_dinto the transfer tank through the access port. In this exchange, the volume of water displaced into the return tank by the displacement device, and the volume of air V_drecovered into the transfer tank by the displacement device are equal to the volume of a power module. Thus, water in the bi-level tank is moved back and forth between the transfer tank and the return tank to account for the passage of one power module through the transfer tank, and to accommodate the next power module in sequence. This is done with no loss of water from the bi-level tank. An important consequence of this is that the difference between respective levels of the upper and lower water surfaces is maintained.

A control unit is provided for the machine that will coordinate an operation of the valve mechanism with an operation of the displacement device as disclosed above. This requires external power from an available source. As envisioned for the present invention, the external power source will preferably be a commercial power grid. However, the electric generator that is driven by the machine of the present invention may itself be used as an alternative power source. In either case, an external source of power will be required to operate power-driven components of the machine, and to account for friction losses.

Ancillary components of the bi-level tank include a deflector/exit chute and a launch platform. Specifically, the deflector/exit chute is located at the top of the return tank and is used to reorient a power module as it exits the return tank. In the return tank, most of the closed-loop underwater pathway traveled by the power module needs to be vertically oriented. This vertical orientation, however, is inefficient for recovering a power module at the end of a duty cycle. For this reason, the deflector/exit chute is oriented to establish an exit angle φ from vertical so that the exit momentum of a power module will be directed toward a launch platform as it emerges from the return tank. The exit angle φ will preferably be in a range between 15°-20°.

In its relationship with the bi-level tank, the launch platform is positioned near the deflector/exit chute to receive a power module as it emerges from the return tank. In its relationship with the duty cycle of a power module, the launch platform is at the start point. Structurally, the launch platform is formed to receive, stabilize and hold the power module in a predetermined, near-horizontal, orientation on the launch platform. This orientation is then held until the power module is to be released to begin another duty cycle. For this purpose, the launch platform also includes a rotating mechanism that is power activated to rotate the launch platform and thereby release (i.e. drop) the power module. Upon its release from the launch platform it is important that the power module be in a vertical, upright orientation for subsequent engagement with the electric generator.

With a specific consideration now directed to the power module, it is important that the power module be buoyant, but that it also have the weight needed to do the work necessary to drive an electric generator (i.e. ½mv_e2). Within these constraints, weight W and buoyancy B are both forces that are constantly acting on a power module. Although W is constant, the buoyancy force B will change in both magnitude and direction during a duty cycle of a power module. Also, when a power module is moving, there will be a drag force D acting on the power module whose magnitude will depend on the velocity v of the power module. Accordingly, these interrelated forces require scrutiny.

By definition, weight W is the force acting on an object of mass m in the gravitational field. Weight is a constant and it is not affected by movements of the object. Moreover, weight always acts on an object in a downward direction toward the center of the earth. On the other hand, buoyancy is defined as the ability or tendency of an object to float in water or any other fluid. For objects in the earth's atmosphere (i.e. air), the buoyant force on heavier-than-air objects is typically ignored. This is not the case, however, when the object is submerged in water.

In general, there are several aspects of a buoyant force (B) that are particularly noteworthy. For one, the magnitude of a buoyant force is determined by the difference between the volume-weight (i.e. weight/volume) of an object, and the volume-weight of the fluid medium (e.g. water) that is displaced when the object is submerged in the fluid medium. Using the respective magnitude of B and W, a buoyancy factor can be determined. Mathematically, the buoyancy factor is a dimensionless ratio of the buoyant force (B) to the weight (W) of the object (i.e. the buoyancy factor=B/W). For this ratio the volume of the object and the volume of the displaced fluid medium (e.g. water) are equal. It is important to note that for the buoyancy factor, the density of the materials that are used for the manufacture of the object, and the shape of the object, are not factors in determining the object's buoyancy. Succinctly stated, it is only the volume of the object that matters.

The power module of the present invention is buoyant because it is engineered to be lighter than the volume of water it displaces in the bi-level tank. Thus, the materials used to provide strength and form for the power module are engineering design considerations. Preferably, the power module is designed to establish a buoyancy ratio (B/W), in water, that is in a range between 0.6 and 0.75.

As indicated above, whenever a power module moves, drag forces act to oppose the movement of the power module. Mathematically, a drag force D is expressed as Drag=D=C_D½ρv²S. In this equation, C_Dis a dimensionless coefficient, ρ is the density of the medium, v is the velocity of the object in the medium, and S is a function of the object's shape and cross-sectional area. The import here is that the drag force D is dependent on medium density, object velocity, and the design shape of the object. In the context of the present invention, the respective drag coefficients C_D(upper)and C_D(lower)have been discussed above with regard to the engineering effect they can have on movements of a power module through a bi-level tank.

According to an exemplary embodiment of the invention, an apparatus includes a volume of water confined by a bi-level tank adjustable between a return configuration and a reset configuration. The bi-level tank includes a transfer tank including an access port configured to open and close, a return tank extending upright from the transfer tank, and a transfer port between the transfer tank and the return tank and configured to open and close. The volume of water includes a transfer component in the transfer tank and defining a lower water surface under the access port, a return component extending upright through the return tank from the transfer port and the transfer component to an upper water surface above the lower water surface, and a transition component. A piston in the transfer component is below the transfer port. The piston includes an upper surface and a lower surface and is mounted for reciprocal movement between a lowered position and a raised position. A force-applying mechanism is operatively coupled to the piston. An extensible and retractable bellows coupled between the piston and the return tank extends upwardly through the transfer component between the upper surface and the return tank and couples the return component to the upper surface under pressure from the return component. An extensible and retractable boot over the bellows and coupled between the piston and the return tank extends upwardly through the transfer component. The boot defines a chamber charged with the transition component around the bellows between the upper surface and the return tank, is configured to maintain a constant volume of the chamber, and includes a first valve and a second valve each configured to open and close. The lower surface is under pressure by a pressurized fluid from a source thereof. The return configuration includes the first valve closed for isolating the transition component from the transfer component, the second valve open for opening the transition component to the transfer component, the access port closed, and the transfer port open for opening the return component to the transfer component. The reset configuration includes the second valve closed for isolating the transition component from the transfer component, the first valve open for opening the transition component to the transfer component, the access port open, and the transfer port closed for isolating the return component from the transfer component. When the bi-level tank is in the return configuration and the piston is in the lowered position, the piston is configured to displace from the lowered position to the raised position, the bellow is configured to retract between the upper surface and the return tank, and the boot is configured to retract between the upper surface and the return tank while maintaining the constant volume of the chamber, for exchanging a first volume of the transfer component in the bellows with a second volume of the fluid from the source for lifting the first volume of the transfer component in the bellows into the return component in the return tank and sourcing the second volume of the fluid from the source to the lower surface of the piston in response to activating the force-applying mechanism for applying a force on the piston sufficient to defeat a pressure differential on the piston produced by the upper surface and the lower surface under concurrent pressures from the return component and the fluid, respectively. When the bi-level tank is in the reset configuration and the piston is in the raised position, the piston is configured to displace from the raised position to the lowered position, the bellow is configured to extend between the upper surface and the return tank, and the boot is configured to extend between the upper surface and the return tank while maintaining the constant volume of the chamber, for exchanging the first volume of the return component in the return tank with the second volume of the fluid sourced to the lower surface of the piston for lowering the first volume of the return component in the return tank into the transfer component in the bellows and returning the second volume of the fluid sourced to the lower surface of the piston to the source in response to deactivating the force-applying mechanism for removing the force from the piston for reestablishing the pressure differential on the piston. The return component is arranged about a first axis. The piston is mounted for reciprocal movement between the lowered position and the raised position along a second axis. The first axis is parallel to the second axis. The bellows is fashioned of Kevlar, ballistic nylon, blimp envelop material, or other material or combination of materials having inherently flexible, strong, cut-resistant, inelastic, non-stretchable, and fluid-impervious material characteristics. The boot is formed of a resilient elastomeric material. The source includes a pressure tank sourcing the pressurized fluid to the lower surface of the piston. The pressurized fluid is a pressurized gas.

According to another exemplary embodiment of the invention, an apparatus includes a volume of water confined by a bi-level tank adjustable between a return configuration and a reset configuration. The bi-level tank includes a transfer tank including an access port configured to open and close, a return tank extending upright from the transfer tank, and a transfer port between the transfer tank and the return tank and configured to open and close. The volume of water includes a transfer component in the transfer tank and defining a lower water surface under the access port, a return component extending upright through the return tank from the transfer port and the transfer component to an upper water surface above the lower water surface, and a transition component. A piston in the transfer component is below the transfer port. The piston includes an upper surface and a lower surface and is mounted for reciprocal movement between a lowered position and a raised position. A force-applying mechanism is operatively coupled to the piston. An extensible and retractable upper bellows coupled between the piston and the return tank extends upwardly through the transfer component between the upper surface and the return tank and couples the return component to the upper surface under pressure from the return component. An extensible and retractable boot over the upper bellows and coupled between the piston and the return tank extends upwardly through the transfer component. The boot defines a chamber charged with the transition component around the upper bellows between the upper surface and the return tank, is configured to maintain a constant volume of the chamber, and includes a first valve and a second valve each configured to open and close. An extensible and retractable lower bellows coupled to the piston extends downwardly through the transfer component from the lower surface and couples a fluid under pressure from a source thereof to the lower surface under pressure from the fluid. The return configuration includes the first valve closed for isolating the transition component from the transfer component, the second valve open for opening the transition component to the transfer component, the access port closed, and the transfer port open for opening the return component to the transfer component. The reset configuration includes the second valve closed for isolating the transition component from the transfer component, the first valve open for opening the transition component to the transfer component, the access port open, and the transfer port closed for isolating the return component from the transfer component. When the bi-level tank is in the return configuration and the piston is in the lowered position, the piston is configured to displace from the lowered position to the raised position, the lower boot is configured to extend from the lower surface, the upper bellows is configured to retract between the upper surface and the return tank, and the boot is configured to retract between the upper surface and the return tank while maintaining the constant volume of the chamber, for exchanging a first volume of the transfer component in the upper bellows with a second volume of the fluid from the source for lifting the first volume of the transfer component in the upper bellows into the return component in return tank and sourcing the second volume of the fluid from the source to the lower bellows in response to activating the force-applying mechanism for applying a force on the piston sufficient to defeat a pressure differential on the piston produced by the upper surface and the lower surface under concurrent pressures from the return component and the fluid, respectively. When the bi-level tank is in the reset configuration and the piston is in the raised position, the piston is configured to displace from the raised position to the lowered position, the lower boot is configured to retract toward the lower surface, the upper bellows is configured to extend between the upper surface and the return tank, and the boot is configured to extend between the upper surface and the return tank while maintaining the constant volume of the chamber, for exchanging the first volume of the return component in the return tank with the second volume of the fluid in the lower bellows for lowering the first volume of the return component in the return tank into the transfer component in upper bellows and returning the second volume from the lower bellows to the source in response to deactivating the force-applying mechanism for removing the force from the piston for reestablishing the pressure differential on the piston. The return component is arranged about a first axis. The piston is mounted for reciprocal movement between the lowered position and the raised position along a second axis. The first axis is parallel to the second axis. The upper bellows and the lower bellows are each fashioned of Kevlar, ballistic nylon, blimp envelop material, or other material or combination of materials having inherently flexible, strong, cut-resistant, inelastic, non-stretchable, and fluid-impervious material characteristics. The boot is formed of a resilient elastomeric material. The source includes a pressure tank sourcing the pressurized fluid to the lower bellows. The pressurized fluid is a pressurized gas.

According to the invention, a bi-level tank includes a transfer tank with a transfer port configured to open and close and a return tank with an upper displacement line port and extending upright from the transfer tank to and beyond the upper displacement line port. The transfer port is between the transfer tank and the return tank. A displacement device is mounted for displacement in a displacement tank with a lower displacement line port. A displacement line coupled between the upper displacement line port above the transfer port and the lower displacement line port below the transfer port fluidly connects the return tank to the displacement tank. A balance line below the transfer port fluidly connects the transfer tank to the displacement tank. The displacement device is operatively coupled to the lower displacement line port, wherein displacement of the displacement device in the displacement tank effectuates fluid transfer between the displacement tank and the return tank via the displacement line. The balance line is below the displacement line. A valve with the displacement line is configured to open to enable fluid transfer through the displacement line between the return tank and the displacement tank and close to disable fluid transfer through the displacement line between the return tank and the exterior tank. a valve with the balance line is configured to open to enable fluid transfer through the balance line between the transfer tank and the displacement tank and close to disable fluid transfer through the balance line between the transfer tank and the exterior tank. There is a manhole to within the displacement tank and a manhole cover movable between a closed position to close the manhole and an open position to open the manhole. The displacement tank has a drain port configured to open to enable fluid to drain therethrough from the displacement tank and close to disable fluid from draining therethrough from the displacement tank. A force-applying mechanism is operatively coupled to the displacement device, wherein the displacement device displaces through the displacement tank when the force-applying mechanism activates to apply a force on the displacement device. The displacement device includes a piston with a first surface and a second surface, the piston configured to displace between a first position of the first surface away from the lower displacement line port and a second position of the first surface toward the lower displacement line port, an extensible and retractable bellows extending between the piston and the displacement tank, the lower displacement line port open to the first surface of the piston through the bellows, and an extensible and retractable boot with a first valve and a second valve each configured to open and close. The boot is over the bellows, extends between the piston and the displacement tank, defines a fluid chamber around the bellows between the first surface of the piston and the displacement tank, and is configured to maintain a constant volume of the fluid chamber. The bellows and the boot are extended when the piston is in the first position of the first surface and retracted when the piston is in the second position of the first surface. The second surface is under pressure by a pressurized fluid from a source thereof. The source is a pressure tank charged with the pressurized fluid, a pressurized gas, preferably pressurized air. The force-applying mechanism is operatively coupled to the piston, wherein the piston displaces from the first position of the first surface to the second position of the first surface when the force-applying mechanism activates to apply the force on the piston.

BRIEF DESCRIPTION OF THE DRAWINGS

Specific objects and advantages of the invention will become apparent to those skilled in the art from the following detailed description of illustrative embodiments thereof, taken in conjunction with the drawings in which:

FIG. 1 is a perspective view of a machine for the present invention;

FIG. 2A is a cross-section view of the machine as seen along the line 2-2 in FIG. 1, when the machine is configured to receive a power module;

FIG. 2B is a view of the machine as shown in FIG. 2A when the machine is configured to reorient the power module in the transfer tank of the present invention;

FIG. 2C is a view of the machine as shown in FIG. 2A after the power module has passed through the transfer tank and the transfer tank has been reconfigured to receive the next successive power module;

FIG. 3A is a cross-section view of a displacement device for use with the present invention, with the displacement device shown in a deactivated configuration;

FIG. 3B is a view of the displacement device as shown in FIG. 3A, with the displacement device in an activated configuration;

FIG. 4A is a perspective view of a power module in accordance with the present invention;

FIG. 4B is a cross-section view of the power module as seen along the line 4B-4B in FIG. 4A;

FIG. 5 is a cross-section view of the machine of the present invention showing a positioning of velocity and hydrodynamic sensors on the machine;

FIG. 6 is a table showing the correlation between a functional operation of the machine and the changeover operation of the valve mechanism of the present invention;

FIG. 7 is a velocity profile for a single power module during a duty cycle in accordance with an operation of the machine wherein four power modules are used, with a corresponding reference for each successive three power modules identified relative to the first power module;

FIG. 8 is a diagram of interconnected components required for operating and controlling an operation of the present invention;

FIG. 9 is a cross-section view like FIG. 3A illustrating an alternate embodiment of a displacement device for use with the present invention;

FIG. 10 is a partial side elevation view corresponding to FIG. 9 illustrating a constant volume boot of the displacement device;

FIGS. 11-14 illustrate a sequence of operation of the embodiment of FIG. 9;

FIG. 15 is a cross-section view of an alternate embodiment of a machine for the present invention; and

FIGS. 16-20 illustrate a sequence of operation of the embodiment of FIG. 15.

DETAILED DESCRIPTION

Referring to FIG. 1, a machine in accordance with the present invention includes a bi-level tank 12 adjustable between a return configuration and a reset configuration. The bi-level tank 12 confines a volume of water including a transfer component defining a lower water surface 42 of the volume of water and a return component defining an upper water surface 44 of the volume of water above the lower water surface 42. The bi-level tank 12 includes a lower transfer tank 14 holding the transfer component and an upper return tank 16 holding the return component. Return tank 16 and its contents extend upright from the transfer tank 14 and its contents. The transfer tank 14 includes an access port 34 and a transfer port 38 each configured to open and close. Return tank 16 is over and extends upright from the transfer port 38. The transfer component defines the lower water surface 42 of the volume of water under the access port 34. The return component extends upright through the return tank 16 from the transfer port 38 and the transfer component in transfer tank 14 to the upper water surface 44 of the volume of water. Machine 10 is configured to move a power module 18 through a duty cycle on a closed-loop pathway designated by dashed line 20 in FIG. 1. The duty cycle on pathway 20 includes a DOWN portion, indicated by arrow 22, and an UP portion, indicated by the arrow 24. A deflector/exit chute 26 connected to the top of the return tank 16 directs the power module 18 as it exits the bi-level tank 12. As will be appreciated with the additional disclosure presented below, an important consideration for the machine 10 is that it requires an external power source 28 for its operation. As envisioned for the present invention, the external power source 28 can be any such source well known in the art, such as a power grid provided by a commercial power company or some other external generator.

Additional aspects of the bi-level tank 12 will be appreciated with reference to FIG. 2A illustrating a launch platform 30 positioned above the transfer tank 14 at a location near the deflector/exit chute 26 of the return tank 16. At this location, the launch platform 30 is positioned to receive a power module 18 as it exits from the return tank 16 through the deflector/exit chute 26 at the end of a duty cycle. A rotating mechanism 32 is provided for the launch platform 30. When a power module 18 is received by the launch platform 30, it will be held on the launch platform 30 until the rotating mechanism 32 is activated to move the launch platform to an orientation indicated for launch platform 30′. The power module 18 will then be dropped from the launch platform 30′. After a power module 18 has been dropped, the orientation for launch platform 30 is reassumed to receive the next power module 18 in sequence. It is to be noted that an operation of the launch platform 30 requires power from the external power source 28.

Still referring to FIG. 2A, it will be seen that the transfer tank 14 includes an access port 34 above lower water surface 42 and which can be closed or opened by an access valve 36 and a transfer port 38 which can be closed or opened by a transfer valve 40. Transfer port 38 is between the transfer tank 14 and the return tank 16 extending upright therefrom. Because the access valve 36 and the transfer valve 40 must perform a changeover operation with each other, the valves are sometimes referred to, collectively in this disclosure, as a valve mechanism 36/40.

An operation of the valve mechanism 36/40, and its import for an operation of the machine 10, will be best appreciated with a successive consideration of FIGS. 2A, 2B and 2C. In FIG. 2A, it will be noted that the valve mechanism 36/40 is configured so that the access port 34 is open and the transfer port 38 is closed. With this starting configuration for the valve mechanism 36/40, the transfer tank 14 is isolated from the return tank 16 isolating the transfer component in the return tank 14 from the return component in the return tank 16 and there is no fluid communication between the transfer component in the transfer tank 14 and the return component extending upright through the return tank 16 from the transfer tank 14 and the closed transfer port 38 to the upper water surface 44. Also, the lower water surface 42 of the transfer component in the transfer tank 14 is exposed to only the atmosphere. The consequence of this configuration of the bi-level tank 12 is that a power module 18 can enter the transfer tank 14 through the open access port 34. Moreover, the kinetic energy of the power module 18 (½mv²) must only do work against an exposed lower water surface 42 that experiences a head height h₁, which is directly influenced by only the atmosphere.

In FIG. 2B the valve mechanism 36/40 is shown configured with the access port 34 closed and the transfer port 38 open in the return configuration of the bi-level tank 12. With this configuration for the valve mechanism 36/40 setting the bi-level tank 12 to its return configuration, the transfer tank 14 is open to the return tank 16 opening the transfer component in the transfer tank 14 to the return component extending upright from the transfer component and the now open transfer port 38 to the upper water surface 44. This establishes an unobstructed underwater pathway 20 from the transfer component in the transfer tank 14, through the return component of the return tank 1, and up to the atmospherically exposed water surface 44 of the return component. At this point however, although transfer component in the transfer tank 14 is subjected to an increased head height h₂, it is to be appreciated there is no adverse operational effect on the power module 18. In their relationship to each other, h₂>>h₁.

For the next successive configuration for the valve mechanism 36/40, FIG. 2C shows that the access port 34 has been opened and the transfer port 38 has been closed. This changeover operation puts the bi-level tank 12 to its reset configuration for receiving a next module 18 into the transfer tank 14. In accordance with the present invention, the successive configurations of valve mechanism 36/40 are repeated for each duty cycle of the power module 18.

As disclosed above, the valve mechanism 36/40 maintains different levels for the water surface 42 of the transfer component and the water surface 44 of the return component in the bi-level tank 12. Valve mechanism 36/40 operates to changeover the open and closed condition of the access port 34 and the transfer port 38 in the bi-level tank 12. For this purpose, the selection of a specific type valve mechanism 36/40 for each machine 10 will depend on the operational requirements of the machine 10 that is being constructed (e.g. structural strength required, size, timing and output power requirements). Thus, although many valve types can be considered for use with the machine 10, the selection of a particular valve type for the valve mechanism 36/40 is a design and engineering consideration that can, and often will, require an evaluation of many different types of valves; to include: globe valves, butterfly valves, gate valves, slide valves, ball valves, check valves, diaphragm valves, plug valves and pinch valves.

In general, the operation of a displacement device 46 in accordance with the present invention will be best appreciated with reference to FIGS. 2B and 2C. In FIG. 2B, the bi-level tank 12 is shown configured after a power module 18 has entered the transfer tank 14. Specifically, for this configuration the access port 34 is closed and the transfer port 38 is open setting bi-level tank 12 to its return configuration. At this point in a duty cycle, the water pathway 20 from the transfer tank 14 into the return tank 16 is unobstructed by the transfer valve 40 at the now open transfer port 38. It is also important to recognize that in FIG. 2B, the displacement device 46′ has been activated while the power module 18 is in the transfer tank 14, which is the same for the displacement device 100 discussed below in conjunction with FIGS. 9-20.

Structurally, the activated displacement device 46′ occupies a displacement volume V_din the transfer tank 14 that is equal to the volume V_mof the power module 18 (V_d=V_m). Displacement device 46 is configured to cyclically displace displacement volume V_dbetween the transfer and return components. To establish this relationship, a surface 48 of the displacement device 46, having a flat projection displacement area A_d, has been moved into the transfer tank 14 through a displacement distance d (i.e. V_d=A_dd). The result here is that in addition to the presence of a power module 18 of volume V_min the transfer tank 14, a volume of water equal to A_dd (i.e. V_d) has been displaced from the transfer tank 14 and moved into the return tank 16. Since V_d=V_m, the total water displaced from the transfer tank 14 for the configuration of the bi-level tank 12 shown in FIG. 2B, is V_d+V_m=2V_m.

In FIG. 2C, the power module 18 has progressed from the transfer tank 14 and into the return tank 16. Also, the displacement device 46 has been deactivated to remove a volume V_dof water from the transfer component in the transfer tank 14 and lift it into the return component of the return tank 16. The configuration of the bi-level tank 12 has also been changed to open the access port 34 and close the transfer port 38. The consequence of this is that the power module volume V_mhas moved into the return tank 16. Also, the displacement volume V_dhas been removed by a deactivated displacement device 46 to recover a volume of air V_dinto the transfer tank 14 that is equal to V_m. The result here is that the bi-level tank 12 has been reconfigured or otherwise reset to receive the next successive power module 18 (see FIG. 2A).

A displacement device 46 can have any one of several different structures. Accordingly, each structure will have correspondingly different components. It is possible that the displacement device 46 may be either pneumatically activated, mechanically activated or activated by a structure that requires both pneumatic and mechanical activation. For instance, as a pneumatic device, the displacement device 46 may employ compressed air to operate pressurized bellows or an inflatable bladder. On the other hand, for a mechanical device the displacement device 46 may employ a piston component that is activated by an electromagnetic drive, an electric drive or a mechanical drive. Stated differently, the present invention recognizes the possibility that different drive components may be employed to operate a displacement device 46 for the purposes of the present invention. In any case, it is necessary for the displacement device 46 to first displace a volume V_dof water from the transfer tank 14 as disclosed above. Then, the displacement device 46 needs to be timely activated in cooperation with the valve mechanism 36/40 to recover a same volume of air V_dinto the transfer tank 14, as also disclosed above.

With reference to FIGS. 3A and 3B, a displacement device 46 submerged in the transfer tank 14 of bi-level tank 12 is shown in a configuration where it is deactivated. The bi-level tank 12 is adjustable between the previously-described return configuration and the reset configuration and confines the volume of water including the transfer component in the transfer tank 14 and the return component in the return tank 16. In this embodiment, an extension 16A of return tank extends over part of transfer tank 14 over displacement device 46 submerged in the transfer component. As shown, the displacement device 46 has an outside upper surface 48, and it includes a piston 49 with opposite surfaces 50 and 51. The piston 49 is under and laterally offset from the transfer port 38 directly under the upwardly-extending return tank 16 and its return component. The piston 49 is oriented so its surface 50 is a downward-facing lower surface 50 and its surface 51 is an upward-facing inside upper surface 51. Also, FIG. 3A indicates that the lower surface 50 of the piston 49 has a surface area A that is in fluid communication with a pressure tank 52 which holds compressed air at a pressure p₁against piston's 49 lower surface 50. Thus, the lower surface 50 of the piston 49 will constantly be subject to or otherwise under a pressure of approximately p₁that exerts a force equal to p₁A on the lower surface 50. Further, FIG. 3A indicates that the inside upper surface 51 of the piston 49 is in fluid communication with the return tank 16 and it will thereby be constantly subject to or otherwise under a pressure p₂from the return component in the return tank 16.

Still referring to FIG. 3A, a bellows 54 surrounds the lower surface 50 of the displacement device 46 and interconnects the displacement device 46 with the pressure tank 52. Further, the displacement device 46 is shown to be mechanically connected directly to a force-applying mechanism 55, in this example a force actuator 56 that is external to the transfer tank 14 and operatively coupled to the piston 49 by a connector 57, which, in this embodiment, is a cable.

At this point in the duty cycle of a power module 18, in order to displace a volume V_dof water from the transfer tank 14, and to move it into the return tank 16, the outside upper surface 48 of the displacement device 46 must act against the water pressure p₂caused by the head height h₂in the transfer tank 14. In this case, the work required to displace V_dwill be equal to the product of the projected displacement area A_dfor the upper surface 48 of the displacement device 46, the pressure p₂in the return tank 16, and the displacement distance d that is required for a movement of the displacement device 46 to create a volume V_d(i.e. A_dp₂d).

In a preferred embodiment for the displacement device 46, fluid pressure p₁from pressure tank 52 is established in fluid communication with the lower surface 50 of the piston 49 of the displacement device 46. This pressure p₁on the lower surface 50 of piston 49 will act directly against the area A of the lower surface 50 and thereby create a biasing force Ap₁. This biasing force Ap₁will then directly oppose the force A_dp₂that acts against the upper surface 48 of the displacement device 46. Since the inside upper surface 51 of the piston 49 will be subject to the pressure p₂, a structure is created where the only pressure forces acting on the displacement device are p₁and p₂. Within this structural combination, the pressure p₂that is due to head height h₂in the return tank 16 and the pressure p₁from the pressure tank 52 can be respectively used to create a pressure differential Δp=p₂−p₁, wherein p₂>p₁. Thus, a force that is proportional to Δp will always act against the displacement device 46 to urge the displacement device 46 into its deactivated configuration. It is also to be appreciated that other devices can be used to create the bias force. For instance, instead of using compressed air, a spring can be used with an appropriate spring constant to establish Δp. Further, the use of a counteracting water column is possible. For example, water pressure from the return tank 16 can be directed against the lower surface 50 of the piston 49 to create Δp.

In any event, it is important that the bias force create a Δp that is relatively small, e.g. in a range between 1.5 and 2 psi. Accordingly, an activating force from the force actuator 56 that will raise the displacement device 46 through a distance d, against the force A_dp₂d that is caused by water in the transfer tank 14, need only be greater than A_dΔp. Preferably, the force actuator 56 of the force-applying mechanism 55 is a motorized winch-type motor operatively connected by the cable 57 with the inside upper surface 51 of the piston 49.

The power module 18 shown in FIGS. 4A and 4B is exemplary of a preferred structure for the power module 18 of the present invention. As shown, the power module 18 has an upper end 58, a body 60 and a lower end 62. Further, FIG. 4A shows that the lower end 62 can be modified for hydrodynamic purposes, such as by being slanted as shown by the dashed line for the lower end 62′. Depending on engineering design considerations, the length L of the power module 18 can be varied. Operationally, the power module 18 remains upright, i.e. with the upper end 58 remains above the lower end 62, during an entire duty cycle of the power module 18.

FIG. 4B, shows that the interior of a power module 18 will include an enclosed chamber 64 that is surrounded by a structure 66. This structure 66 will preferably be a strong heavy material, such as a metal, that is formed to create the exterior surface of the power module 18. For purposes of the present invention, the power module 18 will have weight W and a volume V_m.

As emphasized above, it is an important design consideration for the present invention that the power module 18 be buoyant. For this consideration, the weight W and the volume V_mare constant, and are predetermined. Thus, the buoyancy of the power module 18 must consider the weight that is added by components put into the chamber 64. For instance, it is envisioned that the chamber 64 will include a compartment 68 for holding electronics (e.g. sensors) and possibly magnets (not shown). Also, if necessary, materials including a support grid 70 can be erected in the interior of the chamber 64 for added strength and rigidity. In any event, as disclosed above, the power module 18 must be buoyant, and have a buoyancy factor that is preferably in a range between 0.6 and 0.75.

In accordance with above disclosure, and with reference to FIG. 5, it will be appreciated that an operation of the present invention requires precise velocity control over each power module 18 during its duty cycle. Preferably, by way of example, the present invention will involve a multi-module machine 10 that simultaneously uses four power modules 18. For purposes of the present invention, a plurality of position/velocity control sensors 72 are variously mounted on the machine 10. Additionally, a plurality of hydrodynamic sensors 74 are submerged in the bi-level tank 12. Further, FIG. 5 shows that an output power gauge 76 is mounted on an electric generator 78 that is connected with a linear drive component 80. As envisioned for the present invention, the linear drive component 80 may be either a mechanical chain drive, as show in FIGS. 2A-C, or it can be an electro-magnetic solenoid 80′, as shown in FIG. 5. With either structure, it is important that the power module 18 be securely engaged with the linear drive component 80/80′ as its kinetic energy is used to drive the electric generator 78.

The plurality of position/velocity sensors 72 are specifically located on the machine 10 to measure positions and velocities of each power module 18 as it passes selected points in the bi-level tank 12 during its respective duty cycle. Preferably, at least one position/velocity sensor 72 is positioned at the launch platform 30 to determine when a power module 18 is ready for launch. At least one position/velocity sensor 72 is located on the DOWN portion of the closed-loop pathway 20 to monitor the velocity v_eof power modules 18 while they are driving the electric generator 78 by their engagement with a linear drive component 80 for the electric generator 78.

Also, a plurality of position/velocity sensors 72 are positioned in the bi-level tank 12. More specifically, position/velocity sensors 72 are positioned in the transfer tank 14 to monitor the transfer of a power module 18 from the transfer tank 14 into the return tank 16. Further, position/velocity sensors 72 are positioned in the return tank 16 to ensure appropriate duty cycle locations for power modules 18 on the UP portion of the closed-loop pathway 20 in preparation for a subsequent exit from the return tank 16.

The plurality of hydrodynamic sensors 74 are submerged in the bi-level tank 12 to measure fluid characteristics of the water in the bi-level tank 12. In particular, at least one hydrodynamic sensor 74a records fluid pressure in the transfer tank 14 when the access port 34 is open and the transfer port 38 is closed. At least one other hydrodynamic sensor 74b records fluid pressure in the transfer tank 14 when the access port 34 is closed and the transfer port 38 is open. And, at least one hydrodynamic sensor 74c records fluid pressure in the transfer tank 14 to monitor variations Δ₁in the lower level water surface 42 of the transfer tank 14. The general purpose here is to provide hydrodynamic values that can affect the velocity of a power module 18 in the bi-level tank 12, and to provide information to a control unit 82 (see FIG. 8) pertaining to the level of the lower water surface 42 and the level of the upper water surface 44 together with their respective variations Δ₁and Δ₂that are needed for a timely operation of the valve mechanism 36/40. Additionally, the hydrodynamic sensors 74 in the transfer tank 14 provide important information to the control unit 82 regarding fluid pressure values in the transfer tank 14 that must be accounted for during a proper operation of the displacement device 46.

With reference to FIG. 6, the required operation of the valve mechanism 36/40 with the operation of the displacement device 46 is provided for reference purposes. Specifically, FIG. 6 correlates a functional operation of the machine 10 with the changeover required for an operation of the valve mechanism 36/40, and the corresponding configurations of the access port 34 and the transfer port 38. As disclosed above, a valve mechanism 36/40 is provided for maintaining different water surface levels in the bi-level tank 12. On the other hand, the displacement device 46 is required to accommodate the passage of a power module 18 through the transfer tank 14. The displacement device 46 is activated when the access port 34 is closed and the transfer port 38 is open. Furthermore, the displacement device 46 is deactivated when the access port 34 is open and the transfer port 38 is closed.

Operational control for the machine 10 will be best appreciated with reference to FIG. 7, where the velocity profile of an exemplary duty cycle 84 for one power module 18 is presented. FIG. 7, shows this duty cycle 84 in a context with the operation of the valve mechanism 36/40. When access valve 36 is open, transfer valve 40 will be closed and vice versa. Moreover, in FIG. 7, the duty cycle 84 for a single power module 18 is shown in a relation of its engagement time T_ewith the electric generator 78 and the engagement times 2-4 T_efor three additional power modules 18.

With reference to the timeline in FIG. 7, it is to be appreciated that a duty cycle 84 can be considered as extending from t₀to t₀. In this case, the engagement time T_e(see FIG. 5) will extend from t₂to t₃. For a four-module machine 10, as shown in FIG. 5, a complete duty cycle 84 for each power module 18 will have a duration equal to 4T_e.

With the above in mind, the positions and velocities of each power module 18 as it travels through a duty cycle 84 must necessarily be based on T_e. Also, as discussed above, there are two velocities in a duty cycle 84 that will remain substantially constant. First, the engagement velocity V_ethat a power module 18 has during a power phase 86 (see FIG. 1) of the duty cycle 84 needs to be constant during the time T_e. Specifically, V_eis constant while the power module 18 is engaged with the linear drive component 80 of the electric generator 78. Second, the velocity v_twhich is the terminal velocity attained by the power module 18 as it rises in the return tank 16, during a return phase 88 of the duty cycle 84, will remain constant. Module velocities other than v_eand v_tare transitional velocities which will either accelerate to v_eor v_t; or decelerate from v_eor v_tto zero.

FIG. 7 shows that from the time to when a power module 18 is dropped for free fall 90 from the launch platform 30 until it engages with the linear drive component 80 at time t₂, the velocity of a power module 18 increases from zero to v_e. For the present invention, v_ewill depend on the weight W of a power module 18, as well as the free fall distance 92 (see FIG. 5). Importantly, v_efor a power module 18 is established so it will generate the voltage and sine wave characteristics that are required by the end user (e.g. a commercial grid). Operationally, v_ecan be controlled by control unit 82 using output from power gauge 76 to determine appropriate loading for the linear drive component 80.

As shown, v_eis held constant between t₂and t₃for a time interval T_e. At the time t₃, as a power module 18 disengages from the linear drive component 80, the next successive power module 18 will simultaneously engage with the linear drive component 80. Also, it is important to note that at the time t₃, the access port 34 will be open to allow the disengaged power module 18 to enter the transfer tank 14. At this time, the transfer port 38 will accordingly be closed. As a safety feature, in order to ensure that access port 34 is indeed open, a mechanical trip switch 94 (see FIG. 5) can be provided at a predetermined distance above the access port 34. Shortly after t₃, however, i.e. once the power module 18 has entered the transfer tank 14, access port 34 closes and transfer port 38 opens.

Once the power module 18 is in the transfer tank 14, the displacement device 46 is activated to force a volume V_dof water from the transfer component in the transfer tank 14 to the return component of the return tank 16 through the now-open transfer port 38. Specifically, as noted elsewhere herein, this displaced volume V_dof water will be equal to the volume V_mof the power module 18 that is in the transfer tank 14 at the time.

While it is inside the transfer tank 14, the power module 18 will decelerate to zero (v=0). Then, as it is being reoriented in the transfer tank 14, the power module 18 will accelerate to its terminal velocity v_tas it transitions from the transfer tank 14 and into the return tank 16. It is important that the power module 18 leave the transfer tank 14 within the time interval T_eso the next power module 18 will be able to enter the transfer tank 14 during its respective duty cycle 84.

Still referring to FIG. 7 it will be appreciated that a power module 18 will maintain its terminal velocity v_tin the return tank 16 until it exits from the return tank 16. Before starting its next duty cycle 84, the power module 18 will decelerate from v_tto zero. Deceleration is then complete when the power module 18 is repositioned on the launch platform 30 to begin its next duty cycle 84 with another free fall 90.

With reference to FIG. 7, the above disclosure has been described in terms of a duty cycle 84 for only one power module 18. As has been noted, however, for an operation that involves a plurality of power modules 18 (e.g. four), each power module 18 will experience a same duty cycle 84. Moreover, each power module 18 will be engaged with the linear drive component 80 for a same time interval T_e. Thus, in this example the time duration of the duty cycle 84 for each power module 18 will be 4T_e.

As envisioned for the present invention, it may be desirable for there to be a plurality of power modules 18 concurrently engaged with the linear drive component 80. In this case, the time each power module 18 is reoriented in the transfer tank 14 will necessarily be shortened since there can only be one power module 18 at a time in the transfer tank 14.

Another consideration for the structure of a machine 10 is the incorporation of internal guides 96 that are referred to in FIG. 8. These guides can be positioned along the closed-loop pathway 20 to establish and maintain a controlled movement of the power module 18 through the machine 10 to include engagement with the electric generator 78 and a reorientation of the power module 18 in the transfer tank 14. For this purpose, internal guides 96 can be positioned along the portion of closed-loop pathway 20 where power modules 18 engage with the linear drive component 80 of electric generator 78. Internal guides 96 can also be appropriately positioned in the bi-level tank 12. The particular structures used for internal guides 96 will depend primarily on engineering design criteria, the size and shape of power modules 18, and the operational requirements for a machine 10. With this in mind, internal guides 96 will typically be rollers, rails, bulkheads, barriers, restraints, magnets, or a combination of these various structures.

Referring now to FIG. 8, it will be seen that the control unit 82 is connected in electronic communication with a timer 98 and with other electronic and mechanical components of the machine 10. Specifically, the control unit 82 uses the timer 98 to coordinate the operation of the various system components. In particular, these components include the launch platform 30, the displacement device 46 and the valve mechanism 36/40. They also include the internal guides 96 that assist in keeping power modules 18 on the closed-loop pathway 20 during a duty cycle 84.

FIG. 9 is similar to FIG. 3A and illustrates the bi-level tank 12 configured with an alternate embodiment of a displacement device 100. The bi-level tank 12 incorporating the displacement device 100 confines the volume of water and adjusts or cycles repeatedly between return and reset configurations. The displacement device 100 is configured to repeatedly displace between a deactivated configuration and an activated configuration for repeatedly displacing a volume V_dof water between the transfer component in the transfer tank 14 and the return component of the return tank 16. The displacement device 100 is un-displaced when deactivated to its deactivated position. The displacement device 100 is displaced when activated to its activated position.

The bi-level tank 12 includes the previously-described transfer tank 14, the return tank 16 extending upright from the transfer tank 14, the access port 34 configured to open and close by access valve 36, and the transfer port 38 configured to open and close by transfer valve 40. The volume of water includes the transfer component in the transfer tank 14, the return component in the return tank 16, and, according to this embodiment, a transition component in and managed by the displacement device 100. The transfer component defines the lower water surface 42 under the access port 34. The return component extends upright through the return tank 16 from the transfer port 38 and the transfer component 14 to the upper water surface (See FIG. 2A) above the lower water surface 42. The return tank's 16 extension 16A extends over part of the transfer tank 14 over the displacement device 100 submerged in the transfer component in the transfer tank 14 and shown deactivated.

The displacement device 100 operates to displace volume V_dbetween the transfer and return components cyclically during each duty cycle. The displacement device 100 includes the previously-described piston 49 in the transfer component below and laterally offset from the transfer port 38 directly under the upwardly-extending return tank 16 and its return component contents. The piston 49 includes the downwardly-facing lower surface 50 and the upwardly-facing upper surface 51, and mechanically and operatively connected to the previously described force-applying mechanism 55. The return component and the transfer tank 16 are arranged about vertical axis X1. Piston 49 is mounted for reciprocal movement vertically along axis X2 between a lowered position in FIGS. 9, 10, and 14, and a raised displaced position in FIGS. 12 and 13. Axis X1 is parallel to axis X2.

An extensible and retractable bellows 102 is coupled between the piston 49 and the return tank 16 at return tank's 16 extension 16A. The bellows 102, the upper bellows of the displacement device 100, is a tubular concertina bellows made of Kevlar, ballistic nylon, blimp envelop material, or other material or combination of materials having inherently flexible, strong, cut-resistant, inelastic, non-stretchable, and fluid-impervious material characteristics. The transfer component fills the bellows 102 extending upwardly through the transfer component between the upper surface 51 of the piston 49 and the return tank's 16 extension 16A. The bellows 102 opens the upper surface 51 and the water in the bellows 102 to the return component fluidly coupling the return component to the piston's 49 transfer component contents and the upper surface 51 under pressure p₂from the return component.

The bellows 102 includes open ends 104 and 106. Based on the upright orientation of the bellows 102, the open end 104 is the lower open end of the bellows 102 and the open end 106 is the upper open end of the bellows 12. Bellows 102 extends upright from its lower open end 104 centered on and affixed to piston's 49 upper surface 51 to the open upper end 106 affixed to the transfer tank 14 around a displacement port 108 of the transfer tank 14 that is open to the return tank 16 at its extension 16A. The open lower end 104 is open to the upper surface 51 of the piston 49 and open upper end 106 that is open to the return tank 16 and its return component contents via the displacement port 108. This fluidly couples the return tank 16 and its return component to the bellows 102, the transfer component in the bellows 102, and the upper surface 51. The transfer component in the bellows 102 and piston's 49 upper surface 51 are under pressure p₂from the return component that communicates fluidly with the bellow's 102 transfer component extending downwardly therethrough from the open upper end 106 at the port 108 to the lower open end 104 and the piston's 49 upper surface 51.

An extensible and retractable constant volume boot 110 is over the bellows 102 and coupled between the piston 49 and the return tank 16. The boot 110, a housing, surrounds the bellows 102 between the open lower end 104 and the open upper end 106. The boot 100 extends upwardly through the transfer component between the piston's 49 upper surface 51 and the transfer tank 14. The boot 110 defines a chamber 111, a fluid chamber, charged with the transition component around the bellows 102 between the upper surface 51 of the piston 49 and the return tank 16. The boot 110 is configured to maintain a constant volume of chamber 111 and its transition component contents.

Referring in relevant part to FIGS. 9 and 10, the boot 110, formed of a resilient elastomeric material, includes collars 112 and 114, and a body 116. Based on the upright orientation of the boot 110, the collar 112 is the boot's 110 lower collar and the collar 114 is the boot's 110 upper collar. The body 116 extends between the lower collar 112 and the upper collar 114. The body 116 defines the fluid chamber 111 between the lower collar 112 and the upper collar 114 and includes conical sections 120 and 122 and an intermediate ring section 124. Based on the upright orientation of the boot 110, the conical section 120 is the lower conical section of the boot 110 and the conical section 122 is the upper conical section of the boot 110. The lower and upper conical sections 120 and 122 are integrally formed at their narrow portions with the respective lower and upper collars 112 and 114 by flexible hinges 126 and 128, respectively, and at their widened portions with intermediate ring section 124 by flexible hinges 130 and 132, respectively. The flexible hinges 126, 128, 130, and 132 are thinned regions of the body 116 that allow the lower conical section 120, the upper conical section 122, and the intermediate ring section 124 to pivot about these points relative to one another. Sections 120, 122, and 124, have axial profiles 134, convolutions, ribs, or both, for maintaining the sections 120, 122, and 124, axially rigid when boot 110 extends and retracts. These profiles 134 also permit the sections 120, 122, and 124, to circumferentially expand and retract when the boot 110 extends and retracts to maintain a constant volume within chamber 111. The boot 110 is a standard constant volume boot of known construction. Accordingly, additional details of the boot 110 are not discussed.

According to the invention, the lower collar 112 affixed to piston's 49 upper surface 51 surrounds the open lower end 104 of the bellows 102. The upper collar 114 affixed to an underside of the transfer tank 14 surrounds the open upper end 106 of the bellows 10. The body 116 surrounds the bellows 102 between the lower and upper collars 112 and 114 and extends upright through the transfer component from the lower collar 112 to the upper collar 114. The lower conical section 120 extends upright from hinge 126, connecting the lower conical section 120 to the lower collar 112, to hinge 130, connecting the lower conical section 120 to the intermediate ring section 124. The upper conical section 122 extends upright from hinge 132, connecting the upper conical section 122 to the intermediate ring section 124, to hinge 128, connecting the upper conical section 122 to the upper collar 114. The body 116 forms the chamber 111 about the bellows 102 extending upright through the chamber 111 from the lower collar 112 at bellow's 102 open lower end 104 to the upper collar 114 at the bellow's 102 open upper end 106.

According to the invention, the boot 110 has valves 140 and 142 configured to open and close independently. When valve 140 is open, it opens chamber 111 to transfer tank 14, opening the transition component in chamber 111 to the transfer component in transfer tank 14. When valve 140 is closed, it isolates chamber 111 from transfer tank 14, isolating the transition component in chamber 111 from the transfer component in transfer tank 14. When valve 142 is open, it opens chamber 111 to transfer tank 14, opening the transition component in chamber 111 to the transfer component in transfer tank 14. When valve 142 is closed, it isolates chamber 111 from the transfer tank 14, isolating the transition component in chamber 111 from the transfer component in transfer tank 14. In this embodiment, the valves 140 and 142 are on opposite sides of the upper conical section 122. In alternate embodiments, the valves 140 and 142 can be formed on opposite sides of the lower conical section 120, on opposite sides of the respective lower and upper sections 120, or elsewhere. Valves 140 and 142, the valve mechanism of the boot 110, are any of the valve types discussed above with valves mechanism 36/40.

Referring again to FIG. 9, an extensible and retractable bellows 150 is coupled between the piston 49 and the pressure tank 52, the preferred source of the pressurized fluid that pressure tank 52 sources to piston's 49 lower surface 51 via bellows 150. The bellows 150, the lower bellows of the displacement device 100, is a tubular concertina bellows made of Kevlar, ballistic nylon, blimp envelop material, or other material or combination of materials having inherently flexible, strong, cut-resistant, inelastic, non-stretchable, and fluid-impervious material characteristics. The bellows 150 is coupled to the piston 49. It extends downwardly through the transfer component from its open end 152 centered on and affixed to the lower surface 51 of the piston 49 to its end 154 coupled to the pressure tank 52 fluidly. Based on the upright orientation of the bellows 150, the open end 152 is the open upper end of the bellows 150 and the open end 154 is the open lower end of the bellows 150. The bellows 150 couples piston's 49 lower surface 50 to the pressure tank 52 fluidly. The pressure tank 52 sources the pressurized fluid to and holds it against piston's 49 lower surface 50 under constant pressure p₁from pressure tank's 52 pressurized fluid. The lower surface 50 of the piston 49 has the surface area A in fluid communication with the pressure tank 52 that holds the pressurized fluid, preferably compressed air, at pressure p₁against the lower surface 50. A conduit 160 fluidly coupled between the pressure tank 52 and bellow's 150 lower end 154 couples the pressure tank 52 to the bellows 150 fluidly. Thus, the piston's 49 lower surface 50 is constantly under pressure p₁that exerts the force equal to p₁A on the lower surface 50. The upper surface 51 of the piston 49 in fluid communication with the return tank 16 is constantly under pressure p₂from the return component in the return tank 16.

In the return configuration of the bi-level tank 12, valve 142 is closed, isolating the transition component in chamber 111 from the transfer component in transfer tank 14. Valve 140 is open, opening the transition component in chamber 111 to the transfer component in transfer tank 14. Access port 34 is closed. Transfer port 38 is open, opening the return component in return tank 16 to the transfer component in transfer tank 14.

In the reset configuration of the bi-level tank 12 in FIG. 11, valve 140 is closed, isolating the transition component in chamber 111 from the transfer component in transfer tank 14. Valve 142 is open, opening the transition component in chamber 111 to the transfer component in transfer tank 14. Access port 34 is open. Transfer port 38 is closed, isolating the return component in return tank 16 from the transfer component in transfer tank 14.

When the displacement device 100 is deactivated in FIGS. 9, 11, and 14 to its deactivated or un-displaced configuration, piston 49 is in its lowered position. Bellows 150 is retracted between its lower end 154 and piston's 49 lower surface 50. Bellows 102 is extended between piston's 49 upper surface 51 and return tank 16. Boot 110 is extended between piston's 49 upper surface 51 and return tank 16.

When the displacement device 100 is activated in FIGS. 12 and 13 to its activated or displaced configuration, piston 49 is in its raised position. Bellows 150 is extended between its lower end 154 and piston's 49 lower surface 50. Bellows 102 is retracted between piston's 49 upper surface 51 and return tank 16. Boot 110 is extended between piston's 49 upper surface 51 and return tank 16.

When the bi-level tank 12 is in its return configuration, the displacement device 100 is configured to activate to its activated or displaced configuration in FIGS. 12 and 13 from its deactivated or un-displaced configuration in FIG. 11 in response to activating the force-applying mechanism 55. When it activates, the force-applying mechanism 55 applies a force on the piston 49 sufficient to defeat the pressure differential Δp on the piston 49 produced by the upper surface 51 and the lower surface 50 under the concurrent pressures from the return component and the pressurized fluid, respectively. When the force applied to the piston 49 by the activated force-applying mechanism 55 defeats the pressure differential Δp, the piston 49 automatically displaces out of its lowered position to its raised position. At the same time, the bellows 150 extends between its lower end 154 and the lower surface 50 of the piston 49, the bellows 102 retracts between the upper surface 51 of the piston 49 and the return tank 16, and the boot 110 retracts between the upper surface 51 of the piston 49 and the return tank 16 while maintaining the constant volume of the chamber 111. This exchanges volume V_dof the transfer component in bellows 102 with a corresponding volume of the fluid (i.e., the pressurized fluid) from pressure tank 52, lifting volume V_dof the transfer component in bellows 102 into the return component in return tank 16 through port 108 and sources the corresponding volume of the fluid from pressure tank 52 to bellows 150.

When the bi-level tank 12 is in its reset configuration, the displacement device 100 is configured to deactivate to its deactivated configuration in FIG. 14 from its activated configuration in FIG. 13 in response to deactivating the force-applying mechanism 55. When the force-applying mechanism deactivates, it withdraws its force from the piston 49, automatically reestablishing the pressure differential Δp on the piston 49 produced by the upper surface 51 and the lower surface 50 under concurrent pressures from the return component and the pressure tank′ 52 fluid, respectively. When the force from the force-applying mechanism 55 withdraws from the piston 49, it automatically displaces from its raised position to its lowered position. At the same time, the bellows 150 retracts between its lower end 154 and the lower surface 50 of the piston 49, the bellows 102 extends between the upper surface 51 of the piston 49 and the return tank 16, and the boot 110 extends between the upper surface 51 of the piston 49 and the return tank 16 while maintaining the constant volume of the chamber 111. This exchanges volume V_dof the return component in return tank 16 with the corresponding volume of the fluid in bellows 150, lowering volume V_dof the return component in return tank 16 through port 108 into the transfer component in bellows 102 and returning the corresponding volume of the fluid from bellows 150 to pressure tank 52.

In FIG. 9, the displacement device 100 is deactivated to its un-displaced configuration. Access port 34 is open, enabling power module 18 to enter the transfer component in transfer tank 14 through open access port 34 as shown in FIG. 11 and translate along pathway 20. Transfer port 38 is closed, isolating the return component in return tank 16 from the transfer component in transfer tank 14. Boot's 110 valves 140 and 142 are closed, isolating the transition component in chamber 111 from the transfer component in transfer tank 14. Lower surface 50 of piston 49 is constantly under pressure p₁that exerts a force equal to p₁A on lower surface 50. Upper surface 51 of piston 49 is under constant pressure p₂from the return component in return tank 16.

Upon the power module 18 entering the transfer component through the open access port 34 in FIG. 11, access port 34 closes, valve 140 opens, and transfer port 38 opens. This sets bi-level tank 12 to its return configuration, which opens transfer tank 14 and its contents to return tank and its contents. The return configuration of bi-level tank 12 establishes the unobstructed underwater pathway 20 from transfer tank 14 through the return tank 16 and up to the atmospherically exposed water surface of the return tank 16 extending upright from transfer tank 14. At this stage, the transfer component in transfer tank 14 and bellows 102 and the transition component in boot's 110 chamber 111 are under pressure p₂produced by the increased head height h₂.

The displacement device 100 activates while the power module 18 is in transfer tank's 14 transfer component, displacing from its deactivated configuration in FIG. 11 to its activated configuration in FIG. 12. This displaces volume V_dfrom transfer tank 14 to return tank 16, and power module 18 progresses along pathway 20 from transfer tank 14 to return tank 16 through open transfer port 38. When displacement device 100 activates, the upper surface 51 of the piston 49 must act against the water pressure p₂caused by the head height h₂in the bi-level tank 12 to displace the volume V_dof water through the port 108 from the bellows 102 in the transfer tank 14 to the return tank 16. The work required to displace V_dwill be equal to the product of the projected displacement area for the upper surface 51 of the piston 49, the pressure p₂in the return tank 16, and the displacement distance d required for a movement of the displacement device 100 to displace volume V_d.

The pressure tank 52, the preferred source of the pressurized fluid, sources the pressure p₁of its pressurized fluid to lower surface 50 of piston 49. This pressure p₁held against lower surface 50 acts directly against lower surface's 50 area A to create the biasing force Δp₁. This biasing force Δp₁directly opposes the force of pressure p₂that acts against piston's 49 upper surface 51. Thus, a structure is created where the pressure forces acting on the displacement device 100 are p₁and p₂. The pressure p₂from the head height h₂in the return tank 16 and the pressure p₁from the pressurized fluid from the pressure tank 52 create the pressure differential Δp=p₂-p₁across the piston 49, wherein p₂>p₁. Thus, a force proportional to Δp will constantly act against the piston 49 to urge it into its deactivated configuration in FIG. 9. The boot's 110 now open valve 140 equalizes the pressure p₂between transfer tank's 14 transfer component and the transition component in chamber 111, the volume of chamber 111 maintained constant by the boot 110. As described previously, the bias force creates Δp that is relatively small, e.g., in a range between 1.5 and 2 psi. Accordingly, the activating force on the piston 49 from the force-applying mechanism 55 sufficient to overcome the pressure differential Δp to displace piston 49 distance d from its lowered position in FIG. 11 to its raised position in FIG. 12 need only be greater than pressure p₂.

While the power module 18 is in transfer tank's 14 transfer component, the displacement device 100 displaces from its deactivated configuration in FIG. 11 to its activated configuration in FIG. 12 when the displacement device 100 activates. This concurrently displaces the volume V_dof water from the bellows 102 in the transfer tank 14 to the return tank 16 and the same volume of fluid from the pressure tank 52 to the bellows 150 by the upwardly-displacing piston 49. The displacement device 100 activates in response to activating the force-applying mechanism 55, applying its force on the piston 49 sufficient to defeat the pressure differential Δp across the piston 49, enabling the piston 49 to displace from its lowered position to its raised position automatically. At the same time, the power module 18 progresses along pathway 20 through the open transfer port 38 from the transfer tank 14 and into the return tank 16 in FIG. 13. When displacement device 100 activates in FIG. 11, it cycles from its deactivated configuration to its activated configuration in response to activating the force-applying mechanism 55, applying its force on the piston 49 sufficient to defeat the pressure differential Δp on the piston 49. This exchanges the volume V_dof the transfer component in the bellows 102 with the corresponding volume of the pressurized fluid from the pressure tank 52, lifting the volume V_dof the transfer component in the bellows 102 into the return component in return tank 16 through port 108 by the upper surface 51 of the upwardly-displacing piston 49 and sourcing the corresponding volume of the fluid from the pressure tank 52 to the bellows 150 by the lower surface 50 of the upwardly-displacing piston 49.

The open valve 140 opening the transition component in chamber 111 to the transfer tank's 14 transfer component while the displacement device 100 displaces from its deactivated configuration to its activated configuration equalizes the pressure p₂between the transfer component and the transition component. This pressure equalization between the transition and transfer components and the inherent ability of the boot 110 to maintain the chamber's 111 volume constant causes the chamber's 111 volume to remain fixed or otherwise unchanged while the boot 110 retracts between the upper surface 51 of the piston 40 and the return tank 16 in response to movement of the piston 49 from its lowered position in FIG. 11 to its raised position in FIG. 12. This disables volume loss in the transfer tank 14 enabling the described exchange of the volumes.

After the power module 18 transitions through the transfer port 38 from the transfer component in the transfer tank 14 to the return component in the return tank 16 in FIG. 13, the bi-level tank 12 transitions from the return configuration to the reset configuration and the displacement device 100 deactivates from its activated configuration to its deactivated configuration. This concurrently displaces volume V_dfrom the return component in the return tank 16 to the bellows 102 in the transfer tank 14 and returns the same volume of fluid from the bellows 150 to the pressure tank 52 by the downwardly-displacing piston 49. When the bi-level tank 12 transitions to the reset configuration in FIG. 13 from the return configuration in FIG. 12, the transfer port 38 closes, the valve 140 closes, the valve 142 opens, and the access port 34 opens. The transition from the return configuration to the reset configuration closes the transfer tank 14 from the return tank 16, isolating the transfer component in the transfer tank 14 from the return component in the return tank 16, and severs pathway 20 from the transfer tank 14 to the return tank 16. It also withdraws the pressure p₂from the transfer component in the transfer tank 14 and the transition component in the boot's 110 chamber 111. The transfer component in the bellows 102 and the upper surface 51 of the piston 49 remain under pressure p₂via the open port 108 coupling the bellows 102 and its contents to the return tank 16 and its contents.

While the power module 18 is in return tank's 16 return component, the displacement device 100 displaces from its activated configuration in FIG. 13 to its deactivated configuration in FIG. 14 in response to deactivation of the displacement device 100. Displacement device 100 deactivates and cycles from its activated configuration in FIG. 13 to its deactivated configuration in FIG. 14 in response to deactivation of the force-applying mechanism 55, removing its force on the piston 49. This reestablishes the pressure differential Δp across the piston 49, causing the piston 49 to displace from its raised position to its lowered position automatically under the influence of pressure p₂. The pressure differential Δp reestablished on the piston 49 when the displacement device 100 deactivates automatically displaces the piston 49 from its raised position to its lowered position, displacing the displacement device 100 from its activated configuration in FIG. 13 to its deactivated configuration in FIG. 14. This exchanges volume V_dof the return component in return tank 16 with the corresponding volume of the fluid in bellows 150, lowering the volume V_dof from the return component into bellows 102 through port 108 by upper surface 51 of the downwardly-displacing piston 49 and returning the corresponding volume of the fluid from bellows 150 to pressure tank 52 by lower surface 50 of the downwardly-displacing piston 49.

The open valve 142 opening the transition component in the chamber 111 to the transfer tank's 14 transfer component while the displacement device 100 displaces from its activated configuration to its deactivated configuration equalizes the pressure between the transfer component in the transfer tank 14 and the transition component in the boot's 110 chamber 111. This pressure equalization between the transition and transfer components and the inherent ability of the boot 110 to maintain chamber's 111 volume constant causes the chamber's 111 volume to remain fixed or otherwise unchanged while boot 110 extends between the upper surface 51 of the piston 40 and the return tank 16 in response to movement of the piston 49 from its raised position in FIG. 13 to its lowered position in FIG. 14. This disables volume loss in the transfer tank 14 enabling the described exchange of the volumes.

Upon displacement device 100 reaching its displaced configuration in FIG. 14, the valve 142 closes isolating the transition component in the boot's 110 chamber 111 from the transfer component in the transfer tank 14, resetting bi-level tank 12 to its configuration in FIG. 9 ready to receive the next successive power module 18. In accordance with the present invention, the successive configurations of the bi-level tank 12 and the displacement device 100 are repeated for each power module 18 duty cycle.

Like FIG. 9, FIG. 15 illustrates a tank structure 200 that confines the volume of water and adjusts or cycles between return and reset configurations. The tank structure 200 includes the bi-level tank 12, a displacement tank 202, the displacement device 100, an alternate embodiment of the force-applying mechanism 55, and two lines fluidly connecting the displacement tank 200 to the bi-level tank 12, including a displacement line 204 and a separate balance line 206. The displacement and balance lines 204 and 206 are suitable conduits or pipes that allow for fluid flow between the bi-level tank 12 and the external displacement tank 202. Instead of being in the transfer tank 14, the displacement device 100, the assembly of the piston 49, the bellows 102, the boot 110, and the bellows 150, are in the displacement tank 202.

The bi-level tank 12 includes the previously-described transfer tank 14, the return tank 16 extending upright from the transfer tank 14, the access port 34 configured to open and close by the access valve 36, and the transfer port 38 configured to open and close by the transfer valve 40. For reference purposes, the transfer tank 14 has opposite upright sides 14A and 14B extending between a top 14C of the transfer tank 14 over a bottom 14D of the transfer tank 14. The return tank 16 extends upright from the top 14C of transfer tank 14. The access port 34, the access valve 36 and the transfer port 38 between the transfer tank 14 and the return tank 16 are in the top 14A of the transfer tank 14. The displacement tank 202, an external tank serviceable independently from the bi-level tank 12, is beside and external of the bi-level tank 12 and below the bi-level tank's 12 transfer port 38. For reference purposes, the displacement tank 202 has opposite upright sides 202A and 202B extending between a top 202C of the displacement tank 202 over a bottom 202D of the displacement tank 202. The displacement tank 202 is laterally offset from the side 14A of the transfer tank 14, the side 202B of the displacement tank 202 facing the side 14A of the transfer tank 14.

The displacement line 204 is coupled between the return tank's 16 upper displacement line port 210 above the transfer port 38 and the displacement tank's 202 lower displacement line port 212 below the transfer port 38, fluidly connecting the return tank 16 to the displacement tank 202. The upper displacement line port 210 open to the return tank 16 and its return component is above transfer tank 14. The return tank 16 extends upright from the top 14C of the transfer tank 14 to and beyond the upper displacement line port 210 above the top 14C and its access and transfer ports 34 and 38. The displacement line 204 extends downward from the upper displacement line port 210 to the lower displacement line port 212 open to the displacement tank 202 and its displacement component, the lower displacement line port 212 formed in the displacement tank's 202 side 202B between the displacement tank's 202 top 202C and bottom 202D. The balance line 206 below the displacement line 204 is coupled between the transfer tank's 14 balance line port 220 in the transfer tank's 14 side 14A near the transfer tank's 14 bottom 14C and the displacement tank's 202 balance line port 222 in the displacement tank's 202 side 202B between the lower displacement line port 212 and the displacement tank's 202 bottom 202D, fluidly connecting the transfer tank 14 to the displacement tank 202. The balance line 206 and the balance line ports 220 and 222 are below the displacement line 204 and the lower displacement line port 212 between the displacement tank 202 and the displacement line 204.

The displacement line 204 has a displacement line valve 230 between the upper displacement line port 210 and the lower displacement line port 212. The valve 230 with the displacement line 204 is configured to open to enable fluid transfer through the displacement line 204 between the return tank 16 and the displacement tank 202 and close to disable fluid transfer through the displacement line 204 between the return tank 16 and the exterior tank 202.

The balance line 206 has a balance line valve 232 between the transfer tank's 14 balance line port 220 and the displacement tank's 202 balance line port 222. The valve 232 with the balance line 206 is configured to open to enable fluid transfer through the balance line 206 between the transfer tank 14 and the displacement tank 202 and close to disable fluid transfer through the balance line 206 between the transfer tank 16 and the exterior tank 202.

The volume of water includes the transfer component in the transfer tank 14, the return component in the return tank 16, and a displacement component in the displacement tank 202. Transition and working components of the displacement tank's 202 displacement component are managed by the displacement device 100 submerged in the displacement tank's 202 displacement component. The displacement device 10 is deactivated in FIG. 15. The transfer component defines the lower water surface 42 under the access 34. The return component extends upright through the return tank 16 from the transfer component and the transfer port 38 to and beyond the upper displacement line port 210 to the upper water surface (See FIG. 2A) above the lower water surface 42. The displacement tank 202 and its contents are below the access and transfer ports 34 and 38 and the lower water surface 42. The displacement line 204 extends downward from the upper displacement line port 210 above the transfer tank and the lower water surface 42 to the lower displacement line port 212 below the access and transfer ports 34 and 38 and the lower water surface. The balance line 206 and the balance line ports 220 and 222 are below the lower water surface 42.

The displacement device 100 in the embodiment of FIGS. 9-14 is configured to repeatedly displace vertically along vertical axis X2 between its deactivated configuration and its activated configuration to repeatedly displacing volume V_dof water between the transfer component in the transfer tank 14 and the return component of the return tank 16. The displacement device 100 in tank structure 200 works likewise displaces volume V_dof water. However, instead of displacing volume V_dof water between the transfer component in the transfer tank 14 and the return component of the return tank 16 in the embodiment of FIGS. 9-14, the displacement device 100 in tank structure 200 is configured to repeatedly displace between its deactivated configuration and its activated configuration to repeatedly displace volume V_dof water between the displacement component in the displacement tank 202 and the return component of the return tank 16 via the displacement line 204 fluidly coupling the displacement tank 202 to the return tank 16. Also, the displacement device 100 of the tank structure 200 is configured to repeatedly displace horizontally along horizontal axis Y between its deactivated configuration and its activated configuration to repeatedly displace the volume V_dof water between displacement and return tanks 202 and 16, in which axis Y is perpendicular to axis X1. Like the displacement device 100 of the embodiment of FIGS. 9-14, the displacement device 100 of the tank structure 200 is un-displaced when deactivated to its deactivated position and displaced when activated to its activated position.

The displacement device 100 submerged in the displacement tank's 202 displacement component is configured to repeatedly displace between its deactivated and activated configurations for displacing the volume V_dof water cyclically during each duty cycle between the working component of the displacement tank's 202 displacement component and the return component of the return tank 16. The displacement device 100 of the tank structure 200 is, therefore, inherently useful for displacing water between the working component of the displacement tank's 202 displacement component and the return component of the return tank 16. The displacement device 100 includes the previously-described piston 49 with surfaces 50 and 51. In this embodiment, the piston 49 is oriented so its surface 50 is an upright outer side surface that faces the displacement tank's 202 side 202A and its opposite surface 51 is an upright inner side surface that faces the displacement tank's 202 side 202B and the lower displacement port 212 to the displacement line 204. The piston's 49 surface 51 is open to the lower displacement port 212 to the displacement line 204. The piston's 49 surface 50 is operatively coupled to the previously described pressure tank 52 fluidly and mechanically and operatively connected to the force-applying mechanism 55.

In this embodiment, the force-applying mechanism 55 is an actuator 240 operating a hydraulic drive mechanism 242. The actuator 240 is a standard hydraulic pump device external of the displacement tank's 202 side 202A. The hydraulic drive mechanism 242, a standard cylinder assembly including a stationary cylinder 244 and a reciprocating operating rod 246, is connected at respective ends to the actuator 240 and the piston's 49 surface 50, the cylinder 244 coupled between the actuator 240 and the operating rod 246 coupled between the cylinder 244 and the surface 50 of the piston 49. The operating 246 is mounted partially within the cylinder 244. The hydraulic drive mechanism 242 is of the standard double acting type, whereby the operating rod 246 is driven in reciprocal directions, extending from and retracting into the cylinder 244, when the actuator 240 activates. The cylinder 244 connected to the actuator 240 extends into the displacement tank 202 from the actuator 240 to the operating rod 246 connected to the surface 50 of the piston 49. The return component and the transfer tank 16 are arranged about upright axis X1. The piston 49 is mounted for reciprocal displacement along horizontal axis Y between its first or outer position away from the lower displacement line port 212 in FIGS. 15, 16, 19, and 20, and its second or inner position toward the lower displacement line port 212 in FIGS. 17 and 18. In FIGS. 15, 16, 19, and 20, the surface 51 of the piston 49 is in a first position displaced away from the lower displacement line port 212 when the piston 49 is in its first or outer position. In FIGS. 17 and 18, the surface 51 of the piston 49 is in a second position displaced toward the lower displacement line port 212 when the piston 49 is in its second or inner position. Again, axis Y is perpendicular to axis X1.

The previously-described bellows 102 is coupled between the piston 49 and the side 202B of the displacement tank 202. The displacement component's working component fills the bellows 102 extending laterally through the displacement component between the surface 51 of the piston 49 and the side 202B of the displacement tank 202. The bellows 102, the outer bellows of the displacement device 100, opens the piston's 49 surface 51 to the lower displacement line port 212, fluidly coupling the return component of the return tank 16 to the working component in the bellows 102 via the displacement line 204 with the piston's 49 surface 51 under the pressure p₂applied to the working component in the bellows 102 from the return tank's 16 return component. The bellows 102 has open end 104 centered on and affixed to the piston's 49 surface 51 and extends laterally from the piston's 49 surface 51 to the open end 106 affixed to the displacement tank 202 around the lower displacement line port 212 open to the return tank 16 via the displacement line 204. The open lower end 104 is open to the surface 51 of the piston 49 and the open end 106 is open to the lower displacement line port 212 and, thus, to the return tank 16 and its return component contents via the displacement line 204 fluidly coupled between the upper displacement line port 210 to the return tank 16 and its return component contents and the lower displacement line port 212 to the working component in the bellows 102. This fluidly couples the return tank 16 and its return component to the bellows 102, the working component in the bellows 102, and the piston's 49 surface 51. The working component in the bellows 102 and the piston's 49 surface 51 are under pressure p₂from the return component that communicates fluidly with the bellow's 102 working component extending therethrough from the open upper end 106 at the lower displacement line port 212 to the open end 104 and the piston's 49 surface 51.

The previously described boot 110, which bears its corresponding reference characters in FIGS. 15-20, is over the bellows 102 and coupled between the piston 49 and the displacement tank 202. The boot 110 surrounds the bellows 102 between the open end 104 and the open end 106. The boot 100 extends laterally through the displacement component between the piston's 49 surface 51 and the displacement tank 202. The boot 110 defines the chamber 111, the boot's 110 fluid chamber, charged with the transition component of the displacement tank's 202 displacement component, the transition component around the bellows 102 between the piston's 49 surface 51 and the displacement tank 202. As before, the boot 110, a constant volume boot, is configured to maintain a constant volume of chamber 111 and its transition component contents.

According to the invention, the collar 112 affixed to piston's 49 upper surface 51 surrounds the open end 104 of the bellows 102. The collar 114 affixed to an inner side of the side 202B of the displacement tank 202 surrounds the open end 106 of the bellows 102. The body 116 surrounds the bellows 102 between the collars 112 and 114 and extends laterally through the displacement component from collar 112 to collar 114. Based on the orientation of the boot 110, the collar 112 is the outer collar and the collar 114 is the inner collar. The conical section 120, the outer conical section of the boot 110, extends laterally from the hinge 126, connecting the conical section 120 to the collar 112, to the hinge 130, connecting the conical section 120 to the intermediate ring section 124. The conical section 122, the inner collar of the boot 110, extends laterally from the hinge 132, connecting the conical section 122 to the intermediate ring section 124, to the hinge 128, connecting the conical section 122 to the collar 114. The body 116 forms the chamber 111 about the bellows 102 extending laterally through the chamber 111 from the collar 112 at bellow's 102 open end 104 to the collar 114 at the bellow's 102 open end 106.

According to the invention, the boot 110 has valves 140 and 142 configured to open and close independently. When the valve 140 is open, it opens the chamber 111 to the displacement tank 202, opening the transition component in chamber 111 to the displacement component in the displacement tank 202. When the valve 140 is closed, it isolates the chamber 111 from the displacement tank 202, isolating the transition component in the chamber 111 from the displacement component in displacement tank 202. When the valve 142 is open, it opens the chamber 111 to the displacement tank 202, opening the transition component in the chamber 111 to the displacement component in the displacement tank 202. When the valve 142 is closed, it isolates the chamber 111 from the displacement tank 202, isolating the transition component in the chamber 111 from the displacement component in the displacement tank 202. In this embodiment, the valves 140 and 142 are on opposite sides of the conical section 122. In alternate embodiments, the valves 140 and 142 can be formed on opposite sides of the conical section 120, on opposite sides of the respective sections 120 and 122, or elsewhere. The valves 140 and 142, the valve mechanism of the boot 110, are any of the valve types discussed above with valves mechanism 36/40.

In FIG. 15, the extensible and retractable bellows 150 is coupled between the piston 49 and the pressure tank 52, the preferred source of the pressurized fluid that pressure tank 52 sources to the piston's 49 surface 51 via the bellows 150. The bellows 150, the inner bellows of the displacement device 100, is coupled between the piston 49 and the side 202A of the displacement tank 202. The bellows 150 extends laterally through the displacement component from its open end 152 centered on and affixed to the surface 51 of the piston 49 to its open end 154 affixed to an inner side of the side 202A of the displacement tank 202, the open end 154 of the bellows 150 open to the pressure tank 52 via conduit 160, coupling the piston's 49 surface 50 to the pressure tank 52 fluidly. The bellows 150 surrounds the part of the cylinder 244 extending into the displacement tank 202 from the external actuator 240 and the operating rod 246 connected between the cylinder 244 and the surface 50 of the piston 49. The bellows 150 couples the piston's 49 surface 50 to the pressure tank 52 fluidly. The pressure tank 52 sources the pressurized fluid to the bellows 150 and holds it against piston's 49 surface 50 under constant pressure p₁from pressure tank's 52 pressurized fluid. The surface 50 of the piston 49 has the surface area A in fluid communication with the pressure tank 52 that holds the pressurized fluid, preferably compressed air, at pressure p₁against the surface 50. The conduit 160 fluidly coupled between the pressure tank 52 and bellow's 150 lower end 154 couples the pressure tank 52 to the bellows 150 fluidly. Thus, the piston's 49 surface 50 is constantly under pressure p₁that exerts the force equal to p₁A on the surface 50. The surface 51 of the piston 49 in fluid communication with the return tank 16 is constantly under pressure p2 from the return tank's 16 return component fluidly coupled to the surface 51 via the displacement line 204 and the working component of the bellows 102, which the bellows 102 isolates from the transition component and the rest of the displacement component on the displacement tank 202.

In the return configuration of the tank structure 200 in FIG. 16, the valve 142 is closed, isolating the transition component in the chamber 111 from the displacement component in displacement tank 202. The valve 140 is open, opening the transition component in the chamber 111 to the displacement component in displacement tank 202. The access port 34 is closed. The transfer port 38 is open, opening the return component in return tank 16 to the transfer component in transfer tank 14.

In the reset configuration of the tank structure 200 in FIG. 19, the valve 140 is closed, isolating the transition component in the chamber 111 from the displacement component in displacement tank 202. The valve 142 is open, opening the transition component in the chamber 111 to the displacement component in the displacement tank 202. The access port 34 is open. The transfer port 38 is closed, isolating the return component in return tank 16 from the transfer component in transfer tank 14.

In a closed configuration of the tank structure 200 in FIG. 18, the valves 140 and 142 are closed, each of the closed valves 140 and 142 isolating the transition component in the chamber 111 from the displacement component in displacement tank 202.

When the displacement device 100 is deactivated in FIGS. 15, 16, 19, and 20 to its deactivated or un-displaced configuration, the piston 49 is in its first or outer position away from the lower displacement line port 212 and the side 202B of the displacement tank 202. The hydraulic drive mechanism 242 is retracted with the operating rod 246 retracted in the cylinder 244. The bellows 150 is retracted between its end 154 and the piston's 49 surface 50. The bellows 102 is extended between the piston's 49 surface 51 and the side 202B of the displacement tank 202. The boot 110 is extended between the piston's 49 surface 51 and the side 202B of the displacement tank 202. When the piston 49 is in its first or outer position, the piston's 49 surface 51 is in its first or outer position away from the lower displacement line port 212 and the side 202B of the displacement tank 202.

When the displacement device 100 is activated in FIGS. 17 and 18 to its activated or displaced configuration, the piston 49 is in its second or inner position toward the lower displacement line port 212 and the side 202B of the displacement tank 202. The hydraulic drive mechanism 242 is extended with the operating rod 246 extended from the cylinder 244. The bellows 150 is extended between its end 154 and the piston's 49 surface 50. The bellows 102 is retracted between piston's 49 surface 51 and the side 202B of the displacement tank 202. The boot 110 is retracted between the piston's 49 surface 51 and the side 202B of the displacement tank 202. When the piston 49 is in its second or inner position, the piston's 49 surface 51 is in its second or inner position toward the lower displacement line port 212 and the side 202B of the displacement tank 202.

When the tank structure 200 is in its return configuration, the displacement device 100 is configured to activate to its activated or displaced configuration in FIGS. 17 and 18 from its deactivated or un-displaced configuration in FIG. 16 in response to activating the force-applying mechanism 55. When the force-applying mechanism 55 activates, the hydraulic drive mechanism 242 activates, extending the operating rod 246 from its retracted position in FIG. 16 to its extended position in FIGS. 17 and 18, applying a force on the piston 49 sufficient to defeat the pressure differential Δp on the piston 49 produced by the surface 51 and the surface 50 under the concurrent pressures from the return component and the pressurized fluid, respectively. When the force applied to the piston 49 by the activated force-applying mechanism 55 defeats the pressure differential Δp, the piston 49 automatically displaces laterally out of its first or outer position in FIG. 16 to its inner position in FIGS. 17 and 18 with the extending operating rod 246, moving the piston's 49 surface 51 laterally from its first or outer position to its second or inner position, reducing the volume of the bellows 102 between the piston's 49 surface and the side 202B of the displacement tank 202. At the same time, the bellows 150 extends between the side 202A of the displacement tank 202 and the surface 50 of the piston 49, the bellows 102 retracts between the surface 51 of the piston 49 and the lower displacement line port 212 and the side 202B of the displacement tank 202, and the boot 110 retracts between the surface 51 of the piston 49 and the side 202B of the return tank 202 while maintaining the constant volume of the chamber 111. This displacement of the displacement device 100 exchanges volume V_dof the displacement component's working component in the bellows 102 with a corresponding volume of the fluid (i.e., the pressurized fluid) from pressure tank 52, lifting volume V_dof the working component in the bellows 102 into the return component in return tank 16 through the lower displacement line 204 from the lower displacement line port 212 to the bellows 102 to the upper displacement line port 210 to the return tank 16 and sources the corresponding volume of the fluid from pressure tank 52 to the bellows 150.

When the tank structure 200 is in its closed configuration, the displacement device 100 is configured to deactivate to its deactivated configuration in FIG. 19 from its activated configuration in FIG. 18 in response to deactivating the force-applying mechanism 55. When the displacement device 100 reaches its deactivated configuration in FIG. 19 from its activated configuration in FIG. 18, the tank structure 200 adjusts to its rest configuration. When the force-applying mechanism deactivates, the hydraulic drive mechanism 242 deactivates, withdrawing its force from the piston 49, automatically reestablishing the pressure differential Δp on the piston 49 produced by the surface 51 and the surface 50 under concurrent pressures from the return component and the pressure tank′ 52 fluid, respectively, automatically retracting the operating rod 246 from its extended position in FIGS. 17 and 18 to its retracted position in FIGS. 19 and 20, in which the piston 49 automatically displaces laterally from its second or inner position in FIGS. 17 and 18 to its first or outer position in FIGS. 19 and 20 with the retracting operating rod 246, moving the piston's 49 surface 51 laterally from its second or inner position in FIGS. 17 and 18 to its first or outer position in FIGS. 19 and 20, resetting the volume of the bellows 102 between the piston's 49 surface and the side 202B of the displacement tank 202 to its original size. At the same time, the bellows 150 retracts between its end 154 and the surface 50 of the piston 49, the bellows 102 extends between the surface 51 of the piston 49 and the lower displacement line port 212 and the side 202B of the displacement tank 202, and the boot 110 extends between the surface 51 of the piston 49 and the side 202B of the displacement tank 202 while maintaining the constant volume of the chamber 111. This displacement of the displacement device 100 exchanges volume V_dof the return component in return tank 16 with the corresponding volume of the fluid in the bellows 150, lowering volume V_dof the return component in return tank 16 to the working component in the bellows 102 through displacement line 204 from the upper displacement line port 210 to the return tank 16 to the lower displacement line port 212 to the bellows 102 and returning the corresponding volume of the fluid from bellows 150 to the pressure tank 52.

In FIG. 15, the displacement device 100 is deactivated to its un-displaced configuration. The access port 34 is open, enabling the power module 18 to enter the transfer component in transfer tank 14 through the open access port 34 as shown in FIG. 16 and translate along pathway 20, the power module 18 entering the transfer component through the upper water surface 42 that is below the transfer port 38 and above the displacement tank 202 and its contents. The transfer port 38 is closed, isolating the return component in return tank 16 from the transfer component in transfer tank 14. The boot's 110 valves 140 and 142 are closed, isolating the transition component in the chamber 111 from the displacement component in the displacement tank 202. The surface 50 of the piston 49 is constantly under pressure p₁that exerts a force equal to p₁A on the surface 50. The surface 51 of piston 49 is under constant pressure p₂from the return component in return tank 16. The balance conduit 206 below the displacement line 204 and the lower water surface 42 enables fluid transfer between the transfer and displacement tanks 14 and 202, equalizing the pressure between the transfer component in the transfer tank 14 and the displacement component in the displacement tank 202.

Upon the power module 18 entering the transfer component through the open access port 34 in FIG. 16, the access port 34 closes, the valve 140 opens, and the transfer port 38 opens. This sets the tank structure 200 to its return configuration, which opens transfer tank 14 and its transfer component contents to return tank 16 and its return component contents. The return configuration of bi-level tank 12 establishes the unobstructed underwater pathway 20 from transfer tank 14 through the return tank 16 and up to the atmospherically exposed upper water surface (See FIG. 2A) of the return tank 16 extending upright from transfer tank 14. At this stage, the transfer component in the transfer tank 14 and the surface 51 of the piston 49 are under pressure p₂produced by the increased head height h₂(See FIG. 2B). The balance line 206 equalizes the pressure between the transfer component in the transfer tank 14, the displacement component in the displacement tank 202, and the transition component in the chamber 111 open by the open valve 140 to the displacement tank's 202 displacement component.

The displacement device 100 activates while the power module 18 is in the transfer tank's 14 transfer component, displacing from its deactivated configuration in FIG. 16 to its activated configuration in FIG. 17. This displaces volume V_dfrom working component in the bellows 102 to the return component in the return tank 16, and power module 18 progresses along pathway 20 from transfer tank 14 to return tank 16 through the open transfer port 38. When the displacement device 100 activates, the surface 51 of the piston 49 acts against the water pressure p₂caused by the head height h₂in the bi-level tank 12 to displace the volume V_dof water from the working component in the bellows 102 to the return component in the return tank 16 through the displacement line 204 from the lower displacement line port 212 open to the working component in the bellows 102 to the upper displacement line port 210 open to the return component in the return tank 16. The work required to displace V_dwill be equal to the product of the projected displacement area for the surface 51 of the piston 49, the pressure p₂in the return tank 16, and the displacement distance d required for a movement of the displacement device 100 to displace volume V_d.

The pressure tank 52, the preferred source of the pressurized fluid, sources the pressure p₁of its pressurized fluid to the surface 50 of piston 49. This pressure p₁constantly held against the surface 50 acts directly against surface's 50 area A to create the constant biasing force Δp₁. This biasing force Δp₁directly opposes the force of pressure p₂that acts against piston's 49 surface 51. Thus, a structure is created where the pressure forces acting across the piston 49 are p₁and p₂. The pressure p₂from the head height h₂in the return tank 16 and the pressure p₁from the pressurized fluid from the pressure tank 52 create the pressure differential Δp=p₂−p₁across the piston 49, wherein p₂>p₁. Thus, a force proportional to Δp will constantly act against the piston 49 to urge it into its deactivated configuration in FIG. 16. The boot's 110 now open valve 140 equalizes the pressure p₂between displacement tank's 202 displacement component and the transition component in the chamber 111, the volume of chamber 111 maintained constant by the boot 110. As described previously, the bias force creates Δp that is relatively small, e.g., in a range between 1.5 and 2 psi. Accordingly, the activating force on the piston 49 from the force-applying mechanism 55 sufficient to overcome the pressure differential Δp to laterally displace piston 49 distance d from its first or outer position in FIG. 16 to its second or inner position in FIG. 17 need only be greater than pressure p₂.

And so while the power module 18 is in the transfer tank's 14 transfer component, the displacement device 100 displaces from its deactivated configuration in FIG. 16 to its activated configuration in FIG. 17 when the displacement device 100 activates. This concurrently displaces the volume V_dof water from the working component in the bellows 102 in the displacement tank 202 to the return tank's 16 return component and the same volume of fluid from the pressure tank 52 to the bellows 150 by the inwardly-displacing piston 49. The displacement device 100 activates in response to activating the force-applying mechanism 55, applying its force on the piston 49 sufficient to defeat the pressure differential Δp across the piston 49, enabling the piston 49 to displace laterally from its first or outer position to its second or inner position automatically by the operating rod 246 extending from the cylinder 244, displacing the piston's 49 surface 51 from its first or outer position to its second or inner position. At the same time, the power module 18 progresses along pathway 20 through the open transfer port 38 from the transfer tank 14 and into the return tank 16 in FIG. 18. When the displacement device 100 activates in FIG. 16, it cycles from its deactivated configuration to its activated configuration in response to activating the force-applying mechanism 55, applying its force on the piston 49 sufficient to defeat the pressure differential Δp on the piston 49. This exchanges the volume V_dof the working component in the bellows 102 with the corresponding volume of the pressurized fluid from the pressure tank 52, lifting the volume V_dof the displacement component's working component in the bellows 102 into the return component in return tank 16 through displacement line 204 by the surface 51 of the inwardly-displacing piston 49 pushing volume V_dof the displacement component's working component upwardly into the return tank's 16 return component through the displacement line 204 from the lower displacement line port 212 open to the working component in the bellows 102 to the upper displacement line port 210 open to the return tank's 16 return component.

The open valve 140 opening the transition component in the chamber 111 to the displacement tank's 202 displacement component while the displacement device 100 displaces from its deactivated configuration to its activated configuration equalizes the pressure between the displacement component in the displacement tank 202 and the transition component in the boot's 110 chamber 111 while the balance line 206 allows fluid transfer between the transfer component in the transfer tank 14 and the displacement component in the displacement tank 202 to equalize the pressure between the transfer component in the transfer tank 14 and the displacement component in the displacement tank 202. This pressure equalization between the transition and displacement components and the displacement and transfer components and the inherent ability of the boot 110 to maintain chamber's 111 volume constant causes the chamber's 111 volume to remain fixed or otherwise unchanged while boot 110 retracts between the surface 51 of the piston 40 and the side 202B of the displacement tank 202 in response to movement of the piston 49 from its first or outer position in FIG. 16 to its second or inner position in FIG. 17. This disables volume loss in the displacement 202 enabling the described exchange of the volumes.

After the power module 18 transitions through the transfer port 38 from the transfer component in the transfer tank 14 to the return component in the return tank 16 in FIG. 18, the transfer port 38 closes, the valves 140 and 142 close to set the tank structure 200 to its closed configuration, the access port 34 opens, and the displacement device 100 deactivates from its activated configuration to its deactivated configuration in FIG. 19. This concurrently displaces volume V_dfrom the return component in the return tank 16 to the working component in the bellows 102 and returns the same volume of fluid from the bellows 150 to the pressure tank 52 by the outwardly-displacing piston 49. Closing the valve 38 isolates the transfer tank 14 from the return tank 16, isolating the transfer component in the transfer tank 14 from the return component in the return tank 16, and severs pathway 20 from the transfer tank 14 to the return tank 16. It also withdraws the pressure p₂to the transfer component in the transfer tank 14, to the transition component in the boot's 110 chamber 111 and the displacement component in the displacement tank 202. The working component in the bellows 102 and the surface 51 of the piston 49 remain under pressure p₂via the displacement line 204 fluidly coupling the return tank's 16 return component to the working component of the displacement tank's 202 displacement component, the displacement line 204 coupling the bellows 102 and its contents to the return tank 16 and its contents. All the while, the balance line 206 below the displacement line 204 and the lower water surface 42 enables fluid transfer between the transfer and displacement tanks 14 and 202, equalizing the fluid pressure between the transfer component in the transfer tank 14 and the displacement component in the displacement tank 202 now isolated from the transition component in the chamber 111 by the closed valves 140 and 142.

And so while the power module 18 is in return tank's 16 return component, the displacement device 100 displaces from its activated configuration in FIG. 18 to its deactivated configuration in FIG. 19 in response to deactivation of the displacement device 100. The displacement device 100 deactivates and cycles from its activated configuration in FIG. 18 to its deactivated configuration in FIG. 19 in response to deactivation of the force-applying mechanism 55, removing its force on the piston 49. This reestablishes the pressure differential Δp across the piston 49, causing the piston 49 to displace laterally from its second or inner position in FIG. 18 to its first or outer position in FIG. 19 automatically under the influence of pressure p₂, the operating rod