to end use points like building tops, over head tanks meant fof distance transport of water.

Direct fluid loaded smart fluid displacement systems using plunger mechanism: FIG.SFD (PMP AP) -13 shows the vertical cut view of a direct fluid loaded smart fluid displacement system using plunger mechanism meant for supply of water form source to end use destinations like building tops or high head towers meant for local or transport to distance sources using the high head advantage. From source (S) (River or Canal, or lake or water point), water flows in by gravity via a fore bay FB, down head into header (hd) and is taken to unit I and unit II of direct fluid loaded smart fluid displacement systems using plunger with telescopic seal coupling. The alternate loading of in feed water from source (S) into the ram Έ_\ results in fluid displacement rising via fluid exit slit (FES), overflow trough (OFT,) further via conduction line CL into either building top (MSB), water storage tanks (OHTi) or into a high head level above the source (S). From high head tower HHTi water can be transported to remote distance collection tanks either as bottom delivery line BL or top delivery line TDL and further taken for municipal / irrigation supplies. The fluid lift head 'ht' is kept in such a way to overcome hydraulic head losses, friction etc in the conduction pipe.

Direct fluid loaded Smart Fluid Displacement system using plunger with telescopic seal coupling mechanism: FIG.SFD(PMP AP)-14 shows the vertical configuration of a direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling mechanism meant for fluid displacement into building top overhead tank (OHTj) or high head tank HHT] meant for transport of water to remote distance as bottom delivery line (BDL) or top delivery line (TDL). The only difference here is that, the displacement from exit line EL into conduction line CL due to the action of ram F)/F₂ in Ei E₂ in an alternate manner. By way of simplicity of construction structures the telescopic seal coupling (TSC) based direct plunger is best preferred. Flood / Rain water diversion to remote distance above level walled storage reservoir using smart fluid displacement, system: Indirect or direct loaded fluid displacement system using piston or plunger or plunger with telescopic seal coupling mechanisms (preferably the direct plunger or direct plunger with telescopic seal Coupling) can be advantageously used for flood / rain water diversions to remote distance storage reservoirs without using direct electricity or fuel power. As shown in FIG.SFD(PMP AP)-15, during flood / rainy seasons, surplus flow water from source (S), in diverted to an intermediate fore bay (IFB) via infeed line IF, further down into header (Hd), and is fed via gravity into the plunger based rams Fi/F₂ operating in bottom collection tanks E|/E₂. The water during down ward pressure stroke of the ram is delivered uphead via exit line s ELi EL₂ falls into high head tank HHT. The stored water from high head tank HHT, is further conducted to remote distance reservoirs WSR, /WSR₂ or others via gravity flow through respective conduction lines CL. Wall WL is constructed above land, surrounding lake / pond to the required height so as to increase the storage space of the reservoir for long term use and thus system avoid overflow out discharges out sea without any use to land consumers. Absence of direct electricity / fuel power makes the applications more sustainable to solve the water needs of the society and ensures water for all anywhere.

Application of Smart fluid displacement systems for Rainwater Harvesting in open Seas or larger lakes during rainy seasons :FIG.SFD (PMP AP)-16 shows the vertical cut view of an open sea rainwater harvesting system, attached with direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling mechanism. It is a well known fact that 90% of fresh water rain falls back into the sea, which is a major fresh water resource loss to the planet. Cost of construction of dams, limited land area availability restricts, water storage option on land sources. The smart fluid displacement system components like, hollow air float, and hydraulic fluid loading unit can be conveniently used up for rain water harvesting in open seas.

As per FIG.SFD(PMP AP)-16, individual hydraulic fluid loading tanks FT_1; FT₂, FT₃...etc are kept on floating over fluid reservoir (S) by means of closed hollow air float units (H)A, H₂A, H₃A, etc). Similarly different parallel rows can also be formed. As shown in FIG.SFD (PMP AP)-16 all the bottoms of floating units (FT], FT₂,..etc) are connected by bottom collection pipes (BCP) with suitable flexible pipes to compensate oscillation movements within sea by waves. The inter connection of floating tanks by bottom connection pipe linkage, enhances constant level of rain water in all floating tanks. In order to restrict separation movements of floating tanks mutual fastening fixers between floating tanks can be provided. As the top of these open tanks are kept operied, during rain, fresh water falls into open floating tanks (FT,, FT₂,...etc) the fluid loading of which causes immersion of entire net work of floating tanks. The immersion is permissible upto maximum holding volume beyond which the contained water is allowed to over flow out. Extra collector hoppers arrangements in order to achieve larger rain water collection area is also possible. (HPR - shown in dotted lines). As per requirement, the fresh water from these floating storages can be conducted to the end use destinations via application of any one of the direct or indirect fluid loading smart fluid displacement systems ( piston or plunger or plunger with telescopic seal coupling mechanisms) via conduction lines. As pumping out from floating tanks takes place, the progressive emptying out of fluid results in upward antigravity lifting of floating storage tanks can be left to raise up. The falling water from rain water collection tanks can be transported to land costal collection reservoirs / Islands either as over head delivery or under head delivery from floating smart fluid displacement unit, which displace charged rain water into the bottom collection tanks due to the downward stroke of the ram Fj / F₂. This is one of the effective applications of smart fluid displacement systems to solve fresh water needs of the planet, mainly in water scarce coastal lands and Islands.

II c) Innovative applications of smart fluid displacement systems and methods for ship propulsion

By applying the construction principle of within reservoir power plants, the invention can be made usable at aquatic/marine vessels for deriving propulsion energy for movement, as well as meeting electrical power demands of the ship during movement as well as at stoppages. Excluding running rivers, the invention is adaptable to vessels traveling in stagnant aquatic sources like Seas, Bays, Oceans and Lakes.

Application of plunger with telescopic seal coupling mechanism based direct fluid loaded smart fluid displacement systems to bottom penstock hydro ship propulsion : FIG.SFD (SH AP)-17 shows the vertical cut view of a direct fluid loaded smart fluid displacement system applied plunger with telescopic seal coupling mechanism using weight of falling water applied hydro ship. The main ship assembly (MS), bottom turbine systems, fluid conduction pipes to downhead placed smart fluid displacement system (using plunger with telescopic seal coupling mechanism) attached to sub-ship (SS) with protection housing (PH₂). This hydro ship is comprised of two main units I & II. Unit I is made of main ship body (M.S) attached to bottom hydro turbine unit. Unit II is made of intermediate water conduction from unit I to smart fluid displacement system encompassed in a second ship float (SSF). Unit I and unit II are linked by flexible chain or rope linkage (LCi, LC₂, LC₃, LC₄) just for the reason to avoid the up and down oscillation of unit II, which can disturb the balance of unit I. . As the infeed water in turbine unit drives the turbine which inturn drives the propulsion system of the main ship (unit I), unit II collects and discharges out water outlet from hydro turbines (T_b T₂) back into source. As per FIG.SFD(SH AP)-17, the main ship body of unit I, houses the bottom down head hydro power turbine unit, which is attached to the bottom by means of fish protection covers FPi, leading to horizontal extraction line 2 via gate valve Gi with handle. Line 2 takes down a downward bend as Penstock (3), which in turn leads to waterjet end which moves the bottom turbine unit Di . These hydro turbines can be of a single configuration or double turbine configuration as demonstrated in this description or of manifold as per design criteria. As per FIG.SFD(SH AP)-17, the down head turbine units Dj, D₂ operate from two bottom sides of the ship, at a hydraulic head level 'hi 'which in turn is taken to the respective gear boxes GBi and GB₂ via connecting shafts CST! and CST₂. The gear boxes can deliver the drive either to both side fitted paddle wheels PW_b PW₂ or drive connection shafts CS,, CS₂ which in turn give drive to bottom base propellers (BPPL, and BPPL₂). The efficiency of paddle wheels being very low, as per modern propulsion systems, the back propeller system is preferred. On opening of gate G,, water from reservoir flows in via horizontal line (2) and penstock (3) into individual bottom turbine units D, and D₂. The turbines T] and T₂ in turn will run the propulsion drive (paddle wheels or back propellers) via mechanical or electrical transfer drives. The mechanical motion can also be utilized for lighting and other service needs of ship by proper manipulation (line generators). Thus the hydro power generation system is responsible for the propulsion and other energy needs of the ship. The task of turbine outlet fluid disposal back into reservoir, by means of effective pumping out system applying good deal of mechanical advantage, facilitated by fluid behaviour, gravity and antigravity forces is provided by smart fluid displacement systems. The outlet water from turbines Ti and T₂ is conducted via draft tubes DT₍ and DT₂ ending in a common header (Hd) which in turn is connected to inner flexible hose (IFH), ending in inlet valve line to bottom collection tanks or E₂ via valves E₁V₁ and E₂V₂. To put up in a simplified manner, the turbine outlet water from Ti and T₂ is alternatively allowed to be accumulated down head in E) and E₂,which in turn is cleared out by means of alternate downward stroke of hydraulic fluid loading unit. On opening of valve Gj/G₂ in main ship , the flowing water downhead runs turbines T_!&T₂ ( leading to main propulsion ship drive systems. The falling water from T]&T₂ conducted downhead via drafts tube (DTi/DT₂) is taken to sub-ship fixed plunger based smart fluid displacement system. The alternate plunger action of Fi/F₂ in Ei/E₂ results in fluid displacement from Ej/E₂ upward via fluid exit line EL (by over head discharge or bottom head discharge back to sea / reservoir). Amidst Indirect / direct fluid loaded systems using piston or plunger or plunger with telescopic seal coupling, the direct fluid loaded plunger with telescopic seal coupling is best suited.

Smart fluid displacement systems and methods with telescopic seal coupling mechanism applied Hydro electric ship using raised tower principle: FIG.SFD(SH AP)-18 shows the vertical cut view configuration of a main ship (MS) being supplied with propulsion electrical energy from attached sub-ship with generator (SSG) using raising up level based direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling mechanism. The risks of hydro turbine provision below the main ship body, is the limitation of movement of the ship restricted to deep waters, risk of damage to bottom turbine & sub ship bottom assembled by underwater rocks or wreckages. The dynamic balancing again is a constrain. This category significantly facilitates simplicity of main ship (MS) and sub-ship (SSG) constructions, as well as conversion scope of existing ships with least modification by way of provision of sub-ship with generator attachment (capacity based on main ship capacity plus sub-ship weight) and conversion of fuel propelled IC engines into electrical motors of suitable capacity or still maintaining the IC engines partly for emergency operational services apart from major adaptation to electrical motor based propulsion.

Construction: FIG.SFD(SH AP)-18 shows the vertical cut view of the main ship (MS) being supplied with propulsion electrical energy from attached sub-ship with generator (SSG) using raising up level based direct fluid loaded smart fluid displacement system applying plunger with telescopic seal coupling mechanism. The main ship with capacity load (LD) derives electrical supply from generator (GNi & GN₂) placed at sup-ship via transfer lines (TL). Electrical conduction unit (ECU) in main ship (MS) via conversion gadgets like transformer feeds electricity to run the main propulsion motor (M) which is linked to gear box (GB). Mechanical drive from (gear or hydraulic drives) gear box is used to run the bottom placed propellers BPPLi & BPPL₂ or more numbers as per construction design. The sub-ship assembly with generator (SSG) is constructed to the body of air float (FL), bottom protection housing for direct fluid loaded smart fluid displacement unit, primary generator (GN₂), fluid infeed lines from reservoir (S) and conduction lines etc. The pressurized fluid from direct fluid loaded smart fluid displacement system is transferred to high head placed vertical tower (VT) with top overhead tank (OT). Fluid from source (S) via fish protection device (FP) via gate control (g,) is conducted via line B/2 into the prime turbine unit (DO which houses turbine (Ti) mechanically connected to electrical generator (GNi). The falling water from turbine (Tj) falls into draft tube (DT), taken via bottom conduction line (CLi) leading to downward placed header (hd). From header (hd), fluid is alternately transferred to the direct fluid loaded smart fluid displacement units FpE_! and F₂-E₂ via respective lines L|, L₂ fitted with valves E^ and E₂V₂. Each of F]-E_! and F₂-E₂ smart fluid displacement units are comprised of hydraulic fluid loading tanks FT] / FT₂, hollow air floats HiA / H₂A moving into respective bottom collection tanks Ei or E₂. Drain pipes (DP) in F_]/F₂ renders transfer of fluid from FTVFT₂ into Ei/E₂ and also enhancing anti-gravity upward movement of F[/F₂ in Ei E₂. The pressurized fluid into E|/E₂ can be lifted up via exit lines Iai/Ia₂ through exit valves EIVi EIV₂ leading to uphead placed vertical tower fitted with top overhead tank (OT) during the downward pressurization stroke of Fi in Ei or F₂ in E₂. The top face of OT is kept closed by top lid to avoid fluid splashing out during movement. Fluid from OT can be conducted downhead either via neck point (N placed top line (TL) or bottom line C₂/3 fitted at bottom point in OT fitted with bottom point valve (BPV). Conduction lines C]/3 or C₂/3 form equallent hydraulic head (ht). As per design criteria, fluid can be filled only upto neck point (Ni) to take up (downward conduction via top line (TL), valve TPV and penstock Ci/3) or of full volume level in total of OT, downward conduction via line C₂/3 and valve BPV). Both lines Cj/3 and C₂/3 lead downward into turbine unit (D₂) fitted with turbine (T₂) which is linked to second electricity generator (GN₂). The used up water from turbine (T₂) is taken downwards via draft tube (DT₂) to exit lines (EL) delivering fluid back into reservoir source (S) by gravity. The electrical output from GN] and GN₂ can be transferred to the main ship electrical connection unit (ECU) via transfer lines (TL) with suitable protection and flexible coilages. The total output of GNi & GN₂ can be effectively utilized for all operations involved in main ship and second ship with generator towards propulsion, lighting, operating of pumps and other utilities which are based on design of construction. Protection housing (PH) takes care of all bottom placed working units below float (FL) the uphead placed fluid tanks OT, turbine unit, generator and fluid conduction lines are all properly fixed to the sub-ship (SSG) by suitable foundation and supports. The main ship and sub-ship are linked by means of flexible chains or ropes LCi, LC₃ on top and LC₂, LC at bottom. This flexible linkage restricts oscillations of fluid movement restricted to sub-ship (SSG) only. There is possibility of placing the OT unit at the main ship based on load balance criteria. The vertical tank (OT) can be made conically shaped, to prevent water tumbling within the tower during in ship's movement.

Working : Falling water from Turbine T| coupled to Generator GN] of sub ship is conducted via gravity into bottom placed smart fluid displacement systems applying plunger with telescopic seal coupling mechanism. The alternate reciprocal movement of floating ram F]/F₂ in bottom collection tanks Ei/E₂ leads to pressurized delivery of water from E_t/E₂ via exit lines EL_\/ EL₂ upward into overhead tank OT, thus forming a hydraulic head. As OT in filled up, water from OT is allowed to fall down forming a head of 'h' to run bottom placed turbine T₂ and falls back into source (R). Turbine T₂ being coupled to generator GN₂, the hydro power produced and converted to electrical energy, which inturn can run the bottom placed electrical motor in mainship (MS), the drive is further connected to gearbox (GB) and propellers.

Application of plunger with Telescopic seal coupling based Smart fluid displacement systems and methods using plunger with telescopic seal coupling mechanisms applicable to underwater immersible Ships : FIG.SFD(SH AP)-19 shows the vertical cut view of a direct fluid loaded smart fluid displacement system using plunger with telescopic seal coupling mechanism applied without under water apex fluid supply tank using piston / piston cum plunger mechanisms applied underwater immersible ships. Construction : The bottom, placed hydro turbine propulsion is applicable to underwater immersible ship propulsion, meant for underwater explorations / marine life study vessels, submarines etc. The overall system comprises of an immersible ship (IMS), which is connected to downhead placed smart fluid displacement unit housed by protection housing PH. Connected to the open end of downhead placed smart fluid displacement system is a vertical cable pipe housing (CPH) / trunk, to which extents a spindle (SP), supporting coils of air hose (AH_]) meant for air supply to bottom protection housing (PH) as well to outershell of main ship IMS. Cable pipe housing (CPH) is connected by a flexible trunk (FLT) ( leak proof into CPH), which is connected to cable support float (CSF). Air hose line (AH₂) is meant for air supply to the shell of IMS. Where as cable support float. (CSF) always remain at top of water by floating, the coils of Air Hose (AH]) can be extended as per downward head (hd) immersible ship (IMS) position under water. The whole assembly is connected in by suitable linkage, such that when ship (IMS) moves, protection housing PH, cable support float CSF also moves along with. The immersion ship (IMS) is comprised of outer shells (OS) and inner shell (IS). The water space (WS) between OS & IS is responsible for downward immersion of immersible ship (IMS) by water loading and expulsion of water by air entry, which causes upward lift of IMS due to reduction of density. The inner space surrounded by inner shell (IS) houses all controls, drive, crew movement and other activities. Entry valve (EV) is used for fluid entry and exit valve (EXV) is responsible for fluid expulsion. Connected to the front end of IMS are single or double or higher number of fluid entry lines B/2 via gate valve g,, g₂, etc., and fish protection devices FV], FV₂..etc, line B/2 takes downward bend leading to turbines units Di,D₂ etc comprised of turbines T], T₂, etc which in turn are linked to the connection shafts CS_{1 ;} CS₂,etc. giving drive to bottom placed propellers BPPLi, BPPL₂, etc. via gear box (GB). The outlet water from turbines Ti, T₂ is taken via line IF through outlet valve (OV) into downhead header (hd) connected to downhead placed floating rams Fi & F₂ via respective valves E₁V₁& E₂V₂. Conduction line (CL) is protected by outer piping (OP) linking IMS bottom and protection housing (PH) of downhead placed smart fluid displacement system. Water falling from turbine via 'hd' is alternately let down into FT) or FT₂ via control valves EjVi or E₂V₂, the fluid loading of which expels pre-loaded fluid in bottom collection tanks Ei or E₂ via respective exit valves ΕΓνΊ, EIV₂ to be expelled out by bottom exit line (lb). The required atmospheric air pressure is taken care by air hose cable (AH)) held in support by CPH, FLT and CSF floating unit. The main ship IMS and all the fluid expulsion units PH, CPH are linked by fixers (FX) at suitable points. The study state dynamic motion of the whole unit can be a balanced design feature. As the main ship IMS moves downward into reservoir (R), the increasing head (hd) takes care of fluid pressure in the reservoir and turbine force increases with increase in downward head (hd). The mutual weight aspects of all components, propulsion force requirement and other energy needs of the ship can be suitably incorporated in the design criteria.

Working : When fluid is loaded into the water space (WS) by opening of entry valve (EV) (exit valve (EXV) closed), the main ship (IMS) and attached components PH, CPH also moves down upto the workable limit downhead (hd) at which stage valve EV is closed. As gate valves gi/g₂ are opened, water from reservoir (R) enters into line B/2 by hydraulic fluid pressure, being conducted into turbine units Di/D_2> making the turbines Ti/T₂ rotate. The rotation of T)/T₂ is converted by gear box (GB) so as to rotate the bottom placed propellers BPPL_t/BPPL₂ which causes the forward propulsion of IMS below the surface of reservoir (R). The falling out fluid from turbines is cleared away back into the reservoir (R) by the alternate self pumping pressurization of Fi(FTi-HiA) and F₂ (FT₂-H₂A) in E]/E₂ respectively via exit line (Ib),facilitated by the action of plunger with Telescopic seal coupling. The air hose line (AHi) flexibly suspended from cable support float (CSF) takes care of atmospheric air pressure requirement into protection housing (PH). When IMS needs to be taken to the reservoir surface, fluid from water space (WS) can be replaced by air entry lifting the whole assembly upwards. Suitably the tprbine power can be utilized for air replacement in the WS by disconnection of propulsion drive. All other sensors, rives, safety and emergency provisions are applicable as per similar immersible vessels. The second Air hose line AH₂ leading to outer shell (OS) can be used to release water from immersible Ship IMS, by gravity into conduction line CL, to be delivered under pressure -into sea using bottom placed smart fluid displacement system held in protection housing PH. This eliminates need for used of compressed air to expel water from submarine to lift up.

Propulsion power calculation of the ship : Assuming the IC engine capacity of 2000 kW for a ship of 50000 tonnes, as per general consumption levels, 25000 liters of oil will be consumed per day. This power is meant for main ship body and cargo load, which is the total carrying capacity of 50000 tonnes. Based on such Kw assumption and total tonnage of ship, the hydro electric equivalent rating of propulsion power can be calculated, taking into consideration of additional pulling loads of sub ship fitted with smart fluid displacement system, bottom hydro turbine unit, joint trunks etc.

II d) Innovative applications of smart fluid displacement systems and methods for hydraulic machines. Cranes / Lever moving devices

Free floating indirect fluid loaded smart fluid displacement system with apex fluid supply tank applicable for Cranes / Lever moving devices: FIG.SFD(HDL AP)-20 show the vertical cut view of a free floating indirect fluid loaded Smart fluid displacement system with out apex fluid supply tank applicable for Cranes / Lever moving device, applicable in harbours, coastal dredging, ship loading and unloading operations. Unlike piston based smart fluid displacement systems and methods, here no bottom collection tanks, piston etc are used. Construction : Referring to FIG.SFD(HDL AP)-20, the whole set up is erectable in a fluid reservoir (R) (sea, lake etc). To the bottom of a vertical pole (VL) is connected a fluid loading tank (FTi) which is housed in a hollow air float (HiA), which keeps the hydraulic fluid loading tank (FTi) on floating. To the bottom of hydraulic fluid loading tank (FT,), fluid entry valves (EV), the opening of which causes fluid from reservoir (R) enter into FT, the filling of which causes increased weight of FT,-HiA assembly, making the downward immersion of FT, -Hi A assembly. A fluid clearance pump (CP) is fitted near the top of FT] being supported by hollow air float (HiA) top base, foot valve (FV) placed at the bottom of FTi is connected to clearance pump (CP), connected to the vertical pole (VL) is a lever (LR) supported by two fulcrum points FLi & FL₂. The other end of lever is connectable to hoist pulleys or hooks or baskets or other elements as per end use. In order to render steady state vertical movement of vertical pole (VL), guiders (gd) fixed to suitable pillars or harbours fixers or ship fixers. Based on the principle of couple^' forces and lever mechanism, suitable mechanical advantage (lifted weight distance / movement distance of VL).

Working : When the hydraulic fluid loading unit FT,-HiA is empty without fluid, the whole unit floats on top of reservoir (R), the fluid entry valves EV being are still immersed in reservoir (R). Lever (LR) fulcrum point FLi is at top most point and lever (LR) at horizontal or at forward inclined position. At this point, the load (Ld) to be lifted is connected to hooks of the chain blocks or hoist or dredged sludge is loaded in the bucket. Now, when fluid entry valves (EV) are opened, the reservoir fluid under pressure enters into hydraulic fluid loading tank FTi. AS the fluid is being loaded into FT,, the increasing weight of FT, -Hi A causes hydraulic fluid loading unit assembly to move down, causing the downward pulling of vertical pole (VL) which in turn pulls down the fulcrum point FL).

As FLj moves down, lever (LR) is pulled down which in turn causes the other end of lever (load LD) to move up. By incorporating suitable other provisions revolving or rocking motions etc of VL, the load LD can be taken to the required destination. After reaching the unloading points, the lever (LR) is loaded down by the lifting of fulcrum point (FL^. This can be enhanced by clearing out fluid from FT[ via clearing pump CP evacuating fluid from FT] to fall back into reservoir (R). As clearing pump (CP) is switched on, it is important to see that fluid entry valves EV are kept in closed condition. As all the fluid in FTj is cleared FTi-H)A hydraulic fluid loading unit moves to the upper most floating position. The leverage mechanical advantage, lifted weight versus quantity of fluid loaded in FT] are designable based on principle of couple / leverage principles. This attachment can be made to cranes in harbors, ships or coastal dredging units, thus gravity fluid loading and anti-gravity fluid unloading can be best utilized for improved energy efficiency. Suitable auxiliary movements as per requirements can also be incorporated. The electricity and fuel costs can be tremendously saved.

Experimental proof for workability of smart fluid displacement systems and methods and their innovative applications

The following simulation experiments were conducted to verify workability of smart fluid displacement systems and methods and their innovative applications.

Ball Immersion Test for hollow air float based fluid displacement and anti-gravity reversal movement :

As per FIG.SFD(EP)-21A, within a larger outer vessel VSf a smaller inner vessel VS₂ (equivalent to bottom collection tank E]) was placed and filled with water. An air filled spherical ball (equivalent to Hollow air float HiA) having inner dia smaller than VSi was placed on water surface of VS,. On immersing the ball into the fluid held in VSi by pressure (FIG.SFD(EP)-21B), water from VS, was found overflowing out into outer vessel VS). On release of pressure above the ball, the ball automatically raised up (FIG.SFD(EP)-21C) to float above the residual water level in VS₂. The displaced water from VS₂ was collected and measured and was found equal to the volume of the ball Hi A. The working proof of hollow air float (H]A) immersion displacement of fluid in bottom collection tank by pressure loading (downward pressure stroke) and anti-gravity automatic reversal movement of hollow air float on release of pressure (upward filling stroke) based on Archimedes principle was established.

Verification of hollow air float (ball) fluid displacement system based on plunger principle :

FIG.SFD(EP).22A shows the simulation of bottom collection tank Ei filled with water on to which hollow air float ball H,A is placed floating and a smaller volume inner cylinder resembling fluid loading tank (FT_t) was placed above H_tA. As per FIG.SFD(EP).22B fluid was filled manually from cup Gi (resembling apex fluid supply tank), causing increasing of weight of the ram, first stage pouring upto level of water in Ei to reach just the top of Ei and further pouring in measured quantities resulted in overflow out discharge of water from E,. Equaling volume of water poured into FT,, the proof for hydraulic fluid loading downward movement of Ram. As per FIG.SFD(EP)- 22C on simultaneous suction clearing of water from FT_! and filling in of water into Ei via side way tube feeding, the ram's reversal upward movement due to fluid clearing out in FT_] and anti- gravity buoyancy reversal lifting of raising level of infeed water in Ej. Barrel based experiments for workability verification of indirect plunger based displacement system : As per FIG.SFD(EP)-23A shows the simulation setup on outer bottom collection tank Ej, infeed line IF], floating ram F, comprising of bottom hollow air float barrel (H]A) above which hydraulic fluid loading tank FT, is placed. FIG.SFD(EP)-23B shows the downward pressure stroke of the ram Fi by loading of fluid manually into FTi from cup Gi(verification of downward pressure stroke of the ram by fluid loading under infeed valve closed condition). FIG.SFD(EP)-23C shows the reversal anti-gravity upward buoyancy lift of the ram Fiby fluid released out from FT] by siphoning out and simultaneous infeed fluid entry by opening of infeed pipe IFj. Simulation Test for Indirect fluid loaded Smart fluid displacement system using Piston Mechanism: As per in FIG.SFD(EP)-24B, a simulation setup of infeed fluid source tank S, having downward infeed line IF_! (fitted with inlet valve IjVi) leading to bottom collection tank E_1; fitted with exit line EL (with exit valve E)Vj)and uphead discharge delivery ends at level Lj and L₂. As floating ram F] comprising of bottom hollow air float Hi A fixed with pistons PS, intermediate linkage IML above which the fluid loading tank FT] (a wider area to compensate for the additional pressure energy requirement . FIG.SFD(EP)-24A shows the upward anti-gravity buoyancy lift of empty ram F) enhanced by supply of water from source S via infeed line IFI (infeed valve IiV_t being opened) and exit valve EiV) in exit line E| under closed condition. Ram Fi stops at top most filling level of E, from S. Confirmation of upward reversal movement of the ram due to buoyancy lift caused by charging in fluid El. As per FIG.SFD(EP)-24B, under closed condition of inlet valve I, V,, under opened condition of exit valve EiV| in exit line EL, the manual fluid loading from cup Gi (Resembling Apex fluid supply tank G|) into fluid loading tank FT] resulted in downward pressure stroke of the ram F], into E, and piston PS causing pressure by which entrapped fluid in Ei is displaced to upper destinations at level Lj or L₂ as per valve setting. This confirms downward pressure stroke of ram F) in Ej . On Fi reaching the bottom most position in Ei, the up and down strokes of Fi in E, was repeated and found confirming of fluid displacement by indirect fluid loading system using piston mechanism.

Verification of indirect fluid loaded plunger mechanism applied smart fluid displacement systems : FIG.SFD(EP)-25A shows the simulation setup of bottom collection tank E₍ with overflow trough OFT| at top mouth. Water was filled inside E] either direct via top mouth or via infeed line IFj to reach around 50 to 60% level in Ei . The floating ram assembly having bottom hollow air float H]A, intermediate linkage IML and upper fluid loading tank FT]. On insertion of the floating ram Fi in Ej. The water level in Ei was found raising upward via fluid exit slit FES (annular space between in Fi and E)). ^' Further permanent weight PW was added into FT) , so as to make the water level in Ei , just to reach to mouth of E_t . Under closed condition of inlet valve in line IF_!, pre determined quantity of fluid was manually added (resembling apex fluid supply tank Gi(FIG.SFD(EP)-25B). On progressive fluid loading into FT], the downward pressure stroke of ram F[ in E] is facilitated and reaches the bottom most pre set point, during which pressurized water from E| by F_t over flows via OFTi and stops on stopping of fluid loading in FTI from Gj. This displaced overflow water from OFT_! was found equal to volume of fluid loaded in FT). The reversal stroke by fluid clearing from FTi by siphoning or manual could also be confirmed. The siphoned out water when let down into E) directly was found giving the same effect of charged fluid in E_\.

Verification of workability of Direct fluid loaded smart fluid displacement system usin piston mechanism : FIG.SFD(EP)-26A shows the simulation of a direct fluid loaded smart fluid displacement system using piston mechanism. The bottom collection tank Ei is fitted with bottom infeed line IF] fixed with infeed valve IiVi. Connected to is the exit line EL, fitted with EiV, and two levels of high head discharge point at levels Lj and L₂ with specific control. Placed inside Ei and above the cushion fluid level in E, (FIG.SFD(EP)- 26A is the floating ram F, fitted with hollow air float (H,A) with pistons PS, intermediate linkage IML for permanent fluid or high density metals storage. And the space above IML is assumed as direct fluid loading tank at FTi. H)A, IML and bottom of FTi are connected by drain pipe DP fitted with drain valve DV. A removal plug (PLG) is placed up to the bottom of FT] taking care of fluid loading into FT] under closed conditions enhanced downward movement of Fi and Ei causing overhead displacement to levels Li and L₂. The ram is the guider simulation Gd was also provided via clamps and bearings contacting FT] outer surface during movement.

Working procedure: FIG.SFD(EP)-26B shows the downward movement of F_t in E) on closure of drain valve DL. . Verification of pressure stroke: Under floating condition of Fi and E] with pre filled water or density material in IML takes care of extra pressure required for the discharge of entrapped fluid in Ei to reach discharge levels Li or L₂ via exit line EL. This is ensured by entry of the ram over pre filled water level in Ei and adjusting weight of ram, weight of fluid or density material added to intermediate linkage IML which causes fluid displacement upto level Li or L₂. At this stage, inlet valve I)Vi is closed and exit valve EiV] opened and predetermined volume of water is manually loaded into FTi. Under closed conditions of plug PLG blocking drain line DL, the addition of water load into FTi causes fluid displacement to high head destinations Li or L₂ as per setting. The volume of water displaced was found equal to volume loaded into FT_!. Excepting for higher IML load required to overcome friction. Reverse filling stroke of the ram: On reaching the bottom most position in Ei (FIG.SFD(EP)-26B) exit valve Ει ^ and inlet valve L V) are closed. Plug PLG was opened allowing fluid from FT_! to flow down via drain line DL under opened conditions of drain valve DV causing level raise of drained fluid in Ei and the buoyancy lift causing anti-gravity upward reversal of the ram and stops after clearance of water in FT_!(FIG.SFD(EP)-26A). Friction losses are found higher, leading to conclusion that plunger based systems are more efficient.

Verification of working of direct fluid loaded smart fluid displacement system using plunger mechanism :

As per FIG.SFD(EP)-27 demonstrates the verification of workability of direct fluid loaded smart fluid displacement system using plunger mechanism. The simulation setup consists of bottom collection tank Ei fitted with inlet feed line IF] and inlet valve LV), mainly meant for service operation. The top mouth of Ei is fitted with overflow trough OFTi with conduction lines CL. The floating ram Fi is comprised of bottom hollow air float HiA, intermediate linkage IML (meant for additional fluid or material storage required to add pressure to the ram), fluid loading compartment FTi above IML and also fitted with plug PLG sealing drain pipe DP fitted with drain valve DV meant for transport of fluid from ram into E, . FIG.SFD(EP)-29A,B,C,D demonstrates various stages of fluid discharge levels from Ei based on ram Fi movement. Stage A: Pre stored water in bottom collection tank E_! almost above 50% capacity of E). Stage B: Entry of empty floating ram F| (under closed conditions of plug PLG) above fluid in E[ . The weight of empty ram results in fluid raise in Ei via fluid exit slit FES (annular space upto level Li, the empty ram descending in Ei based on its weight). Level raise volume in Ei upto level Li is equivalent to weight of ram F](based on Archimedes principle). The level raise^' is also based on surface area of ram Fi cross section and area of FES as per Pascal's Law of equilibrium in hydraulic pressure system. Stage C: Water is loaded into IML (under closed conditions of plug PLG) upto the result of fluid raise in FES reaching just the top mouth level of OFT]. This stage is addition to the weight of the ram to overcome required pressure to lift water from E) upto level of OFT]. Stage D: Predetermined level of water was further loaded into FTj (under closed conditions of plug PLG) resulting in fluid overflow discharge out from OFT_] via annular space FES. This water was collected and measured for volume or weight which was equivalent to weight or volume of water loaded into FT,. On controlled release of water from FT_! by removal of plug PLG, the ram was found reaching position as per stage C, confirming the fact that the volume or weight of water released from FTi into Ej is equivalent to charged fluid in FT]. Stage C figure is demonstrated in FIG.SFD(EP)'-26A. This experiment was repeated in several time to reach the fundamental energy equation involved in the fluid displacement system, the simulation setup for displacement volume of 8 liters to head level of 1.5 to 1.75 meters was constructed and all the above said stages A, B,C, D were found confirming to the following basic equation. For displacing water of weight (M) to a height (H), work done is decided by formula,

M G H

in Newton Meters

η

M = weight of water (w)

G = Acceleration due gravity = 9.81 m / sec²

H = Head of lift (h) in meters

η—> Efficiency of pumping

Work done on the pre loaded ram of total weight ( i + w₂ + w₃ ) for a height (h,) to pressurize water (w) stored in ram

(WL+ W2 + W3 ) x 9.81 x h]

. N_m

η

W]→ weight of hollow ram to raise upto level L,

w₂→ pre loading weight in IML to raise fluid level in El upto OFT, top

w₃→ standard weight of fluid loaded in FTi equivalent to displacement weight (M)

(hi - Distant moved by the ram during fluid loading into FT] along with weight of empty ram and loaded weight in IML)

Now, equating the above two equations,

M G H (w, + W2 + W3 ) x 9.81 x hi

Nm = Nm

η η

Displacement fluid weight M = w₃ (loaded weight of fluid in FT] in this case)

Substituting respective standard values to the above equation

M = weight Of water (w) = 10,000 gs

G = Acceleration due gravity = 9.81 m / sec²

H = Head of lift (h) = 60 meters

η→ Efficiency of pumping ( 0.8)

10,000 x 9.81 x 60

Work done = Nm = 7357500 Nm

0.8

Assuming,

W]→ weight of hollow ram to raise upto level L) = 4000 Kgs w₂→ pre loading weight in IML to raise fluid level in El upto OFTi top = 6000 kgs

w₃→ standard weight of fluid loaded in FTj (M) = 10,000 Kgs ( M = w₃)

η→ Efficiency of pumping ( 0.8)

Work done on the ram (w_I + w₂ + w₃ ) x 9.81 x h)

during displacement in Nm = — m

η

Substituting the above values of i , w₂ , w₃, hi & η (4000 + 6000+ 10000) x 9.81 x hi

Nm

0.8

Equating both equations of Energy required for fluid lift ( 10,000 Kgs to 60 meters and work done on the ram during displacement )

M G H (wi + w₂ + w₃ ) x 9.81 x h_!

Nm = Nm

η η

. 0.8

7357500 x 0.8

h| (distant moved by the ram during displacement ) = = 30 Mtrs

20,000 x 9.81

Substituting value of hi as 30 mtrs = Nm = 7357500Nm in the energy equation Ά

(as per assumed figures)

A higher weight of the ram is moved to a smaller distance equaling the smaller weight of displacement fluid weight by a higher distance, a balancement of hydraulic couple system.

Thus the working energy balance equation of smart fluid displacement system is found confirming to following basic laws and principles.

M G H

1) Nm

η

2) Archimedes principle^'of floatation & immersion

3) Pascal's Law of hydraulic pressure based on Brahma's Press

4) Working of evidence of controlled immersion of lowering and lifting (by density modification) of submarines in open sea, which is now placed in a walled well in this case.

5) The 'η' of energy conversion factor restricts that the output energy of the system is lower than input energy, thus confirming law of conservation of energy.

6) Friction in case of plunger is negligible due to absence of piston and one end is open in the hydraulic system. Verification of workability of direct fluid loaded smart fluid displacement system using plunger mechanism with telescopic seal coupling

a) Verification of workability of telescopic sealed coupling for expansion and contraction strokes: FIG.SFD(EP)-28.1A shows the simulation setup consisting of bottom collection tank E, and the moving ram Fj having bottom hollow air float (Hi A) fitted with centralized exit line pipe EL) via conduction line CL connected with control valve CV and the bottom placed inverse funnel. The bottom outer orifice (00) of hollow air float Hi A and top inner orifice (IO) of bottom collection tank are connected by telescopic sealed coupling using polythene sheet diaphragm, in order to prevent fluid exit via space between (inner of Ej and outer of H)A) during pressure stroke.

b) Verification of pressure stroke: As per FIG.SFD(EP)-28.1A, water was filled in E], the hollow air float of ram Fi is placed above even fluid level and using telescopic sealed coupling. As per FIG.SFD(EP)-28.1B, when the ram F] was pressurized manually into Ei (opened condition of control valve CV), the simultaneous pressure developed and blocking action of expanding telescopic sealed coupling, resulted in discharge of fluid in Ei via conduction line CL / exit line ELi and was coming out as uphead discharge flow out. The flow out continued till reaching of HiA to the bottom most feasible point. The reverse stroke of ram Fi was found feasible on draining of water downward into E) via ELi / CL.

Verification of complete workability of Telescopic sealed coupling based direct fluid loaded plunger mechanism : FIG.SFD(EP)-28.2A shows the simulation setup consisting of bottom collection tank E, fitted with exit line ELi along with exit valve EiV). Under empty condition of E) the floating ram setup Fi comprising of bottom hollow air float (H[A), intermediate linkage space IML (filled with sand or equivalent weight of water in order to provide additional hydraulic pressure during displacement as well as overcoming resistance of the flexible diaphragm (TSQ), a hollow space FTi above IML in order to hold loading fluid into the ram Fp A drain pipe DP passes through IML top hollow air float H]A and bottom placed drain valve DV. The bottom of FTi is sealed via mechanical plug PLG guided by inner guides Gd. The bottom outer orifice (00) of hollow air float Hi A and the top position inner orifice (10) of Ei are connected via polyethylene or telescopic sealed coupling using flexible Rexene segments (TSC). Verification of downward pressure stroke: As per FIG.SFD(EP)-28.2A, the empty ram F_! without fluidjn FT) is kept placed on E, using telescopic sealed coupling and water is filled into E, by opening of valve E,V, through top level feed into EL] . The filling level of water in Ei keeps the floating ram F| in Ei by buoyancy forces causing shrinkage of diaphragm TSC(Fi top most position). Now, plug PLG is inserted to close drain line DL, predetermined volume of water is filled in FT] manually, the added density resulting in downward descending of ram Fi in E). The pressurized water in Ei by combined action the descending ram F, and blocking effect of diaphragm TSC forces entrapped water in Ei to get displaced uphead via exit line ELi (under exit valve EjV| opened condition) and overflows out at the preset uphead level as shown in FIG.SFD(EP)-28.2B. Verification of upward buoyancy based anti-gravity reversal movement of ram: A shown in FIG.SFD(EP)-28.2A, on opening of plug PLG, water from FT] close downward through drain line DL into E_\. The raising level of water in Ei causes buoyancy based antigravity lifting of ram Fi to preset top position on complete draining of water in E]. The TSC diaphragm shrinks down during the stroke. The upward and downward strokes were repeated many times for verification of consistency. Compared to direct fluid loaded plunger mechanism, the telescopic sealed coupling mechanism based plunger calls for additional energy for displacement to overcome the resistance of the diaphragm TSC which can be enhanced by adjusting weight of material or fluid stored in IML space.

Construction of a simulation ship fitted with bottom hydro turbine unit : As shown in FIG.SFD(EP).30A, the simulation ship with bottom fitted hydro turbine unit was constructed on the following basis. Two hollow air sealed PVC floats (FLi, FL₂) were linked by bottom support frame (SPF) which inturn was linked to bottom clamps CL b means of metal strips MSj and MS2. The clamps were fastened to Turbine Housing (TH), which inturn was housing two turbines Ti and T₂ fed fluid via entry lines Q and C₂ (resembling Penstocks) vertically attached to turbine housing (TH). The turbines Ti and T₂ were mounted on bottom shaft BS fitted with bearings at ends to the housing TH. The outer ends of bottom shaft BS was linked to upper placed paddle wheel shaft (PS), fitted on both ends of the shop float by bearings. The upper shaft had extended paddle wheels PWi and PW2, placed on both ends. The bottom of the turbine housing (TH) was linked to Draft tube(DT). A belt drive BL connected bottom shaft of turbine and upper paddle shaft. The experimental verification involved two stages. (1)A hydro Turbine powered ship propulsion within fluid source, positioned under the ship (2) Application of smart fluid displacement attachment for fluid clearance from hydro turbine of the ship via floating unit attachment. '

1) Verification of movement of Hydro ship using bottom head Turbine rotary motion driven propulsion:

As shown in FIG.SFD (EP)-30A the simulation float ship was placed in a water filled reservoir (R) having a water infeed line with valve IV]. The simulation ship unit's bottom draft tube was tightly linked to a flexible hose line (FH), the open end of (FH) having linked to an exit tube fixed on the tank wall jW, closable using cork CK₃. At the beginning of the experiment, the tank was filled at level hi and water infeed valve IV, is kept open. The float ship was set at line position L| from the wall of RiW and found stationary. As the corks CKi, C ₂ from Turbine inlet lines were removed and bottom outlet line cork CK₃ was also removed, with the infeed water line being open, the fluid kinetic flow was activated inside the turbine House (TH) resulting in rotational movement of Turbines T], T₂, Turbine shaft (BS), connected belt drive activating the paddle wheel shaft's (PS) rotation. As the paddle wheels PWi and PW₂ rotated, the whole float ship assembly moved forward in the tank (Ri) and got stopped till reaching position line L₂ (FIG.SFD(EP)-30B) in forward direction into the reservoir tank R]. As the infeed line flow was low, the float ship was found reaching a lower head position (h₂) instead of position (hi) at the beginning, with slowing speeds and stoppage due to the pulling back force of fixed flexible hosing reaching maximum stretching position (L₂). Cork CK₃ was closed, the infeed line flow continued so as to raise the level of float back to position (hi) and the whole experiment was repeated multiple times to verify the movability of down head Turbine based hydro ship's self propulsion. Having provided a discharge out via flexible hosing, the fluids flow down from turbine, caused turbine rotation, which inturn resulted in forward propulsion of the float ship.

2) Verification of sub ship based direct plunger mechanism applied smart fluid displacement for expulsion of outlet fluid from hydroship turbine under floating condition: The sub ship assembly prior to fluid displacement is shown in FIG.SFD(EP)-31A. The sub ship SS is constructed by a sealed PVC Air float (SS/AFS), to which a bottom collection tank Ei BCT (resembling a single unit of bottom collection tank in sub ship float) was inserted and filled with water, assuming the position of charged water from turbine down flow from hydro ship over the surface of water in E,, the floating plunger ram F, (with bottom hollow air float H_{A and fluid loading tank FT,) was placed and water manually loaded in FT,(as shown FIG.SFD(EP)-31A). The direct loading of water in FTi resulted in downward plunging movement of ram F] in Ei causing overflow discharge out. The simultaneous filling of water in Ei and suction of water out from FTi resulted in reverse upward motion of Fj in E_\. The floating level of sub ship (SS/AFS) was found lowering compared to free float position prior to fluid loading in FTI. The above test confirms workability of application of plunger based direct fluid loading smart fluid displacement system to bottom turbine placed hydro ship propulsion.

Proof of workability of Hydraulic Crane movements using Smart Fluid Displacement System : A simulation experiment setup similar to demonstration in FIG.SFD(HDL AP)-20 was constructed using a 200 liter barrel (R) is filled with 80% of water to represent a reservoir. A top open and bottom closed PVC cylinder (FTi) surrounded by closed hollow air float (H]A), tied-up with counter dead weight components is allowed to float on the water in barrel (R). The bottom of FTi is fitted with fluid entry valves (EV) at both sides and bottom. At the floating top most position, fluid entry valves (EV) are under closed condition. As the entry valves (EV) below FT) are opened fluid from 'R' enters into FTi and the raising level causes fluid loading in FT] which inturn moved towards the bottom of R. After reaching the lowest possible position (entry valves (EV) were closed. A hollow pipe (HP) was placed into FTi and manual suction (resembling clearance pump CP) was done. The progressive clearance of fluid from FT] resulted in upward anti-gravity reversal movement of FT, and could continue till reaching a top most possible point. This simple test proof is an evidence for the workability of smart fluid displacement systems applicable to hydraulic crane movement

It will be obvious to a person skilled in the art that with the advance of technology, the basic idea of the invention can be implemented in a plurality of ways. The invention and its embodiments are thus not restricted to the above examples but may vary within the scope of the claims.

Further the above described embodiments of the present invention are intended to be examples only. Alternations, modifications and variations may be effected to the particular embodiments by those of skill in the art without departing from the scope of the invention, which is defined solely by the claims appended hereto.

Claims

I claim,

1) Fluid displacement units mainly comprised of bottom collection tank, floating ram, fluid in let & exit lines, based on indirect, direct loading systems which apply piston, plunger, plunger with telescopic seal coupling mechanisms for pressurized displacement, classified as,

(i) Indirect fluid loaded displacement system using piston mechanism

(ii) Indirect fluid loaded displacement system using plunger mechanism

(iii) Indirect fluid loaded displacement system using plunger with telescopic seal coupling mechanism

(iv) Direct fluid loading displacement system using piston mechanism

(v) Direct fluid loading displacement system using plunger mechanism

(vi) Direct fluid loading displacement system using plunger with telescopic seal coupling mechanism. Wherein a single displacement unit comprising of

(i) Indirect fluid loaded displacement system using piston mechanism - a bottom collection tank (E,) connected to infeed line (IFj) from source (S) leading to top infeed line TIF connected to downhead expandable hose EH , housed in slot space SP , connected to fluid drain pipe DP piercing down head through hollow air float(HiA) fixed with drain valve DV ending into El or bottom infeed line BIF, with inlet valve IiVj, and exit line EL| fitted with valve E|Vi leading to conduction line CL placed at the head level of displacement ending at destined point of discharge, a floating ram vertically reciprocating supported by guiders Gd placed over the pre stored cushion fluid in E, comprising of bottom hollow air float (H]A) with piston elements (PS) to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FT]) linked to Apex fluid supply tank (G via flexible hoses FH and control valves for delivery of fluid flow from G| into FT, during loading stroke and pipe line with foot valve FV connected to clearance pump CPi for reverse clearing of fluid from FT, to G, during unloading stroke, a feed pump supplying fluid from source (S) to G_: .

(ii) Indirect fluid loaded displacement system using plunger mechanism - a bottom collection tank (E_:) connected to infeed line (IF|) from source (S) leading to top infeed line TIF connected to downhead expandable hose EH , housed in slot space SP , connected to fluid drain pipe DP piercing down head through hollow air float(H]A) fixted with drain valve DV ending into El or bottom infeed line BIF, with inlet valve IjV] , and the exit outlet being the annular space / fluid exit slit (FES) extending up to the top of bottom collection tank E| via over flow trough (OFT)₎ and conduction line CL, placed at the head level of displacement ending at destined point of discharge, a floating ram vertically reciprocating supported by guiders Gd placed over the pr_e stored cushion fluid in Ei comprising of bottom hollow air float (H|A) without piston, to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FTl) linked to Apex fluid supply tank (G₎) via flexible hoses FH and control valves for delivery of fluid flow from G) into FT] during loading stroke and pipe line with foot valve FV connected to clearance pump CP1 for reverse clearing of fluid from FT, to Gi during unloading stroke, a feed pump supplying fluid from source (S) to G_t

Indirect fluid loaded displacement system using plunger with telescopic seal coupling mechanism - a bottom collection tank (E]) connected to infeed line (IF]) from source (S) leading to top infeed line TIF linked to downhead expandable hose EH, housed in slot space SP, connected to fluid drain pipe DP piercing down head through hollow air float(H[A) fixed with drain valve ,DV, ending into E) or bottom infeed line BIF, with inlet valve Ij V) and exit line ELI fitted with valve ElVi leading to conduction line CL, placed at the head level of displacement, ending at destined point of discharge, a floating ram vertically reciprocating supported by guiders Gd placed over the pre stored cushion fluid in E] comprising of bottom hollow air float (HiA) to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FT)) linked to Apex fluid supply tank (G via flexible hoses FH and control valves for delivery of fluid flow from G) into FT] during loading stroke and pipe line with foot valve FV connected to clearance pump CP, for reverse clearing of fluid from FT, to G, during unloading stroke, a feed pump supplying fluid from source (S) to Gl,a telescopic seal coupling diaphragm connecting the inner orifice 10 of bottom collection tank E| and outer orifice 00 of F] / Hi A, blocking fluid rise via fluid exit slit FES, and forcing displacement

Direct fluid loading displacement system using piston mechanism - a bottom collection tank (Ei) connected to exit line (ELi) fitted with valve EiVi leading to conduction line CL placed at the head level of displacement ending at destined point of discharge, a floating ram vertically reciprocating supported by guiders Gd placed over the pre stored cushion fluid in Ei comprising of bottom hollow air float (H|A) with piston elements (PS) to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FT,) receiving fluid inlet from infeed line fitted with valve IV i via header 'Hd' from source (S), the fluid loading tank FT, being connected to fluid drain pipe DP piercing down head through hollow air float(Hl A) fixed with drain valve DV ending into E,, optional bottom infeed line BIF, with inlet valve I,V] , and exit line EL, Direct fluid loading displacement system using plunger mechanism - a bottom collection tank (E_t) with top over flow trough OFT|, connected with optional bottom in feed line BIF from source (S), a floating ram vertically reciprocating placed over the pre stored cushion fluid in El supported by guiders Gd, comprising of bottom hollow air float (H|A) without piston to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FT_t) receiving fluid inlet from infeed line top infeed line TIF connected to downhead expandable hose EH , housed in slot space SP, provided with fluid loading tank FT i, connected to fluid drain pipe DP piercing down head through intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, hollow air float^A) fixted with drain valve DV ending into or bottom and the exit outlet being the annular space / fluid exit slit (FES) extending up to the top of bottom collection tank Ei via over flow trough (OFT|) and conduction line CL, placed at the head level of displacement ending at destined point of discharge

(vi) Direct fluid loading displacement system using plunger with telescopic seal coupling mechanism- a bottom collection tank (E|) with top infeed line TIF or bottom infed line BIF with in feed valve I]V] and exit line ELi fitted with valve EiVj leading to conduction line CL, placed at the head level of displacement, ending at destined point of discharge, a floating ram F_t , a floating ram vertically reciprocating supported by guiders Gd placed over the pre stored cushion fluid in Ei comprising of bottom hollow air float (H|A) without piston elements to impart buoyancy floating effect, intermediate linkage space (IML) for pre-loaded weight/ fluid storage for adding density to the ram, top placed fluid loading tank (FT|) receiving fluid inlet from infeed line (IFi) from source (S) leading to top infeed line TIF linked to downhead expandable hose EH, housed in slot space SP, connected to fluid drain pipe DP piercing down head through hollow air float(H₍A) fixed with drain valve DV, ending into bottom collection tank E^a telescopic seal coupling diaphragm connecting the inner orifice 10 of bottom collection tank Ei and outer orifice 00 of F| / Hi A, blocking fluid rise via fluid exit slit FES, and forcing displacement via exit line EL) connected to conduction line CL leading to end point of discharge.

The basic cycle of working of the displacement system being filling in of fluid in bottom collection tank, pressurization displacement by the ram action via exit lines

The displacement systems find vast applications to continuous hydro power generation, Mass water transport, ship propulsion and hydraulic machines like cranes.

2) As per claim 1, methods of downward pressurization stroke of the ram in the displacement unit by way of fluid loading into the Ram component FT[

a] The direct fluid loading mechanism comprising of floating ram Fi having bottom hollow air float, intermediate linkage for standard weight / fluid storage for density addition to the ram, a top placed fluid loading tank connected to apex fluid supply tank G| via flexible hose FH with control valves. The draining of fluid form apex fluid supply tank via flexible hose FH on opening of control valves lead to weight / density addition to the floating ram, causing immersion into fluid stored in bottom collection tank and further displacement via exit line.

b) The direct fluid loading mechanism comprising of floating ram F) having bottom hollow air float, intermediate linkage for standard weight / fluid storage for density addition to the ram, a top placed fluid loading tank FTi receiving fluid directly from source (S) via header Hd and infeed line IF_t with valve controls. The draining of fluid into fluid loading tank via opening of control valves lead to weight / density addition to the floating ram, causing immersion into fluid stored in bottom collection tank and further displacement via exit lines which are case specific based on piston / plunger / plunger with telescopic seal coupling mechanisms.

3) As per claim 1, methods of upward reversal cum filling stroke of the displacement system unit, i) In case of indirect loading system, fluid load reduction on ram Fj , by the action clearance pump CPlvia pipe line with foot valve FV delivering back into apex fluid supply tank and simultaneous simultaneous fluid entry form source (S) via infeed line IF, either through top infeed line TIF, expandable hose EH, hollow air float inner, drain pipe DP fitted with drain valve into bottom collection tank E, or via bottom infeed line BIF under opened condition of valve I]V], the reversal action caused by rising level of filled in fluid in Ei and buoyancy floating effect of ram F,, ii) In case of direct fluid loading system, the fluid load reduction on ram Fj by draining down fluid form fluid loading tank FTi via opening of drain valve DV, drain pipe DP under closed condition of line valve E|V) , the reversal action caused by rising level of filled in fluid in Ei and buoyancy floating effect of ram Fi,

4) As per claim 1. A method of continuous supply of fluid form source into moving Ram F_! via infeed line IF, , top infeed line TIF bored into bottom collection tank wall, an extensible hose FH positioned inot a slot space(SP) entering the body of the ram via fluid loading tank FT or direct through inter mediate linkage IML, hollow air float via drain pipe DP fitted with drain valve DV.

5) As per claim 1, means for pressurized displacement of stored fluid in bottom collection tanks by,

a) Piston( PS) based pressurization, by which the scrapping action pressurizes entrapped fluid leading to displacement via exit line EL|, conduction line CL leading to end point of discharge under open condition of exit valve E|V|

b) Plunger based pressurization, by which the fluid is made to rise through the exit slit FES via annular space between ram & bottom collection tank, reaching over low trough OFTi, over flowing and taken to end point of discharge via conduction line CL.

c) Plunger with telescopic seal coupling mechanisms (TSC) based pressurization, which the entrapped fluid movement via annular exit slit FES is blocked by a flexible diaphragm, forcing exit discharge via exit line ELi, conduction line CL to end point of discharge,

6) As per claim 1. A method of continuous supply of fluid form source into moving Ram F| via infeed line IF] , top infeed line TIF bored into bottom collection tank wall, an extensible hose FH positioned in a slot space(SP) entering the body of the ram via fluid loading tank FT or direct through inter mediate linkage IML, hollow air float via drain pipe DP fitted with drain valve DV.

7}In case of direct fluid loaded smart fluid displacement system, the input energy for downward movement of the floating ram being mere forces of nature-gravity, dead weight of ram (ram material weight + weight of stored standard fluid volume in intermediate linkage) and additional weight of inflow fluid into hydraulic fluid from source and for the upward reversal stroke , the floating buoyancy and rising level of fluid from fluid loading tank into bottom collection tank. The input energy supplied externally is merely for operation of valves, control and breaks and in case of piston, telescopic seal coupling frictional resistance need to be overcome

8)As per claim 1, the energy balance equation of the working of direct fluid loaded plunger or plunger with telescopic seal coupling can be expressed in Newton meters (Nm) based on Mass x distance moved.

9.81 x weight fluid displaced from bottom (material weight of ram (wi) +

Collection tank (w kgs x lift head (h_j) mtrs weight of stored fluid in IML(w₂) +

Efficiency of the system weight of loaded fluid into fluid loading tank (w)kgs x (Nm) vertical distance moved by the ram (h_? ) meters

Efficiency of the system

(Nm)

In case of piston frictional losses being taken into consideration.

9] The working of the displacement systems mainly by gravity, total weight of the moving ram over the fluid cushion is confined & confirmed to established scientific principles like Archimedes principle of floatation & immersion, Pascal's Law of hydraulic pressure based on Brahmas Press, frictional losses in hydraulic energy transfer losses and Working of evidence of controlled immersion of lowering and lifting (by density modification) of submarines in open sea,

10) The displacement system units further apply- valves control systems, limit switches, sensors, safety devices, emergency alerts, monitoring devices & controls riot limited to computerized hard ware & soft ware systems

11) As per claim 1, a method of continuous hydro power generation form existing hydro power plants ( Dam / Barrage / Run of river / Pumped storage power plants) by collection of the outlet ware form Turbine draft tube into the smart fluid displacement units ( F F| , E₂/ F₂) in an alternate manner via a header Hd, the downward pressure stroke of the tarns Fl / F2 resulting in fluid displacement form El/ E2 uphead into conduction line CL and fall back to intermediate forebay or source (S).

12) As per claim 1, a method of continuous hydro power generation from any water source (Dam/Barrage/run of river/pumped storage plant, running river/ canals/lakes/large scale water points, Effluent Treatment Plants, Sea coasts) by formation of an artificial downhead hydraulic head below the water source (S) forming a penstock(PS) being fed water form source (S) via in take line( lL),intermediate forebay(IFB), the downflow water into penstock (PS), is used for power generation using hydro turbine coupled to generator and further taken to downhead placed smart fluid displacement units ( _Ei / F| , ¾/ F2preferably applying direct plunger /direct plunger with telescopic seal coupling mechanisms) in an alternate manner via header (Hd), The downward pressure stroke of the rams Fl / F2 resulting in uphead fluid discharge via exit lines EL, conduction CL to fall back into intermediate forebay or fluid source (S). 13) As per claim 1, a method of damless continuous hydro power generation from any water source (Dam Barrage/run of river/pumped storage plant, running river/ canals/lakes/large scale water points, Effluent Treatment Plants, Seacoasts), by downhead gravity based feeding water from source (s), via intake lines, intermediate forebay; downhead placed smart fluid displacement units (preferably applying direct plunger /direct plunger with telescopic seal coupling mechanisms), the alternate action of the dams F, F₂ in E _/ E₂ resulting in upward discharge into high head tank (OT) forming a hydraulic head above fluid source (S), and further release of spread wake in OT downhead via. hydro turbine coupled to generator used for power generator and further falling back to intermediate forebay or source (S).

14) . As per claim 1. A method of a method of continuous hydro power generation from open sea . reservoirs by construction of a open well within sea . reservoirs, letting down water to flow down v from source (s), via intake lines, downhead placed smart fluid displacement units (preferably applying direct plunger /direct plunger with telescopic seal coupling mechanisms), the alternate action of the dams F] _/ F₂ in E _/ E₂ resulting in upward discharge via exit lines, conduction lines back to source.

15) .As per claim 1 , a method of continuous hydro power generation from any existing thermal (coal, gas, fuel, Biomass), nuclear and wind mill power plants, by replacing the prime mover turbine units by smart fluid displacement systems and methods (preferably the Direct plunger with seal coupling mechanisms), by artificial high head formation from a high head tank (OT), the released out water from OT being used for running replaced hydro turbine of equal capacity coupled to existing generator, and falter of back to intermediate forcing or water source by gravity.

16) As per claim 1 , a method of mass water transport to Building tops, water distribution high head tanks from source to remote end user points, the system comprising of source(S} , in take lines leading to intermediate forebay, allowed to fall by gravity into smart displacement system units (preferably of direct plumper or direct plumper with telescopic seal company mechanism) which further displaces/pumps up water to end use destinations like building tops or high head tanks for public distribution.

17) As per Claim 1, a method of rain / flood water diversion to remote end walled reservoirs storage, the pumping system comprising of in feed line from source (S), intermediate forebay (IFB), Header (Hd), alternate feed lines to smart fluid displacement systems units (preferably applying direct plunger or Direct Plunger with Telescopic seal coupling), the flowing in fluid being discharged / pumped up info remote distant, walled reservoirs WR, / WR₂ etc, thus preventing flood / rain water run up to sea and providing scope of water storage above land.

18) As per Claim 1, a method of rain harvesting on open sea surface using floating top open tanks connected in series, the downwards outlet water from the collection tanks being delivered to coastal land/islands applying smart fluid displacement systems unit which is placed in a air float support

19}As per Claim 1, a method of application of smart fluid displacement systems and methods (preferably the direct plunger using telescopic seal coupling mechanism) being held down heads supported in a subship float with protection housing, used for collection and discharging down flow water from a bottom placed hydro turbine unit placed at the main ship bottom, which is run by intake of reservoir fluid intake, the energy being used for ship propulsion and other uses.

20) As per Claim 1 , a method of application of smart fluid displacement systems and methods for collection of fluid calling from hydro turbine unit, supported by protection housing in a sub ship float, the collected water into smart fluid displacement systems (preferably direct plunger with telescopic seal coupling mechanism) lifted to high head tower (OT), via alternate rams F|. _/ F₂ action, the release of water from OT being used for hydro electric power generation from generator 2 and falls back into reservoir/sea by gravity and the electrical output from generators 1 and 2 being used for Main ship propulsion and other needs, apart from energification of floating off shore work stations.

21) As per Claim 1, a method of application of smart fluid displacement systems and methods for descending and ascending actions of immersible under water ships, as well as propulsion of the same by bottom placed hydro turbines unit, which runs by in take of reservoir fluid into the system, the fluid outlet from the same being discharged out into the sea/reservoir, as well for the outer shell of the immersible ship using linked smart fluid displacement system unit preferably the direct plunger system with telescopic seal coupling mechanism along with air hose lines hanging from a float support

22) As per claim 1. A method of application of smart fluid displacement systems and methods for activation of cranes / levers on open sea by a open end floating tank fitted with hollow air float & dead weight, in let provisions for fluid loading from reservoirs for subsequent immersion based downward movement due to density addition and reversal by fluid clearance from the system by clearance pump CP, the reciprocal movement system attached to a crane /lever for activation.

23) As per claim 1, the smart fluid displacement systems & methods application part of any new application arising further.