EP2558689B1 - Generator - Google Patents

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Publication number
EP2558689B1
EP2558689B1 EP11718789.8A EP11718789A EP2558689B1 EP 2558689 B1 EP2558689 B1 EP 2558689B1 EP 11718789 A EP11718789 A EP 11718789A EP 2558689 B1 EP2558689 B1 EP 2558689B1
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EP
European Patent Office
Prior art keywords
temperature
pressure
medium
heat
work medium
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Application number
EP11718789.8A
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German (de)
English (en)
French (fr)
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EP2558689A2 (en
Inventor
Gershon Harif
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GERSHON MACHINE Ltd
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GERSHON MACHINE Ltd
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Publication of EP2558689A2 publication Critical patent/EP2558689A2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/02—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the fluid remaining in the liquid phase
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • F01K27/005—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for by means of hydraulic motors

Definitions

  • This subject matter of the present application relates to energy generating systems, more particularly, systems adapted for the generation of electrical energy utilizing heating/cooling and corresponding expansion/compression of a material.
  • Generation of electrical power is a process in which one form of energy is converted into electricity, and a great plurality of processes is known and used today for performing the same. Some of these processes involve turning one form of energy into mechanical energy allowing the movement/rotation of a mechanical element within a magnetic field for the generation of electricity.
  • Such systems are disclosed, for example, in WO 2009/064378 , US 2008/0236166 ,etc.
  • the documents listed below disclose similar systems comprising heat differential modules with high-temperature reservoirs and low temperature reservoirs, a heat mechanism to maintain a temperature difference between the reservoirs, a pressure module with a pressure medium in selective fluid communication with the reservoirs for performing heat exchanges with fluid therein, a conversion module for utilizing temperature changes of the pressure medium to produce energy, and a heat recovery arrangement to absorb heat from the pressure medium and providing heat to the heat differential or pressure module.
  • GB 1 536 437 discloses is a method and an apparatus for the conversion of thermal energy into mechanical or electrical energy by means of an exchange of temperature between two water sources having a temperature differential, and utilizing a compressible fluid to be alternately compressed and expanded by the use of the thermal differential, with the flow imparted to the compressible fluid utilized through an improved positive displacement rotary valve and a motor wherein the motor is operated by hydraulic cylinders alternately pressurized and depressurized and connected between a pair of canted discs.
  • US 2005/0198960 discloses an apparatus and method for converting a differential in thermal energy between a first thermal source having a thermal conducting fluid and a second thermal source having a thermal conducting fluid.
  • the apparatus employs a first vessel and a second vessel. Each of the vessels contain a gas under pressure.
  • the vessels contain heat exchanging coils that are connected to the thermal sources by fluid lines.
  • a plurality of cooperating valves regulate the flow of the thermal conducting fluid from the first and second thermal sources to the first and second vessels. The valves alternate between first and second operating positions.
  • the valves In the first position, the valves permit a flow of thermal conducting fluid from the first thermal source to the first vessel and from the second thermal source to the second vessel and prevent a flow of thermal conducting fluid from the first thermal source to the second vessel and from the second thermal source to the first vessel. In the second position, the valves permit a flow of thermal conducting fluid from the first thermal source to the second vessel and from the second thermal source to the first vessel and prevent a flow of thermal energy from the first thermal source to the first vessel and from the second thermal source to the second vessel.
  • a pressure driven actuator in fluid communication with the first and second vessels is driven into reciprocating motion between a first position and a second position by alternating positive pressure and negative pressure from the first and second vessels.
  • US 2006/0059912 discloses a power plant with at least two pressure vessels containing a hydraulic fluid.
  • a heat exchanging assembly is in heat transferring association with the pressure vessels.
  • the hydraulic conduit is hydraulically connected with the pressure vessels.
  • a power outlet device is in hydraulic association with the conduit between the vessels and is configured for outputting power from the flow of the hydraulic fluid.
  • a controlling mechanism is operably associated with the heat exchanging assembly to cause the heat exchanging assembly to alternately increase the pressure in one of the pressure vessels compared to the other.
  • hydraulic fluid is caused to flow through the power outlet device alternately between the pressure vessels to produce power from the power output device.
  • a generator configured for extracting heat from and medium, and utilizing said heat in a process for the generation electrical energy.
  • said heat can be utilized for reciprocating/rotating a mechanical element for the generation of said electricity.
  • the invention is defined by the generator of claim 1 and the method of claim 22.
  • a generator comprising a heat differential module configured for providing a first reservoir and a second reservoir having a temperature difference therebetween, a pressure module containing a pressure medium configured for performing an alternate heat exchange process with the reservoirs of the heat differential module so as to fluctuate its temperature, and a conversion module configured to utilize the fluctuation of the pressure module for the generation of energy.
  • said generator can comprise:
  • the term ' medium ' is used herein to describe any of the following: solids, fluids - liquids and gasses.
  • the pressure medium can even be a solid, or, for example, even a substance which solidifies under pressure.
  • T H and T C can vary as follows:
  • the term ' ambient ' is used herein to define the average temperature of the external environment in which at least the heat differential module of the generator is located.
  • this environment is simply ambient air
  • the generator can also be configured to be immersed in any desired medium, whereby the term ' ambient ' will refer to the average temperature of that medium.
  • the heat differential module can be constituted by a work medium sub-system comprising the high temperature reservoir and the low temperature reservoir.
  • each of the high/low temperature reservoirs can be provided with an inlet line configured for providing selective fluid communication between the reservoirs and an inlet access end of the pressure module, and an outlet line configured for providing selective fluid communication between an outlet access end of the pressure module and the reservoirs.
  • the respective inlet/outlet lines of the heat differential module are configured for alternately providing high/low temperature work medium to the pressure module so as to perform a heat exchange process with the pressure medium.
  • the work medium sub-system can comprise a heat pump having an evaporator end and a condenser end, the heat pump being configured for withdrawing an amount of heat Q from the evaporator end towards the condenser end under the provision thereto of input power W.
  • the condenser end is constantly provided with heat, so that the temperature of the condenser end exceeds that of the evaporator end.
  • the arrangement is such that at least one of the high temperature reservoir and the low temperature reservoir is thermally associated with one of said evaporator end and condenser end of the heat pump.
  • the high temperature reservoir can be thermally associated with the condenser end of the heat pump and/or the low temperature reservoir can be associated with the evaporator end of the heat pump.
  • the heat pump can operate as a cooling unit to maintain the low temperature reservoir at a desired 'low' temperature, while heat expelled from the air heat pump during cooling is used to maintain the high temperature reservoir at a desired 'high' temperature.
  • Thermal association between the evaporator/condenser end of the heat pump and the high/low temperature reservoir can be achieved via direct/indirect contact between the evaporator/condenser end of the heat pump and the work medium contained within the high/low temperature reservoir, allowing for a heat exchange process between the former and the latter. According to a specific example, such contact is achieved via emersion of the evaporator/condenser end of the heat pump within the high/low work medium.
  • the high temperature reservoir is in direct thermal communication with the condenser side of the heat pump while the low temperature reservoir is associated with the outside environment (i.e. exposed to ambient temperature).
  • the low temperature reservoir though exposed to the outside environment can also be fitted with an element providing thermal association of the low temperature reservoir with the evaporator end of the heat pump.
  • the high temperature reservoir is in direct thermal communication with the condenser side of the heat pump while the low temperature reservoir is in direct thermal communication with the evaporator side of the heat pump.
  • the pressure module can comprise a vessel containing the pressure medium and at least one conduit (referred herein as ' conduit ' or ' core ') having an inlet end and an outlet end, constituting the respective inlet and outlet access ends of the pressure module.
  • said conduit can be configured for being in selective fluid communication with said high/low temperature reservoirs, to allow passage of high/low temperature work medium therethrough.
  • the generator is configured such that high/low temperature work medium can be alternatively passed through the conduit of the vessel (using selective fluid communication with the reservoirs) so as to perform a heat-exchange process with the pressure medium.
  • the high temperature work medium is used to bring the pressure medium to said maximal operative temperature and said low temperature work medium is used to bring said pressure medium to said minimal operative temperature.
  • the pressure medium is configured to fluctuate between a maximal operative temperature and a minimum operative temperature thereof, said fluctuation causing a respective increase/decrease of the volume of said pressure medium, which can be utilized by the conversion module for the production of energy.
  • At least one or more of the components of the generator through which a heat transfer process takes place can be formed with a heat transferring surface which has an increased surface area.
  • said surface can be formed with a plurality of elements increasing its surface area, e.g. bulges, protrusions etc.
  • the elements can be micro-structures having geometric shapes such as cubes, pyramids, cones etc.
  • the elements can be ridges (either parallel or spiraling).
  • such ridge elements yield that in cross-section of the pipes taken along a central axis thereof, the surface appears undulating (between peaks and troughs).
  • the arrangement can be such that a peak on the inner surface faces a trough on the outer surface and vice versa , thereby maintaining a generally constant material thickness in each cross-section perpendicular to the central axis.
  • the conversion module of the generator can comprise a dynamic arrangement being in mechanical communication with the pressure medium so as to be driven thereby.
  • the dynamic arrangement can comprise a movable member configured to reciprocate in correspondence with the fluctuation of the pressure medium from said maximal operative temperature and said minimal operative temperature.
  • the dynamic arrangement can be constituted by a piston assembly, comprising a housing with a piston located therein, the piston sealingly dividing the housing into a first, input chamber being in mechanical communication with the pressure medium and the second, output chamber being in mechanical communication with a motor assembly configured for generating output energy.
  • the piston of the conversion module can be configured for reciprocating within the housing respective to volumetric fluctuations of the pressure medium. Specifically, as the temperature of the pressure medium increases, its volume increases correspondingly, thereby displacing the piston so that the volume of the input chamber increases and the volume of the output chamber decreases. Respectively, as the temperature of the pressure medium decreases, its volume decreases correspondingly, thereby displacing the piston so that the volume of the input chamber decreases and the volume of the output chamber increases.
  • This reciprocation can be used by the motor assembly for the production of output energy.
  • the motor assembly comprises a crank shaft arrangement so that reciprocation of the piston is configured for generating revolution of the crank shaft about is axis. This revolution can be converted, by known means, for the production of output energy.
  • the piston can be associated with a linear shaft which is configured to be meshed with a gear assembly, which in turn is configured for converting the linear reciprocation of the shaft into rotational movement.
  • This rotational movement can be converted, by known means, for the production of output energy.
  • an intermediary device between the piston and the motor for example, the piston can be adapted to drive a utility piston via pressure on an intermediary substance such as oil.
  • the generator of the present invention can further comprise at least one auxiliary heat exchanger which is in thermal communication at least with one of the outlet lines of the high temperature reservoir and the low temperature reservoir.
  • the heat exchanger can be configured for performing a heat exchange process between the work medium within said outlet lines and the outside environment and/or a medium in which the heat exchanger is immersed.
  • the heat exchanger can be configured to respectively cool down / heat up the work medium heated up / cooled down during the heat exchange process with the pressure medium of the pressure module, upon its exit from the pressure vessel.
  • the heat differential module comprises a high temperature reservoir which is in thermal communication with a condenser end of a heat pump, and a low temperature reservoir which is in thermal communication with the outside environment.
  • the evaporator end of the heat pump is also exposed to the outside environment, so that, in operation, the evaporator end constantly withdrawn heat from the environment, and the heat pump constantly withdrawn heat from the evaporator end to the condenser end.
  • the pressure module comprises a single pressure vessel containing therein a pressure medium which is pre-loaded to high pressure (approx. 6000 atm. (600 MPa)), and having at least one conduit passing therethrough.
  • the pressure vessel is further provided with an inlet valve associated with an inlet end of the conduit and an outlet valve associated with an outlet end of the conduit.
  • the pressure vessel can also be provided with an output line which is in fluid communication with a dynamic arrangement of the conversion module.
  • Each of the high/low temperature reservoirs comprises an inlet line providing selective fluid communication between the reservoir and the inlet valve and an outlet line providing selective fluid communication between the reservoir and the outlet valve.
  • the piston has a predetermined resistance which requires a predetermined threshold pressure of the high-pressure medium to overcome this resistance and displace the piston. In the event a low-pressure medium is used, heating thereof will first result in a pressure increase of the low-pressure medium to the threshold pressure and only then displacement of the piston.
  • pre-loading the medium within the pressure vessel to a high pressure ensures that upon heating of the pressure medium will directly entail displacement of the piston and will not go to waste for pressuring the medium to the threshold pressure.
  • the above method can further include an additional step (c) in which the heated up low temperature work medium is passed through the auxiliary heat exchanger in order to allow more efficient emission of heat from the work medium to the outside environment.
  • the outlet line of the low temperature reservoir is not returned directly back into the low temperature reservoir upon exiting the pressure vessel, but rather is first passed through the evaporator end of the heat pump. In this manner, instead of its heat being emitted to the environment and re-absorbed by the heat pump at the evaporator end, it is directly returned to the evaporator end of the heat pump, thereby increasing the efficiency of the operation of the generator.
  • the generator is shown demonstrating a cooled reservoir arrangement in which the first, high temperature reservoir is in thermal communication with the condenser end of the heat pump (as in previous examples), while the low temperature reservoir is in thermal communication with the evaporator end of the heat pump.
  • the low temperature work medium recovers a partial amount of heat from the pressure medium upon a heat exchange process therewith, and a remaining amount of heat from the environment to provide an overall amount of heat from the evaporator end to the condenser end of the heat pump HP.
  • the generator can comprise two pressure vessels, each of which is connected to the high and the low temperature reservoir via corresponding inlet/outlet valves.
  • the pressure medium of each of the pressure vessels is in fluid mechanical communication with a respective piston.
  • the generator can comprise three reservoirs: a high temperature reservoir, a low temperature reservoir and an intermediate temperature reservoir.
  • This arrangement is based on the cooled reservoir configuration, wherein an additional intermediate reservoir is added containing intermediate temperature work medium.
  • the intermediate temperature reservoir is configured to contain an intermediate temperature work medium, the term ' intermediate ' referring to a temperature between said high temperature and said low temperature.
  • Each of the high/intermediate/low temperature reservoirs is in selective fluid communication with the pressure vessel.
  • each cooling/heating step is divided into two stages, the first being performed by intermediate work medium and the second being performed by high/low work medium.
  • the high/low temperature work medium is practically used to provide heating/cooling within a reduced temperature range (i.e. between intermediate and high and/or between intermediate and low), thereby making the operation of the generator more effective.
  • the intermediate temperature reservoir can be in thermal communication with the outside environment, while the high/low temperature reservoirs are in thermal communication with the condenser/evaporator ends of the heat pump respectively.
  • any one of the outlet lines of the high/intermediate/low temperature reservoirs can be passed through the auxiliary heat exchanger upon exiting the pressure vessel.
  • the intermediate outlet line can pass through the auxiliary heat exchanger so as to respectively convey to/absorb from the atmosphere the required amount of heat gained/lost during the heat exchange process with the pressure medium before returning to its reservoir.
  • the outlet lines of the high/low temperature reservoirs can return the work medium directly to its respective reservoir without necessarily passing through the heat exchanger.
  • the generator comprises two pressure vessels (similar to the dual operation arrangement), and each of the outlet valve is also in selective fluid communication with the inlet valves.
  • each outlet valve O is also provided with a cross-over line COL which provides fluid communication between the outlet valve of one pressure vessel and the inlet valve of the other pressure vessel.
  • the above arrangement provides for a more significant heat recovery from the pressure medium. More specifically, instead of emitting/withdrawing a certain amount of heat to/from the environment during its return to the intermediate temperature reservoir, the intermediate temperature work medium now emits/withdraws a portion of that amount of heat in a heat exchange with the pressure medium, thereby increasing the efficiency of the generator.
  • the generator also comprises one pressure vessel (similar to the basic arrangement), and at least one gradient tank associated with the outlet valve.
  • the gradient tank can comprise an arrangement configured for preventing mixing of portions of work medium contained therein, thereby considerably reducing heat transfer between the portions and the speed with which these portions reach a thermal equilibrium.
  • the gradient tank when used in the present generator, can contain a first portion of work medium at a temperature T1, a second portion of work medium at temperature T2 and so forth so that T1 ⁇ T2 ⁇ and so forth.
  • the gradient tank allows for maintaining the work medium contained therein at a temperature gradient so that T1 > T2 > .... > Tn, or alternatively, T1 ⁇ T2 ⁇ .... ⁇ Tn.
  • the portions of the heated/cooled intermediate temperature work medium entering the gradient tank have different temperatures, and, as will be explained in detail later, it can be beneficial to maintain a temperature gradient between these portions within the gradient tanks.
  • the gradient tank can further comprise a non-mix mechanism, configured for maintaining a temperature gradient within the reservoir by preventing different portions of the work medium from mixing with one another.
  • the non-mix mechanism is configured for slowing down the work medium received within the gradient tank from reaching a uniform temperature.
  • the non-mix mechanism can be any mechanism formed with a flow path such that the cross-sectional area for heat transfer between consecutive portions of the work medium entering the gradient tank is small enough to considerably slow down the heat transfer.
  • the term 'small enough' refers to a cross-sectional area defined by a nominal cross-sectional dimension D which is considerably smaller than the length L of the path.
  • Examples of such a non-mix mechanism can be:
  • the flow path can be made out of a material having isolating properties, i.e. having poor heat conduction.
  • a material having isolating properties i.e. having poor heat conduction.
  • One example for such a material can be plastic.
  • each portion of the intermediate temperature work medium passing through the heated/cooled pressure vessel is emitted therefrom having a different temperature.
  • T INTERMEDIATE when the intermediate temperature work medium of temperature T INTERMEDIATE begins circulating through the heated pressure vessel containing the pressure medium at the high temperature T HOT > T INTERMEDIATE , the first portion of the intermediate temperature work medium will be emitted from the pressure vessel at a temperature T HOT ' such that T INTERMEDIATE ⁇ T HOT ' ⁇ T HOT , the second portion of the work medium will be emitted from the pressure vessel at a temperature T HOT ", such that T INTERMEDIATE ⁇ T HOT " ⁇ T HOT ' ⁇ T HOT etc.
  • the temperatures T HOT , T INTERMEDIATE and T COLD correspond to the high/intermediate/low temperature of the work medium in the respective high/intermediate/low temperature reservoirs.
  • the above arrangement provide for another way of performing heat recovery in the generator, thereby further increasing its efficiency. It is also appreciated that the use of the LIFO configuration allows the pressure medium to be gradually heated (starting from the lowest temperature portion first), making better use of the amount of heat of each portion of the work medium.
  • the gradient tank can be used both for the heated low temperature work medium and the cooled high temperature work medium.
  • the generator can comprise more than one gradient tank.
  • each pressure vessel can be provided with its own gradient tank and/or gradient tanks are provided for high/low temperature work medium.
  • the heat gradient recovery configuration can be combined with the dual operation configuration, wherein the operation of the generator can be described as follows: At a first stage, similar to the previously described example (without gradient tanks), high temperature work medium at temperature T HOT is passed through one pressure vessel to heat up the pressure medium contained therein, while, simultaneously, low temperature work medium at temperature T COLD is passed through the other pressure vessel to cool down the pressure medium contained therein. After this stage, the pressure medium in one pressure vessel is heated up to a temperature T HOT ' ⁇ T HOT and the pressure medium in the other pressure vessel is cooled down to a temperature T COLD ' > T COLD .
  • a return step is performed, during which intermediate temperature work medium at temperature T INTERMEDIATE is passed through both pressure vessels in order to cool down / heat up the pressure medium therein.
  • the intermediate temperature work medium passing through the heated pressure vessel performs a heat transfer process with the latter and cools it down to a temperature closer to T INTERMEDIATE
  • the intermediate temperature work medium passing through the cooled pressure vessel performs a heat transfer process with the latter and heats it up to a temperature closer to T INTERMEDIATE (however, not reaching T INTERMEDIATE ).
  • the intermediate temperature work medium flows into the gradient tanks in a two-beat sequence.
  • the first portion of the heated intermediate temperature work medium to exit the pressure vessel is at a temperature T HEATED such that T INTERMEDIATE ⁇ T HEATED ⁇ T HOT '
  • the second portion of the work medium will be emitted from the pressure vessel at a temperature T HOT ' such that T INTERMEDIATE ⁇ T HEATED ' ⁇ T HEATED ⁇ T HOT ' etc.
  • the heated work medium is passed into the gradient tank of its respective pressure vessel such that the gradient tank contains therein the different portions of the heated work medium and maintains a temperature gradient therebetween.
  • the first portion of the cooled intermediate temperature work medium to exit the pressure vessel is at a temperature T COOLED such that T INTERMEDIATE > T COOLED > T COOL '
  • the second portion of the work medium will be emitted from the pressure vessel at a temperature T COOLED ' such that T INTERMEDIATE > T COOLED ' > T COOLED > T COOL ' etc.
  • the cooled work medium is passed into the gradient tank of its respective pressure vessel such that the gradient tank contains therein the different portions of the cooled work medium and maintains a temperature gradient therebetween.
  • each portion of the heated intermediate temperature work medium is at a temperature T HEATED n such that T INTERMEDIATE ⁇ T HEATED n ⁇ T HOT .
  • the intermediate temperature work medium passing therethrough also never leaves the pressure vessel at a temperature T INTERMEDIATE , but rather always slightly cooler.
  • each portion of the cooled intermediate temperature work medium is at a temperature T COOLED n such that T INTERMEDIATE > T COOLED n > T COOL .
  • the work medium in each of the gradient tanks is maintained with a temperature gradient, slowing down mixing between the different portions of the heated/cooled intermediate temperature work medium.
  • the second beat of the sequence is performed, also referred to as the cross-over step: work medium from the gradient tank of the heated pressure vessel (i.e. the gradient tank containing the heated intermediate temperature work medium used during the first beat) is passed through the opposite (cooled) pressure vessel containing the pressure medium previously cooled down by the low temperature work medium to a temperature T COLD ', and work medium from the gradient tank of the cooled pressure vessel (i.e. the gradient tank containing the cooled intermediate temperature work medium used during the first beat) is passed through the opposite pressure vessel containing the pressure medium previously heated up by the high temperature work medium to a temperature T HOT '.
  • the work medium from the gradient tanks flows to the opposite pressure vessels in a First In Last Out (FILO) order, i.e. the last portion of the heated up intermediate temperature work medium to enter the gradient tank (which is also the coolest portion of the heated intermediate temperature work medium) will be the first portion to be passed through the opposite pressure vessel.
  • FILO First In Last Out
  • T INTERMEDIATE ⁇ T HEATED n ⁇ T HOT ' and T INTERMEDIATE > T COOLED n > T COLD ' the temperatures T AV_C and T AV_H are hotter/cooler than a corresponding average temperature T AV_C ' and T AV_H ' that would have been achieved if only intermediate temperature work medium at T INTERMEDIATE was used to cool/heat the pressure medium.
  • step (I) and (III)) repeats itself but with high temperature work medium now flowing to the previously cooled pressure vessel and the low temperature work medium now flowing to the previously heated pressure vessel.
  • the switch step thus provides an improvement over the previously described example of the generator allowing for a more efficient heat transfer process with the pressure medium, so that the heated/cooled pressure medium returns, after heating/cooling to a temperature much closer to T INTERMEDIATE , and can even reach a temperature which is lower/higher than T INTERMEDIATE .
  • intermediate temperature work medium (although not necessarily at temperature T INTERMEDIATE ) is passed through the radiator, allowing it to perform a heat transfer process with the outside environment (usually ambient air but can be any other medium in which the radiator is immersed).
  • the generator due to thermodynamic performance of the work medium and pressure medium, the generator constantly produces heat, which is, in turn, emitted to the ambient environment through the radiator. More particularly, the arrangement is such that the increase in temperature of the heated intermediate temperature work medium is slightly greater than the decrease in temperature of the cooled intermediate temperature work medium. This difference in increase/decrease is expressed by slight overheating of the intermediate temperature work medium, i.e. excess heat being generated. However, it is compensated by the eviction of the excess heat via the radiator.
  • the entire generator, and more particularly, all the piping of the generator configured for passing high/low/intermediate temperature work medium is always under constant pressure (i.e. there is always work medium present in each section of the pipe, whether circulating or not).
  • the gradient tanks contain therein intermediate temperature water (i.e. water at temperature T INTERMEDIATE ).
  • intermediate temperature water i.e. water at temperature T INTERMEDIATE
  • the work medium previously contained therein is emitted and re-circulated back into the auxiliary storage reservoir containing intermediate temperature work medium at temperature T INTERMEDIATE .
  • intermediate temperature work medium is circulated into the gradient tanks, thus pushing the heated/cooled intermediate temperature work medium out of the reservoir and into the desired pressure vessel. It is noted that during the second beat of the sequence, the reservoirs (high/low/intermediate) are shut off from the circulating fluid so that, in fact, only intermediate temperature work medium is circulated through the piping of the generator.
  • the generator can also comprise one or more thermostats configure for providing control over high/low/intermediate temperature work medium as well as heated/cooled pressure medium.
  • the thermostat/s can be configured for maintaining the intermediate temperature work medium at a temperature generally equal to that of the ambient environment (air, water etc.) the generator is surrounded by.
  • the generator can further comprise an accumulator unit containing a storage work medium.
  • the accumulator unit is provided with a heating arrangement which is configured to be operated by output power provided by the generator.
  • the accumulator unit can be in selective fluid communication with the pressure vessel via corresponding inlet and outlet lines which are connected to the inlet and outlet valve respectively.
  • a portion of the output power of the generator can be used to operate the heating arrangement, so that it heats up the work medium contained within the accumulator unit.
  • the high temperature reservoir can be shut-off, and the accumulator unit can provide the necessary high temperature work medium.
  • any excess output power which is not used can be provided to the accumulator unit, thereby operating, de facto, as an accumulator.
  • the heating element can be a heating coil or any other element which is configured to be heated so as to heat the storage work medium.
  • the heating arrangement can be constituted by an auxiliary heat pump (not shown), and the accumulator unit can comprise two compartments, one being in thermal communication with the evaporator side of the auxiliary heat pump and the other in thermal communication with the condenser side of the auxiliary heat pump.
  • each of the compartments can have a respective inlet to which corresponding inlet and outlet lines are attached respectively.
  • the arrangement can be such that the outlet is located at a top end of the high temperature compartment, while the inlet is located at a bottom end of the high compartment.
  • the outlet of the low temperature compartment can be located at a bottom end of the compartment while the inlet thereof can be located at a top end of the compartment.
  • the above arrangement allows for withdrawing high temperature work medium from a high temperature zone of the high temperature compartment, and returning the work medium to a low temperature zone of the high temperature compartment.
  • this arrangement allows withdrawing low temperature work medium from a low temperature zone of the low temperature compartment, and returning the temperature work medium to a high temperature zone of the low temperature compartment.
  • auxiliary work medium in the compartments In operation, once the auxiliary work medium in the compartments and reaches temperatures which are similar to those of the high/low temperature reservoirs respectively, it can be used in operation of the generator while the main heat pump temporarily ceases its operation.
  • the accumulator can comprise both a heat pump and direct heating elements (e.g. coil), and work in combination with both.
  • the high temperature compartment can be provided with heaters which are configured for directly heating the storage fluid contained within the compartment.
  • the storage medium within the high/low temperature compartment can reach a heating/cooling limit (i.e. reaching a maximal/minimal temperature limit). In such an event, the operation of the auxiliary heat pump can be interrupted, and the heaters are then used to further heat the storage medium in the high temperature compartment.
  • the work medium in the high temperature compartment can be used as a high temperature work medium, while the work medium in the low temperature compartment is used as the low/intermediate work medium.
  • the A/C unit used for generating the heat/cold source for the respective high/low temperature reservoir can be in the form of a cascade arrangement, comprising several grades, each of which operates as a basic A/C compression/expansion manner.
  • the cascade arrangement can comprise a first end-grade configured for providing the heat for the high temperature reservoir and a second end-grade configured for providing the necessary cold for the low temperature reservoir.
  • Each of the grades comprises an evaporator section, a compressor, an expansion member and a condenser section, and contains a fluid (gas or liquid) configured for undergoing corresponding compression and expansion to provide a high temperature source at the condenser and a low temperature source at the evaporator as known per se.
  • the fluid in each of the grades is configured to have an evaporator temperature T EVAP(n) and a condenser temperature T COND(n) , where T COND(n) > T EVAP(n) , and n denotes the number of the grade.
  • the cascade arrangement is designed such that the condenser section of one grade is configured for performing a heat exchange process with the evaporator section of the subsequent grade.
  • the design can be such that the temperature of compressed fluid in the condenser of the one grade is higher than the temperature of the expanded fluid in the evaporator of the subsequent grade with which the heat exchange process takes place.
  • Each of the grades can operate in a closed-loop, i.e. the fluid of each grade does not come in contact with the fluid of a subsequent grade.
  • the heat exchange process between two subsequent grades can be performed via an intermediate member, e.g. a heat conducting surface.
  • the heat exchange process between two subsequent grades takes place in a heat exchanger comprising an inner tube of diameter D 1 passing through an outer tube of diameter D 2 ⁇ D 1 .
  • the inner tube constitutes the condenser of the one grade while the outer tube constitutes the evaporator of the subsequent grade.
  • compressed fluid of one grade heated due to compression thereof to a temperature T COND(n)
  • an expanded fluid of the subsequent grade cooled due to expansion thereof to a temperature T EVAP(n+1) ⁇ T COND(n)
  • flows through the outer tube so as to flow around the inner tube.
  • a heat exchange process takes place via the wall of the inner tube - the heated fluid coming in contact with an inner surface of the inner tube and the cooled fluid coming in contact with an outer surface of the inner tube.
  • heat is emitted from the fluid flowing within the inner tube to the fluid flowing in the outer tube.
  • the design of the heat exchanger can be such that the volume defined by the inner tube is smaller than the volume defined between the external surface of the inner tube and the internal surface of the outer tube.
  • the inner surface of the outer tube is essentially round in cross-section taken perpendicular to a longitudinal axis of the tube, while the inner and/or outer surfaces of the inner tube can be of a more convoluted shape in the same cross-section.
  • the flow direction within the condensing portion and evaporator portion can either be parallel, i.e. both the compressed fluid and the expanded fluid flow in the same direction (as in a parallel heat exchanger).
  • the flow direction can be opposite, i.e. i.e. the compressed fluid and the expanded fluid flow in opposite directions (as in a counterflow heat exchanger).
  • Each of the grades can contain a different fluid, and is configured for operation at a different temperature range.
  • the difference between the high temperature T COND of the fluid in the condenser and the low temperature T EVAP of the fluid in the evaporator can be generally similar between all the grades.
  • the temperature difference can be about 30°C.
  • the cascade arrangement can comprise seven grades, each operating at a temperature range ⁇ of about 30°C, with the temperature of the fluid at the evaporator of the first grade T EVAP(1) is as low as 0°C, and the temperature of the fluid at the condenser of the seventh grade T EVAP(7) is as high as 245°C.
  • the generator can also comprise a controller configured for regulating the operation of the compressor and/or the expansion valve of each grade so as to maintain a desired difference between the compression temperature of a fluid in one grade and the expansion temperature of fluid in a subsequent grade.
  • each grade can comprise a compressor configured for compressing the fluid circulating in the grade during its progression between the evaporator to the condenser.
  • the compressors of the grades can have different power consumptions so that each grade is configured for operating at a different COP.
  • the COP for heating/cooling is calculated as the temperature difference divided by the high/low temperature. Therefore, a grade having a 30°C condenser/evaporator difference between 27°C and 57°C yields a COP which is different than that of a grade having a 30°C condenser/evaporator difference between 90°C and 120°C.
  • each grade can be fitted with the same compressor (i.e. providing the same power).
  • the temperature difference between the condenser/evaporator in each grade will gradually be reduced.
  • the ⁇ for the first grade can be 30°C for the first grade, 24°C for the second grade, 20°C for the third grade and so forth.
  • each of the seven grades can contribute about 30°C, thereby yielding a temperature difference of 240°C.
  • a single compression/expansion cycle having a temperature difference of 240°C has a COP which is much lower than that of seven compressors, each contributing to its own compression/expansion cycle.
  • the energy going to waste in the single compression/expansion cycle is greater than that of the cascade arrangement, making the latter more efficient for the presently described generator.
  • the generator can comprise a radiator configured for allowing the work medium to perform a heat exchange process with the environment after heating/cooling the pressure fluid within the pressure vessels.
  • the high work medium after heating the pressure fluid (and subsequently cooling down) is provided directly back into the high temperature reservoir, while the low temperature work medium, after cooling the pressure fluid (and subsequently heating up) passes through the radiator in order to be cooled down by the environment.
  • the radiator unit can be configured for being controlled according to the temperature of the environment and the resulting temperature of the low temperature work medium, so that the low temperature work medium leaves the radiator unit at a generally constant and predetermined temperature.
  • the radiator unit can comprise a control element configured for determining the cooling rate provided by the radiator, and a sensing unit configured, on the one hand, for measuring the temperature of the low temperature work medium leaving the radiator unit, and, on the other hand, providing the data to the control unit.
  • the sensing unit measures the temperature T' of the low temperature work medium leaving the radiator unit and:
  • the configuration is such that the heat exchange process within the radiator takes place with the low temperature work medium entering the first grade of the cascade arrangement associated with the low temperature reservoir.
  • this heat exchange process brings the low temperature work medium (which is now heated after passing through the pressure vessel) to a temperature T' ⁇ T ENV , while T COND > T ENV > T EVAP , where T COND is the high temperature of the compressed fluid at the condenser of the first grade and T EVAP is the low temperature of the expanded fluid at the evaporator of the first grade.
  • each grade (depending on its compressor) is designed for a predetermined temperature range, i.e. it is configured to remove a predetermined amount of heat from the cold end (evaporator). If the evaporator is located at an environment providing it with more heat than the compressor can withdraw in the compression/expansion cycle of the grade, the grade becomes less efficient (i.e. the compressor can't cope with removing heat from the evaporator).
  • the cascade arrangement can further be configured for adjusting its operation, and its overall temperature range, in accordance with the temperature of the environment. More particularly, if the temperature of the environment increases such that T ENV > T COND > T EVAP , and the first grade of the cascade arrangement becomes less efficient (as described above), the cascade arrangement can be configured for bypassing the first grade and connecting the low temperature reservoir to the second grade.
  • the cascade arrangement instead of operating between a low temperature of T EVAP(1) and a high temperature of T COND(7) , the cascade arrangement now operates between as low temperature of T EVAP(2) and a high temperature of T COND(7) .
  • the overall temperature difference between the high and low temperature reservoir decreases, but the efficiency of the cascade arrangement remains generally the same.
  • the cascade arrangement can have a bypass module comprising an evaporator associated to the second grade and located within the low temperature reservoir.
  • the bypass module can further comprise valves allowing shutting off the first grade completely, and directing the compressed fluid of the second grade to expand within the evaporator of the bypass module instead of in the original evaporator of the second grade.
  • a full cycle of one side of the generator can include the following steps (taking into account that the opposite side undergoes the same steps only at a shift):
  • steps (a) and (b), and (e) and (f) can last for a first period of time and steps (c) and (d), and (g) and (h) can last for a second period of time which is greater than the first period of time.
  • the second period of time can be twice as long as the first period of time.
  • the first period of time can be about 5 seconds and the second period of time can be about 10 seconds.
  • the generator can be utilized in a variety of power-requiring systems, e.g. households, vehicles (for example cars, boats, plains, submarines etc.), industrial systems etc.
  • the generator can be configured to use this particular medium as the work medium.
  • the work medium can be sea water.
  • the generator of the present invention can incorporate the following features:
  • FIG. A a schematic diagram is shown demonstrating a basic arrangement of the generator of the present invention comprising a heat differential module, a pressure module and a conversion module.
  • the heat differential module comprises a first, high temperature reservoir and a second, low temperature reservoir, each containing therein a work medium WM (not shown) at a respective high/low temperature.
  • the first, high temperature reservoir is thermally associated with a condenser end CE of a heat pump HP, so that operation of the heat pump HP (under provision of power W 1 ) provides heat Q to the condenser end so as to maintain the work medium WM in the first reservoir at high temperature.
  • the second, low temperature reservoir is thermally associated with the environment.
  • Each of the reservoirs is provided with an inlet line IL which is in selective fluid communication with an inlet of the pressure vessel PV of the pressure module via an inlet valve I and an outlet line OL which is in selective fluid communication with an outlet of the pressure vessel PV via an outlet valve O.
  • the pressure vessel PV contains therein a pressure medium PM and is formed with a central conduit C passing therethrough which is in fluid communication with the inlet valve I and with an outlet valve O, allowing the passage therethrough of the work medium WM from the reservoirs.
  • the pressure vessel PV is provided with a pressure line PL being in fluid communication with the pressure medium PM, which is in fluid communication with the conversion module.
  • the conversion module in turn, comprises a piston P which is in fluid communication with the pressure line PL, and with a generator.
  • the piston in configured for reciprocation which is utilized by the generator for the generation of output power W 2 .
  • high/low temperature work medium WM is selectively provided into the pressure vessel, entailing expansion and shrinkage of the pressure medium PM, consequently entailing reciprocation of the piston P. Specifically, the following steps are performed:
  • the heat pump HP withdraws an amount of heat Q' (heat absorbed from the environment with which the evaporator is in thermal communication) from the evaporator end thereof into the condenser end by applying an amount of work W 1 .
  • the amount of heat Q contained within the high temperature work medium WM of the high temperature reservoir Q Q' + W 1 .
  • the amount of heat Q is provided to the pressure medium PM via the heat exchange process, so that a portion Q 1 of the amount Q of heat is used for displacing the piston P, and at least a portion amount Q 2 of heat is absorbed by the low temperature work medium WM via heat exchange with the pressure medium PM.
  • An amount of heat Q 2 is released back to the outside environment during passage of the heated low temperature work medium WM via outlet line OL, and from the environment, is free to be re-drawn into the evaporator end of the heat pump HP.
  • Such an arrangement provides for a certain amount of heat Q 2 to be recovered by the generator (i.e. a recovery arrangement).
  • the amount of heat Q 2 is less than the amount of heat Q' participating in the thermodynamic process of the heat pump HP, and thus the heat pump constantly withdraws additional heat from the environment (on top of Q 2 ) to allow provision of a full amount Q' to the condenser end.
  • the amount of output work W 2 provided by the generator of the conversion unit depends on the amount Q 1 of heat which is converted into energy thereby.
  • the arrangement is such that the amount Q 1 of heat is greater than the amount Q' + W 1 , so that the output energy W 2 produced is greater than W 1 .
  • Fig. B an alternative arrangement is shown, demonstrating direct heat recovery arrangement.
  • the outlet line LO of the low temperature reservoir is not returned directly back into the low temperature reservoir upon exiting the pressure vessel, but rather is first passed through the evaporator end of the heat pump HP.
  • the heat Q 2 is directly returned to the evaporator end of the heat pump HP, thereby increasing the efficiency of the operation of the generator.
  • FIG. C yet another alternative arrangement of the generator is shown demonstrating a cooled reservoir arrangement in which the first, high temperature reservoir is in thermal communication with the condenser end of the heat pump HP (as in previous examples), while the low temperature reservoir is in thermal communication with the evaporator end of the heat pump HP.
  • the low temperature work medium WM recovers a partial amount of heat Q 2 from the pressure medium PM upon a heat exchange process therewith, and a remaining amount of heat q from the environment to provide an amount of heat Q' form the evaporator end to the condenser end of the heat pump HP.
  • Fig. D another arrangement of the generator is shown, demonstrating dual operation of pressure vessels.
  • the pressure module comprises two pressure vessels, each being in selective fluid communication with the high/low temperature reservoirs on the one hand, and on the other hand being in fluid communication with its own piston arrangement.
  • the arrangement is further such that each of the pistons is in mechanical connection with the generator, so that reciprocation of both pistons is used by the generator for the generation of output power.
  • reciprocation of the pistons is coordinated so that when both pistons displace generally in the same direction generally at the same time.
  • the pressure medium PM of the bottom pressure vessel increases its volume and pushes its piston to the right
  • the pressure medium PM of the top pressure vessel decreases it volume, displacing the piston to the left and vice versa.
  • the terms ' top ' and ' bottom ' are used solely for descriptive purposes - as it will be shown in later arrangements, the pistons can also be positioned side-by-side. It is also appreciated that the above arrangement provides for the use of a plurality of pressure vessels (not only two) which are interconnected with each other.
  • FIG. E in which yet another example of the generator is shown demonstrating an intermediate reservoir arrangement in which the generator comprises three reservoirs: a high/intermediate/low temperature reservoir.
  • This arrangement is a combination of the cooled reservoir arrangement shown in Fig. C, wherein an additional intermediate reservoir has been added containing intermediate temperature work medium.
  • Each of the high/intermediate/low temperature reservoirs is in selective fluid communication with the pressure vessel.
  • the intermediate temperature reservoir can be in thermal communication with the outside environment, while the high/low temperature reservoirs are in thermal communication with the condenser/evaporator ends of the heat pump HP respectively.
  • FIG. F still another example of the generator is shown demonstrating a cross-over arrangement in which the generator comprises two pressure vessels (similar to the dual operation arrangement), and each of the outlet valve is also in selective fluid communication with the inlet valves.
  • each outlet valve O is also provided with a cross-over line COL which provides fluid communication between the outlet valve of one pressure vessel and the inlet valve of the other pressure vessel.
  • the above arrangement provides for a more significant heat recovery from the pressure medium PM. More specifically, instead of emitting/withdrawing a certain amount of heat to/from the environment during it return to the intermediate temperature reservoir, the intermediate temperature work medium WM now emits/withdraws a portion of that amount in a heat exchange with the pressure medium PM, thereby increasing the efficiency of the generator.
  • FIG. G still a further example of the generator is shown demonstrating a heat gradient arrangement in which the generator comprises one pressure vessel (similar to the basic arrangement), and a gradient tank associated with the outlet valve O.
  • the gradient tank comprises an arrangement configured for preventing mixing of portions of work medium contained therein, thereby considerably reducing heat transfer between the portions and the speed with which these portions reach a thermal equilibrium.
  • the gradient tank when used in the present generator, can contain a first portion of work medium at a temperature T1, a second portion of work medium at temperature T2 and so forth so that T1 ⁇ T2 ⁇ and so forth.
  • the gradient tank allows for maintaining the work medium contained therein at a temperature gradient so that T1 > T2 > .... > Tn, or alternatively, T1 ⁇ T2 ⁇ .... ⁇ Tn.
  • the above arrangement provide for another way of performing heat recovery in the generator, thereby further increasing its efficiency. It is also appreciated that the use of the LIFO configuration allows the pressure medium to be gradually heated (starting from the lowest temperature portion first), making better use of the amount of heat of each portion of the work medium.
  • the gradient tank can be used both for the heated low temperature work medium WM and the cooled high temperature work medium WM.
  • the generator can comprise more than one gradient tank.
  • each pressure vessel can be provided with its own gradient tank and/or gradient tanks are provided for high/low temperature work medium.
  • FIG. H still a further example of the generator is shown demonstrating an accumulator (green battery) arrangement in which the generator further comprises an accumulator unit containing a storage work medium.
  • the accumulator unit is provided with a heating arrangement which is configured to be operated by output power W 2 provided by the generator.
  • the accumulator unit is in selective fluid communication with the pressure vessel PV via corresponding inlet and outlet lines which are connected to the inlet and outlet valve respectively.
  • a portion of the output power of the generator is used to operate the heating arrangement, so that it heats up the work medium contained within the accumulator unit.
  • the high temperature reservoir can be shut-off, and the accumulator unit can provide the necessary high temperature work medium.
  • any excess output power which is not used can be provided to the accumulator unit, thereby operating, de facto, as an accumulator.
  • the heating element can be a heating coil or any other element which is configured to be heated so as to heat the storage work medium.
  • the heating arrangement can be constituted by an auxiliary heat pump (not shown), and the accumulator unit can comprise two compartments, one being in thermal communication with the evaporator side of the auxiliary heat pump and the other in thermal communication with the condenser side of the auxiliary heat pump.
  • a generator generally designated 1, comprising an air conditioning unit 10 connected to a work medium sub-system 100, two pressure vessels 200, a mechanical power assembly 300, a radiator unit 400, a power generator unit 500, an accumulator unit 50 and output.
  • each of the vessels 200 contains a pressurized fluid, and the generator operates on the principle of periodic increase/decrease of the volume of the pressurized liquid to be used for mechanical back and forth displacement of a piston for generating electricity.
  • the pressure vessel 200 has a hollow cylinder body 210, and a hollow central core 240 passing therethrough, such that there is formed a cavity between the outer surface 242 of the central core 240 and the inner surface 214 of the cylinder body 210, which is adapted to contain the pressurized fluid.
  • the inner space 243 of the hollow central core 240 is adapted to received therethrough a high/intermediate/low temperature work medium from the work medium sub-system 100, in order to manipulate the temperature of the pressurize fluid.
  • the work medium sub-system 100 comprises a high temperature reservoir 110, a low temperature reservoir 120 and a reservoir 130 of intermediate temperature water at room temperature.
  • the terms 'high', 'low' and 'intermediate' refer in this specific example to the corresponding temperatures: about 40°C, about 10°C and about 25°C.
  • the work medium sub-system is in fluid communication on one side with an air conditioning unit 10, and on the other side with the pressure vessels 200.
  • Each of the reservoirs 110, 120 and 130 is connected to both of the pressure vessels 200 via distribution valves 140. Since the generator 1 comprises two pressure vessels 200, and is generally symmetric about a central plane passing therethrough, left (L) and right (R) designations are used where applicable.
  • the manner of connection between the work medium sub-system 100 and the right pressure vessels 200R will now be explained in detail (it should be noted that the manner of connection to the second pressure vessel 200 is essentially similar):
  • the high temperature reservoir 110 is connected to the distribution valve 140R via inlet 111R and to the outlet of the pressure vessel 200R via line 112R.
  • low temperature reservoir 120 is connected to the distribution valve 140R via inlet 121R and to the outlet of the pressure vessel 200R via line 122R.
  • the reservoir 130 is connected to the distribution valve 140R via inlet 131R and to the outlet of the pressure vessel 200R via line 132R.
  • the line 132R is then connected to a cooling element 410R of the radiator unit 400, and the outlet of the cooling element 410 is connected back to the reservoir 130 via line 133R.
  • the reservoirs 110 and 120 as well as the piping connecting them to the pressure vessels 200L, 200R, and the radiator unit 400 can be applied with thermal insulation in order to prevent heat losses to the piping itself.
  • the distribution valves 140L, 140R can also be made of low conductivity materials (e.g. Titanium or plastic) or covered with thermal insulation.
  • the piping connecting the reservoir 130 to the pressure vessels 200L, 200R, and the radiator unit 400 can be made of materials having high heat transfer coefficients (for example copper) and be exposed to the environment, allowing the temperature of the 'intermediate' water to be as equalized as possible with that of the surrounding environment.
  • the piping described above can be constructed such that it has an in-built water pressure (and no air), that is maintained throughout the operation of the generator 1.
  • the intermediate temperature water reservoir 130 can be connected to the household water pressure (consumer pressure) via faucet 135 ( Fig. 1C ), such that in case of a drop of pressure in the system, additional water can be provided to the system to re-build the pressure.
  • the vessels 200 are filled with the pressure medium, which is pressurized to about 5000 atm. (500 MPa).
  • the cores 240 as well as all of the above connecting lines are filled with the work medium at a standard household pressure (consumer pressure).
  • the temperature of the pressure medium is equal to the room temperature (e.g. about 25°C), and correspondingly, the piston of the motor is at an intermediary position.
  • the distribution valve 140R opens the port for line 111R, and high temperature water from the high temperature reservoir begins circulating through the core 240 of the vessel 200R. While passing through the core 240, a heat exchange process takes place between the high temperature water (at about 40°C) and the pressure medium (at about 25°C), causing the pressure medium to be heated up. As a result of heating, the pressure medium increases its volume (expands), consequently displacing the piston towards a first end point thereof.
  • the high temperature water now of slightly reduced temperature, now exits the pressure vessel 200R via line 112R, and is returned to the high temperature reservoir. This process takes place until the pressure medium is heated (and expanded) to a desired/sufficient amount, i.e. until the piston is displaced to its desired first end position.
  • the pressure medium is not heated to be the same temperature as the high temperature water, but rather several degrees below, e.g. 32-35°C.
  • the distribution valve 140R closes the port for the high temperature water inlet, and opens the port for line 131R of the intermediate temperature water reservoir.
  • Intermediate temperature water i.e. at 25°C
  • the heated pressure medium at about 32-35°C gives away its heat to the intermediate temperature water.
  • the pressure medium is cooled and the intermediate temperature water is heated.
  • the cooling down of the pressure medium causes its volume to consequently be reduced, entailing mechanical displacement of the piston towards its initial position. This process continues until the pressure medium is cooled to a desired/sufficient amount, i.e. until the piston is displaced back to its initial (intermediary) position.
  • the heated intermediate temperature water leaves the pressure vessel 200R via line 132R, and enters the cooling element 410R of the radiator unit 400.
  • the heated intermediate temperature water undergoes another heat exchange process in which it emits to the surrounding atmosphere the heat absorbed from the heated pressure medium.
  • the intermediate temperature water returns to the intermediate temperature water reservoir 130 via line 133R at a temperature close to its initial temperature within the reservoir (at about 25 °C).
  • the second part takes place, in which a similar operation is performed using the low temperature water as follows: the distribution valve 140R shuts off the water from the intermediate temperature water reservoir 130, and opens for fluid communication with line 121R incoming from the low temperature reservoir. Low temperature water is then passed through the core 240 of the vessel 200R. While passing through the core 240, a heat exchange process takes place between the low temperature water (at about 10°C) and the pressure medium (which is now, after the first part of the cycle, back to about 25°C), causing the pressure medium to be cooled down. As a result of cooling, the pressure medium decreases its volume (compresses), consequently displacing the piston towards a second end point thereof.
  • the low temperature water now of slightly elevated temperature, exits the pressure vessel 200R via line 122R, and is returned to the low temperature reservoir. This process takes place until the pressure medium is cooled (and compressed) to a desired/sufficient amount, i.e. until the piston is displaced to its desired second end position.
  • the pressure medium is not cooled down to be the same temperature as the low temperature water, but rather several degrees below, e.g. 15-18°C.
  • the distribution valve 140R closes the port for the low temperature water inlet, and re-opens the port for line 131R of the intermediate temperature water reservoir.
  • Intermediate temperature water i.e. at 25°C
  • the pressure vessel 200R causing a reverse heat transfer process to take place, in which the cooled pressure medium (at about 15-18°C) absorbs heat from the intermediate temperature water.
  • the pressure medium is heated up and the intermediate temperature water is cooled down.
  • the heating of the pressure medium causes its volume to consequently be increased, entailing mechanical displacement of the piston towards its initial position. This process continues until the pressure medium is heated to a desired/sufficient amount, i.e. until the piston is displaced back to its initial (intermediary) position.
  • the cooled intermediate temperature water leaves the pressure vessel 200R via line 132R, and enters the cooling element 410R of the radiator unit 400.
  • the cooling element 410R the cooled intermediate temperature water undergoes another heat exchange process in which it absorbs from the surrounding atmosphere the heat lost to the heated pressure medium.
  • the intermediate temperature water returns to the intermediate temperature water reservoir 130 via line 133R at a temperature close to its initial temperature within the reservoir (at about 25°C).
  • the intermediate temperature water after passing through the pressure vessel 200R, is passed through the cooling element 410 of the radiator unit 400, in order to respectively convey to/absorb from the atmosphere the required amount of heat gained/lost during the heat exchange process with the pressure medium.
  • the high temperature reservoir 110 and the low temperature reservoir 120 constitute part of the air conditioning unit 10, as is observed from Fig. 1D .
  • Each of the reservoirs 110, 120 has fully immersed therein a tube array adapted to receive an operating fluid of the air conditioning unit 10, e.g. Freon gas.
  • the air conditioning unit 10 has a compressor (not shown) adapted to compress the Freon gas into the tubes of the high temperature reservoir 110 through line 12, such that the heated Freon gas conveys the heat to the water of the high temperature reservoir.
  • the cooled Freon gas then leaves the high temperature reservoir 110 via line 14 back to the air conditioning unit 10.
  • the cooled Freon gas is then provided to the low temperature reservoir 120 via inlet 22, in the tubes of which it is allowed to expand, thereby cooling the water of the low temperature reservoir 120, and leaving it via line 24 back into the air conditioning unit 10. This process takes place repeatedly in order to provide a high temperature water reservoir in the high temperature reservoir 110, and a low temperature water reservoir in the low temperature reservoir 120.
  • the pressurized fluid within the pressure vessels 200L, 200R should be chosen such that it has good heat expansion properties (expands considerably under heating), as well as sufficient heat transfer capabilities.
  • materials used for the pressurized fluid can be (yet not limited to): water, N-Pentene, Diethyl ether, Ethyl Bromide, Methanol, Ethanol, Mercury, acids and others. It should also be understood that the pressurized fluid is not limited to a liquid medium and can be constituted also by a gas material.
  • the work medium passing through the core 240 should be chosen such that it has sufficient heat transfer properties and a density allowing easy propulsion thereof through the generator 1.
  • Examples of materials used for the pressurized fluid can be (yet not limited to): water, Mercury, Freon and others. It should also be understood that the work medium is not limited to a liquid medium and can be constituted also by a gas material (e.g. Freon in gas form).
  • FIG. 2A to 4A to 4F unique construction of the pressure vessels 200 and the cores 240 will be described in detail.
  • Each of the pressure vessel 200L, 200R comprises an external shell 210 made of a material which is both strong enough and thick enough to sufficiently withstand the pressure of the pressurized fluid, i.e. about 5000 atm. (500 MPa).
  • An example of such a material can be steel.
  • the core 240 can be made, on the one hand of a material which is also able to withstand the high pressure within the pressure vessel 200L, 200R, and on the other hand has sufficient heat capacity and heat transfer properties in order to provide an effective heat transfer process between the work medium and the pressurized fluid. Examples of such a material can be Copper-Beryllium, 4340 steel etc.
  • FIG. 4B Particular reference is drawn to Fig. 4B , in which a segment of the core 240 is shown. It is observed that the inner and outer surfaces of the core are formed with surface elements 247 in the form of pyramids. The purpose of the surface elements 247 is to increase the contact area with the work medium and the pressurized fluid, thereby increasing the effectiveness of the heat transfer between the core 240 and the work medium / pressurized fluid. Forming of the elements 247 can be performed by gradual sand spraying on the outside, and on the inside using a designated finishing head (not shown). In this manner, the surface area of the core 240 can be increased by almost 20 times (compared to a smooth inner/outer surface).
  • the mixing unit 220 adapted for mixing the pressurized fluid during operation of the generator in order to increase its effectiveness.
  • the mixing unit 220 has a central axis X extending in the direction of the core 240 and comprises a plurality of fan blades 224 spread about the central axis X, connected to one another using rings 225.
  • the mixing unit 220 is delimited on each side by a limit ring 223.
  • the fan blades 224 can be made of a material having sufficient insulation properties so as to reduce heat losses to the blades 224 themselves, having low heat capacity to reduce heat absorption and lightweight to minimize the required drive power.
  • Such a material can be, for example, Titanium.
  • the limit ring 223 is fitted with a spur-gear 229 adapted to mesh with a gear 228a mounted on a driving rod 226.
  • the driving rod 226 is driven by an external motor 205L, 250R, the connection being between a gear 228b mounted on the driving rod 226 and a corresponding gear 254 of the driving motor 250R.
  • the motor can be located within the pressure vessel, not necessarily outside the vessel - saves on energy required for overcoming dynamic resistance of the shaft and the forces acting in conjunction with the seal.
  • Another option is revolving the shaft using a magnetic mechanism - eliminating the need for complex dynamic seals.
  • the heat dissipation unit 280 is in the form of a sleeve 282 from which a plurality of heat dissipating elements 284 extend radially, adapted for increasing the heat transfer between the core 240 and the pressurized fluid.
  • the heat dissipation unit 290 has a central sleeve 292 with radial heat dissipation elements 294 extending therefrom.
  • the heat dissipation unit 290' is generally similar with the difference being in that each of the heat dissipation elements 294' is formed with additional extension 296' for increased heat transfer.
  • the heat dissipation units 280, 290 and 290' are firmly attached to the core 240 so as to have a maximal surface contact therewith, allowing for better conduction heat transfer.
  • the pressure vessel 200L, 200R further comprises an inner shell 230 having a diameter smaller than that of the inner surface 214 of the shell 210, and greater than that of the mixing unit 220.
  • the shell 230 divides the inner space of the pressure vessel 200L, 200R into an inner chamber 232 between the shell 230 and the mixing unit 220, and an outer chamber 234 between the shell 230 and the inner surface 214 of the pressure vessel 200L, 200R.
  • the shell 230 can be made of a material having sufficient insulation properties so as to reduce heat losses to the shell 230 itself, for example, Titanium.
  • the inner chamber 232 and the outer chamber 234 are in fluid communication with one another since the shell 230 is open at both ends.
  • separation to an inner chamber 232 and an outer chamber 234 facilitates insulation of the pressurized fluid of the inner chamber 232 by the pressurized fluid in the outer chamber 234 (despite the face they are in fluid communication with one another). Insulation of the pressurized fluid increases the efficiency of the generator 1 by reducing the heat losses to the external steel shell 210.
  • the circulation created by the mixing unit 240 hardly effects that pressurized fluid contained between the shell 230 and the inner surface of shell 210.
  • the core 240 is fitted therein with a drive-screw 248 adapted to revolve about itself in order to propel the work medium through the core 240 (working on a principle similar to the Archemedes screw).
  • the drive-screw 248 is driven by an external motor 260L, 260R, and is connected thereto via meshing of the gear 246 with the gear 264 of the motor 260L, 260R.
  • the drive-screw 248 can be made of a material having sufficient insulation properties so as to reduce heat losses to the drive-screw 248 itself. Examples of such a material can be Titanium or high-strength plastic. It is noted that over variations of the drive screw 248 can be used, as will be evident from Figs. 14F and 14G to be later discussed.
  • each of the pressure vessels 200R, 200L is fitted at both ends thereof with a sealing assembly 270, comprising a head seal 272 fastened by bolts, a main seal body 273 onto which three sealing members 274 are mounted, an auxiliary seal assembly 276 and a soft sealing member 278.
  • a sealing assembly 270 comprising a head seal 272 fastened by bolts, a main seal body 273 onto which three sealing members 274 are mounted, an auxiliary seal assembly 276 and a soft sealing member 278.
  • two seals 276', 278' of similar design shown Fig. 3C ), used for sealing the space between the main seal body 273 and the core 240.
  • FIG. 3A to 3E the mechanical power assembly 300 and the power generator unit 500 will now be described in detail.
  • Each of the pressure vessels 200L, 200R is fitted at one end thereof with a mechanical power assembly 300L, 300R. Since both mechanical power assemblies 300L, 300R are essentially similar, only one of them will now be described in detail, understanding that the description holds true for the other assembly as well.
  • the mechanical power assembly 300R is in maintained in fluid communication with the pressure vessel 200R via an outlet port 216R.
  • the mechanical power assembly 300R comprises a piston unit 320R, and a pressure regulator 340R.
  • the piston unit 320R has a hollow housing 322 and a neck portion 324 articulated to the port 216 of the pressure vessel 200R.
  • the neck portion 324 is formed with an inlet orifice 326 providing fluid communication between the pressure vessel 200R and the neck portion 324.
  • a displaceable piston 330 having a head portion 332 snugly and sealingly received within the housing 322 by o-rings 333, and a neck portion 334 snugly received within the neck portion 324.
  • the housing 322 is divided into an inlet chamber 323 I being in fluid communication with the pressure vessel 200R to receive therein the pressure medium, and an outlet chamber 323 O , the chambers being isolated from one another by the heat portion 332.
  • the design of the piston unit 320 is such that the inlet chamber 323 I is adapted to contain therein some of the pressure medium and the outlet chamber 323 O is adapted to contain therein an auxiliary work medium, adapted for operating the generator unit 500.
  • a fluid can be, for example, machine oil or the like.
  • the housing 322 is further formed with an outlet port 325 through which the auxiliary fluid can leave the piston unit towards the generator unit 500.
  • stage (I) of the generator cycle the pressure medium heat up and its volume increases, thereby flowing into the inlet chamber 323 I , pushing the head portion 332 of the piston 330 towards the bottom 328 of the housing 322.
  • the auxiliary work medium contained within the outlet chamber 323 O is pressured out through the outlet port 325 and into line 302.
  • stages (II) and (III) of the cycle the pressure medium cools down and its volume decreases, thereby flowing from the inlet chamber 323 I back into the pressure vessel 200R, pulling the head portion 332 of the piston 330 towards the neck portion 324 of the housing 322. As a result, the auxiliary work medium is sucked back into the outlet chamber 323 O .
  • the piston 330 is designed such that the cross-sectional area of the head portion 322 is 20 times greater than that of the cross-sectional area of the neck portion 324, thereby reducing the pressure in the outlet chamber 323 O from 5000 atm. (500 MPa) to about 250 atm. (25 MPa).
  • the back and forth movement of the auxiliary fluid is used for operating a piston of the motor 520 ( Figs. 6A and 6B ), which is in turn used for the generation of electricity.
  • auxiliary work medium is also in fluid communication with the pressure regulator 340 situated between the piston unit 320 and the generator unit 500.
  • the pressure regulator 340 is formed with a housing 342 holding therein a piston 350 biased by a compression spring 360.
  • the piston 350 can be biased by a compresses gas, e.g. Nitrogen.
  • the pressure regulator 340 is formed with a T-junction member 343 having an inlet port 345 adapted to receive line 302, a housing inlet 346 and an outlet port 347 connected to line 304.
  • the pressure regulator also functions as a synchronizer of the piston movement in the following manner: if the expansion of the pressure medium in one pressure vessel is too great, and the piston of the other pressure vessel has no room to "retreat", the gas piston will absorb the additional pressure, and will return it upon reciprocation of the mechanism. More particularly, any additional pressure provided to the piston which should not be expressed in movement of the opposite piton is absorbed by the gas piston 340, and alternatively, upon a shortage of pressure, the gas piston 340 compensates for the above shortage.
  • the generator unit 500 comprises a motion converter 520 and a power unit 540.
  • the motion converter 520 comprises a base housing 510, and two piston housings 522R, 522L, each connected at one end to the main conversion unit and at the other end to line 304.
  • the base housing is formed of a top member 512 and a bottom member 514 (of similar design), each member being formed with a channel 516 such that when the two members are attached, there is formed a space 518 (not shown) in which a center plate 513 is adapted to reciprocate.
  • the center plate 513 is fitted with a cam follower 517 via stud 515.
  • the cam follower 517 is adapted to revolve about a second stud 519 under reciprocation of the center plate 513.
  • the cam follower 517 is fixedly attached to plate 511, such that revolution of the cam follower 517 about the stud 519 entails revolution of the plate 511 about its central axis X.
  • a fly wheel (not shown) can also be provided between the gear and the generator in order to overcome top/bottom "dead points".
  • the housing 522R (only one will be described since they are both of similar design), comprises a piston 530R adapted to reciprocate therein, forming in the housing 522R an inlet chamber 524R.
  • the housing 522R is formed with an inlet 526R providing fluid communication between the inlet chamber 524R and the auxiliary work medium incoming from line 304.
  • the pistons 530R and 530L are formed at one end with a head portion 532R, 532L, located closer to the inlets 526R, 526L respectively, and at the other, opposite end, are integrally formed with the center plate 513.
  • the pressurized fluid in the right chamber 200R heats up and increases in volume
  • the pressurized fluid in the left chamber 200L cools down and decreases in volume.
  • the auxiliary work medium in the right piston unit 320R is urged towards the piston 530R pushing on it, while the auxiliary work medium in the left piston unit 320R is sucked in, pulling on the piston 530L.
  • the movement of the pistons 530R, 530L displaced the center plate 513 in one direction.
  • Reciprocation of the center plate 513 entails revolution of the cam follower 517 resulting in revolution of the plate 511 about its central axis. This rotational movement is converted into electrical energy by the power unit 540.
  • a part of the electrical power generated by the power unit 540 is provided to the output, a part for the air conditioning unit 10, and the remainder is provided to a battery 50.
  • the battery 50 can be used for jump starting the system.
  • the above described system 1 can produce at least up to 4 times the amount of electricity used for its operation, i.e. if the generator 1 requires 1kwh (kilowatts per hour) for its operation, it can produce at least up to 4kwh of electricity. It should also be understood that this profit in electricity is gained by performing a heat exchange process with the environment, i.e. using the surrounding medium (air, water) to absorb/convey heat to the water running through the radiator 400.
  • an air conditioning unit 10 allows for the significant gain in electricity production.
  • a space e.g. a room
  • this heat does not go to waste and is used for heating the water in the high temperature reservoir.
  • the generator 1 can also comprise an accumulator arrangement 590 filled with a storage medium, e.g. water, where, in the event that an excess amount of electricity is produced by the generator 1, this excess amount will be diverted to a heating body used for heating the water within the accumulator arrangement 590.
  • a storage medium e.g. water
  • the accumulator arrangement 590 can function as a battery.
  • the high temperature water for the operation of the generator 1 can be provided by the accumulator arrangement 590 instead of by the high temperature reservoir 110.
  • the operation of the air conditioning unit 10 can be reduced (or even be completely interrupted), allowing it to consume less electricity.
  • the air conditioning unit 10 returns to normal operation and the water in the accumulator arrangement 590 will gradually be cooled down.
  • increased pressure within the accumulator arrangement can allow heating it above the boiling point of the work medium, in order to accumulate more heat. For example: water at 5 atm. (0.5 MPa) (standard household pressure) can boil at 150°C.
  • the accumulator arrangement 590 can comprise a heating element configured for directly heating up the water in the accumulator arrangement in order to maintain therein a desired temperature.
  • the generator 1 can also comprise a controller (not shown) adapted to monitor the temperature of the pressurized fluid, the work medium, the temperature of the water in the accumulator arrangement 590, the displacement of the pistons 330R, 330L, 530R, 530L, the pressure within the pressure regulator 340, the displacement of the center plate 513 etc.
  • the controller can be used to control the operation of the distribution valves 140, the operation of the motors 250, 260, the displacement of the pistons etc.
  • FIG. 11A and 11B another example of the generator is shown, generally designated as 1', and comprising an air conditioning unit 10 connected to a work medium sub-system 100', two pressure vessels 200', a mechanical power assembly 300, a radiator unit 400, a power generator unit 500, a gradient assembly 600, an accumulator unit 50 and output.
  • an air conditioning unit 10 connected to a work medium sub-system 100', two pressure vessels 200', a mechanical power assembly 300, a radiator unit 400, a power generator unit 500, a gradient assembly 600, an accumulator unit 50 and output.
  • the generator 1' is similar in design to the generator 1 previously described, with the difference being in the design and number of the cores passing through the pressure vessels 200', a different design of the radiator unit 400', the additional gradient assembly 600, and corresponding valves and piping associating various components of the generator to one another.
  • the gradient assembly 600 and its utilization in the generator 1' will be described in detail with respect to Figs. 12A to 12D :
  • the piping of the generator are filled with work medium at a predetermined pressure, the work medium being at an intermediate temperature. Consequently, the pressure medium is also at the intermediate temperature.
  • the air conditioning unit AC begins its operation, heating up the work medium in the high reservoir 110' and cooling down the work medium in the low temperature reservoir 120'.
  • the intermediate reservoir 130' has working medium remaining at intermediate temperature.
  • Steps (a) to (d) then repeat themselves but in an opposite manner, i.e. high temperature work medium is now passed through the left pressure vessel 200L' and low temperature work medium is passed through the right pressure vessel 200R', and so on.
  • the first portion of the heated intermediate temperature work medium entering the gradient tank 600R is the hotter than the next portion of intermediate temperature work medium passing into the gradient tank 600R, and respectively, the first portion of the cooled intermediate temperature work medium entering the gradient tank 600L is the cooler than the next portion of intermediate temperature work medium passing into the gradient tank 600L.
  • This cross-over step provides for many advantages, one of which is a better heat transfer process with the pressure medium.
  • the pressure medium first performs a heat transfer process with intermediate temperature work medium at temperature T INTERMEDIATE (steps (b)(i) and (b)(ii)), and thereafter an additional heat transfer process with a heated/cooled intermediate temperature work medium (steps (c)(i) and (c)(ii)).
  • the intermediate temperature work medium contained in the gradient tanks 600R, 600L flows through lines L 5R , L 5L and L 5 into the radiator, where any accumulated heat of the generator can be removed via a heat transfer process with the outside environment.
  • the gradient tanks 600R, 600L are formed with a spiral structure 620R, 620L, configured for preventing the different portions of the heated/cooled intermediate work medium from performing a heat exchange process therebetween, and thus maintaining a temperature gradient within the reservoirs 600R, 600L.
  • FIG. 13A further piping arrangements of the generator are shown, in particular:
  • the low temperature reservoir 120' comprises a heat transfer element 124' configured for cooling the work medium in the reservoir 120' by constituting a condenser of the air conditioning unit AC.
  • the reservoir 120' further comprises a fan 128' driven by an external motor 126', configured for maintaining a uniform temperature within the reservoir 120'.
  • Figs. 14A to 14D the driving mechanism of the work medium and the cores of the pressure vessels 200R', 200L' will be described: It is observed that, whereas the previously described generator 1 only has one core 240 per vessel, the presently described generator 1' has six cores 240' per vessel, each having a design similar to that of the previously described core 240.
  • a motor 250' is provided, configured for driving a gear 254' meshing with a gear 256', which in turn drives a mutual gear 259', meshing with the respective gears 242' of each of the cores 240.
  • the gears 242' are responsible for the rotation of the drive screw (not shown) which propels the work medium through the entire generator piping system.
  • a secondary drive motor 260' configured for revolving the cores 240' the fan arrangement 220' of each of the cores 240' about the axis of the cores (it is noted that in some application, even the cores themselves can revolve about their axis).
  • the drive motor 260' is configured to be meshed with the mutual drive wheel 269', which, in turn, meshes with the gears 222' of the fan arrangement 220'.
  • the generator further comprises an additional array of driving motors 250', 260' located at a rear side of the generator, i.e. at the other end of the pressure vessels 200R', 200L'. In this manner, the driving load is distributed between the front array and the rear array of motors.
  • the drive screw used in the presently described generator can be of a different design, the difference lying in the pitch angle of the screw (70 deg.), which further contributes to circulation of the work medium through the core 240' and to pushing the work medium towards the inner surface of the core 240'.
  • a controller of the generator 1' is shown, generally designated as 700.
  • the controller 700 is positioned so as to interject between line L 0 exiting the pressure vessel 200' and line L 1 leading to the valve 140'.
  • the purpose of the controller 700 is to regulate the flow rate Q from the pressure vessel 200', by controlling the cross-sectional area through which the work medium is passed.
  • the controller 700 comprises a casing 720 formed with an inlet hole 722 in fluid communication with line L 0 , and an outlet hole 724 in fluid communication with line L 1 .
  • the controller 700 further comprises a plunger 740 formed with a top portion 742, a neck portion 744 and a main block 746.
  • the main block 746 is formed with a passageway 748, and a spring is mounted onto the neck portion 744, pressing against the casing, so as to bias the plunger 740 downwards.
  • the accumulator arrangement 590 is shown when used in the generator 1' described above.
  • the reservoir 590 has two lines L 10 leading thereto, one from each pressure vessel 200'.
  • the accumulator arrangement 590 further has lines Ln leading thereto from the rear side of the generator 1'.
  • the storage reservoirs also have an outlet line 592 leading to a user port (not shown).
  • the accumulator arrangement 590 may, as previously described, comprise a heating element therein, configured for heating up the work medium contained therein.
  • the accumulator arrangement 590 can be used to accumulate excess energy produced by the generator 1'. More specifically, any additional energy generated by the generator 1' (i.e. energy not consumed by a user) can be diverted to heating up the work medium contained in the accumulator arrangement 590.
  • the heated work medium of the accumulator arrangement 590 can later be used instead of the high temperature work medium produced in the high temperature reservoir 110' by the air conditioning unit AC, thereby saving on the power of the AC.
  • the pressure of the work medium in the accumulator arrangement 590 can be increased (greater than that required to the end user of line 592) so that the boiling point of the work medium increases, thereby allowing the work medium in the accumulator arrangement to absorb more energy.
  • FIG. 17A to 17D the valves and piping system of the generator 1' are displayed:
  • Fig. 17E a schematic chart of the temperature of the work medium passing through the core is shown, one for each of the pressure vessels 200R', 200L'.
  • the chart can be divided into the following sections:
  • step (b)(ii) instead of step (b)(i).
  • a vehicle is shown, generally designated as 800, in which a modified version of generator 1' is employed, generally designated as 1". It is observed that the containers of the work medium are disposed at the front F of the vehicle 800 while all the movement generating mechanisms are located at the rear R of the vehicle 800.
  • the pressure vessels 200' are disposed horizontally along the chassis 820 of the vehicle, connecting between the front F and the rear R.
  • the gradient tanks 600 are located on the same side f the pressure vessels 200' as the work medium reservoirs 110', 120' and 130'.
  • the disposition of the pressure vessels 200' provides the vehicle 800 with extra stability due to the weight of the pressure vessels 200'. It is also appreciated that since the vehicle 800 is usually in movement when the generator 1' is active, the efficiency of the operation of the radiator 400 can be considerably improved due to the increase in the heat transfer coefficient between the moving vehicle 800 and the ambient air.
  • a marine vessel generally designated 900 is shown comprising a modified version of the previously described generator 1', generally designated as 1"' .
  • the intermediate reservoir 130' is missing.
  • the generator 1"' uses the water it is submerged in as its main work medium, and therefore, the reservoir holding the water in which it is submerged (lake, ocean, pool) replaces the reservoir 130'.
  • two lines L 9 ' are provided, allowing the generator to withdraw water from the above medium into the generator 1"' .
  • FIGs. 20A and 20B there is shown a cross-section of a core of the pressure vessel 200' when without pressure and when pressure is applied thereto respectively. It is observed that the inner surface of the core is lined with an inner layer 1000 having an increased surface area due to micro-structures 1100 formed thereon. Increasing the surface area is desired in order to increase the heat transfer coefficient between the inner layer and the work medium flowing through the core.
  • Fig. 20C shows the core of the vessel 200' with the spiral 240' passing therein, configured for causing progression of the work medium through the pressure vessel 200' and the entire generator system 1.
  • a method for producing the inner layer including the following steps:
  • FIG. 20D and 20E another example of a core is shown generally designated as 240", which formed, both on its inner surface and on its outer surface, with ridges 246" and 247" respectively.
  • This core 240" can be made of tungsten or other materials (see Figs. 26A , 26B ), and its design provides for a more robust core 240".
  • ridges 246" and 247" are designed such that the peak of one is opposite the trough of another and vice versa, so that the thickness in each point along the central axis X is generally the same (N).
  • the ridges 246", 247" can be parallel as in the present example, or, alternatively, be in the form of one spiraling ridge (as in a thread).
  • One advantage of the latter example is the simplicity of production - the external ridges 247" can be made by turning and the internal ridges 246" can be formed by a tap.
  • FIGs. 22A and 22B still another example of the generator is shown, generally designated as 2000 which is generally similar in construction to the generator 1 previously described, but differs from it mainly by the design of the work medium sub-system 2100 (as opposed to the work medium sub-system 100).
  • the work medium subs-system 2100 is in the form of a cascade arrangement 2150 which comprises a high temperature reservoir 2110 and a low temperature reservoir 2120, without an intermediate work medium reservoir as in the previous examples.
  • Each of the pressure vessels 2200 R, 2200 L is provided at its inlet end with a respective inlet line 2136 R, 2136 L, regulated by respective valves 2140 B and 2140 A, and at its outlet end with a respective inlet line 2146 R, 2146 L, regulated by respective valves 2140 D and 2140 C.
  • An outlet end of the high temperature reservoir 2110 is connected to the valves 2140 B and 2140 A via respective lines 2134 R, 2134 L, and an inlet end of the high temperature reservoir 2110 is connected to the valves 2140 D and 2140 C via respective lines 2144 R, 2144 L.
  • An outlet end of the low temperature reservoir 2120 is connected to the valves 2140 B and 2140 A via respective lines 2132 R, 2132 L, and an inlet end of the low temperature reservoir 2120 is connected to the valves 2140 D and 2140 C via respective lines 2142 R, 2142 L.
  • the pressure fluid within the pressure vessel is at the temperature T ENV which is roughly the temperature of the environment.
  • steps (a) and (b) repeat themselves, with the difference being that the pressure fluid now constantly fluctuates between the temperatures T hot and T cold .
  • the heated low temperature work medium which is now at a temperature of T C-Heated > T C , is cooled down by performing a heat exchange process with the environment which is at a temperature T ENV ⁇ T C-Heated .
  • This process is regulated by a radiator unit 2400 (shown Figs. 22A , 22B ).
  • the cooled high temperature work medium which is now at a temperature of T H-Cooled ⁇ T H , is heated up by the A/C system, bringing it back to the temperature T H .
  • step (a) takes place in one pressure vessel (for example vessel 2200 R), the second pressure vessel 2200 L undergoes step (b).
  • the pressure vessels keep alternating - while the pressure fluid in one heats up, the pressure fluid in the other is cooled down and vice versa.
  • Figs. 23A to 23F the main difference in the design of the work medium sub-system 2100 is that the A/C previously used to provide the high/low temperature reservoirs at the respective condenser/evaporator sections of the A/C is now replaced by a cascade arrangement 2150, having several grades G 1 to G 7 , each operating as a basic A/C compression/expansion mechanism as will now be explained.
  • the arrangement is such that the cascade 2150 has a first end-grade G 1 which provides the 'low' for the low temperature reservoir 2120 and a second end-grade G 7 which provides the heat for the high temperature reservoir 2110.
  • Each of the grades G (n) comprises a compressor C (n) , a condenser section 2152 (n) , an expansion valve 2154 (n) , an evaporator section 2156 (n) and a return pipe 2158 (n) to the compressor C (n) , where (n) denotes the number of the grade G.
  • Each of the grades G 1 to G 7 comprises a compressible fluid (gas or liquid), and is designed to operate between a high fluid temperature T H(n) at the respective condenser section 2152 (n) and a low temperature T C(n) at the respective evaporator section 2156 (n) .
  • the arrangement is such that the condenser section 2152 (n) of one grade G (n) and the evaporator section 2156 (n) of a subsequent grade G (n+ 1 ) are thermally coupled to provide a heat exchange process.
  • the arrangement is of concentric tubes where the condenser section 2152 (n) is constituted by the inner tube and the evaporator section 2156 (n) is constituted by the outer tube.
  • compressed fluid from one grade G (n) flows within the inner tube and performs a heat exchange process with the expanded fluid from the subsequent grade G (n+ 1 ) which flows between the inner surface of the outer tube and the outer surface of the inner tube (see Fig. 23 E ).
  • the cascade arrangement 2150 is designed such that the temperature T C(n) of the fluid in the evaporator section 2156 (n) of one grade G (n) is lower than the condensation temperature of the fluid flowing in the subsequent grade G (n+ 1 ) , and necessarily lower than the temperature T H(n+ 1 ) of the fluid in the condenser section 2152 (n+ 1 ) of that grade G (n+ 1 ) .
  • T C(n) of the fluid in the evaporator section 2156 (n) of one grade G (n) is lower than the condensation temperature of the fluid flowing in the subsequent grade G (n+ 1 ) , and necessarily lower than the temperature T H(n+ 1 ) of the fluid in the condenser section 2152 (n+ 1 ) of that grade G (n+ 1 ) .
  • T C(n) , T H(n) and T COND are shown below: (n) T H(n) T C(n) T COND 1 27 0 2 57 27 30 3 90 57 60 4 11 6 90 93 5 15 5 11 6 11 9 6 19 7 15 5 15 8 7 24 5 19 7 20 0
  • the evaporator section 2156 1 of the first grade G 1 is submerged within the low temperature reservoir 2120 bringing the low temperature water to a temperature of about 3° C
  • the condenser section 2152 7 of the seventh grade is submerged within the high temperature reservoir 2110 bringing the high temperature water to a temperature of about 242° C. It is appreciated that the high/low temperatures of the high/low temperature reservoirs 2110, 2120 never reach the temperature of the respective condenser/evaporator sections 2152 7 , 2156 1 , and are always slightly lower/higher respectively.
  • the generator 2000 is fitted with a front and a rear driving motor 2250 F and 2250 R respectively configured for driving the cores of the pressure vessels 2200, and with a front and a rear driving motor 2260 F and 2260 R configured for driving the spiral for circulating the work medium within the generator 2000.
  • front and rear motors for driving the same element facilitates lower loads exerted on the revolved element (core or spiral) which are positioned within a high pressure environment. Should only one motor be used, the core and/or spiral will tend to bend within the pressure vessel, which can lead to damage of the mechanical integrity of the system.
  • the radiator unit 2400 is shown positioned along the lines 2146 R, 2146 L leading from the pressure vessels 2200 R, 2200 L to the low temperature reservoir 2120.
  • the purpose of the radiator unit 2400 is to provide for a heat exchange process between the heated low temperature water flowing in these lines (at a temperature of T C-Heated ) and the ambient air of the environment.
  • the radiator unit is fitted with a fan (not shown) and control unit (not shown) configured for regulating the operation of the fan, so that the low temperature water leaving the radiator remain essentially at a constant temperature. For example, if T C-Heated is about 50 °C, it is required to lower this temperature down to about 20 °C to allow the first grade G 1 to perform efficiently. Thus, the control unit is used to maintain the low temperature water leaving the radiator at a temperature of about 20 °C.
  • the control unit can comprise a sensor associated with line 2149 of the low temperature water emitted from the radiator and configured for measuring its temperature. Should this temperature exceed the predetermined temperature (in this particular example 20 °C), the control unit will cause the fan to revolve faster in order to increase the heat-exchange rate within the radiator unit 2400. Alternatively, should this temperature be lower than the predetermined temperature (in this particular example 20 °C), the control unit will cause the fan to revolve slower in order to decrease the heat-exchange rate within the radiator unit 2400.
  • the predetermined temperature in this particular example 20 °C
  • FIGs. 24A to 24D another example of a cascade arrangement is shown generally designated as 2150', and configured for adjusting its operation mode to the ambient temperature of the outside environment.
  • the ambient temperature of the environment increases to an extent when it exceeds the temperature of the compressed fluid in the condensation section 2152 2 of the second grade G 2 .
  • the low temperature water emitted from the radiator unit after performing a heat exchange process therewith will also be at a temperature exceeding that of the compressed fluid in the condensation section 2152 2 of the second grade G 2 .
  • the evaporator section 2156 1 of the first grade G 1 will be submerged in a very hot environment. Since each grade is fitted with a compressor of predetermined power and is design for a predetermined temperature difference ⁇ , the compressor C 1 simply will not be able to remove so much heat from the evaporator section 2156 1 rendering the operation of the first grade G 1 inefficient.
  • a bypass arrangement 2170 is used, configured to bypass the first grade G 1 and connect the low temperature reservoir 2120 with the evaporator of the second grade G 2 .
  • the bypass arrangement 2170 comprises two valves 2172 A , 2172 B associated with the evaporator section of the second grade G 2 and the compressor C 2 of the second grade respectively.
  • the bypass arrangement 2170 has an expansion valve 2174 leading to an evaporator section 2176 which is in the form of a tube leading into the low temperature reservoir 2120, and an outlet lien 2178 leading out of the low temperature reservoir 2120.
  • ports A 1 and B 1 are closed and ports A 2 and B 2 are open to allow the following: Compressed fluid from the condenser section 2152 2 of the second grade G 2 passes to the expansion valve 2174 allowing the fluid to expand and cool down. After passing through the expansion valve 2174, the expanded fluid progresses along the line 2176 to pass into the low temperature reservoir 2120 where it cools down the water and is emitted (slightly heated) through line 2178 leading to the compressor C 2 .
  • the temperature difference between the low temperature reservoir 2120 and the high temperature reservoir 2110 was about 240°C (between 3°C provided by the 0°C of the first grade evaporator 2156 1 and 242°C provided by the 242°C of the seventh grade condenser 2152 7 )
  • the temperature difference now is about 210°C between 30°C provided by the 27°C of the second grade evaporator 2156 2 and 242°C provided by the 242°C of the seventh grade condenser 2152 7 .
  • FIGs. 25A and 25B another example of a cascade arrangement is shown generally designated as 2150", which is similar to the previously described cascade arrangement 2150, with the difference being in that the flow of the fluids in the heat exchanger of each grade is now in opposite directions (as opposed to parallel flow in the previously described example).
  • compressed fluid of the first grade G 1 flows through its respective condenser section 2152 1 " in one direction, while expanded fluid of the second grade G 2 flows through its respective evaporator section 2156 2 " in the opposite direction.
  • counterflow heat exchangers provide for higher efficiency of the heat exchanger and consequently for a more efficient operation of the cascade arrangement 2150".
  • cascade arrangement 2150 is shown without a bypass arrangement 2170 (see Figs. 24A to 24D ) as in the previous example of cascade arrangement 2150', such a bypass arrangement 2170 can be fitted to the presently described cascade arrangement 2150".
  • FIG. 27A to 27E yet another example of a generator is shown, generally designated as 3000.
  • the structure of the generator 3000 is generally similar to that of the previously described generators, however, with the following differences:
  • a full cycle of one side of the generator can include the following steps (taking into account that the opposite side undergoes the same steps only at a shift):
  • steps (a) and (b), and (e) and (f) can last for a first period of time and steps (c) and (d), and (g) and (h) can last for a second period of time which is greater than the first period of time.
  • the second period of time can be twice as long as the first period of time.
  • the first period of time can be about 5 seconds and the second period of time can be about 10 secnods.
  • valve A is equivalent to valve B
  • valve C is equivalent to D
  • valve G is equivalent to H.
  • Valves E and F are not equivalent, and are each responsible for a different reservoir - valve E for the high temperature work medium reservoir and valve F for the intermediate temperature work medium reservoir.
  • the generator 3000 comprises four pressure vessels 3200, each comprising six cores C 1 through C 6 . It is also noted that the cores are inter-connected so as to form a single flow path. In particular, the cores are connected as follows:
  • Figs. 30A to 30C the generator 3000 is shown to have a middle-point feed, i.e. the work medium enters the pressure vessels at the area between two consecutive pressure vessels 3200 rather than at the front of the first pressure vessels 3200 as in the previously described examples. It is also observed that all four cores 3200 I to 3200 IV are inter-connected via pipes W 1-2 , W 2-3 and W 3-4 .
  • the line L RI is connected to the first core C 1 of the first pressure vessels 3200 I .
  • the flow path of the work medium is as follows:
  • Figs. 31A and 31B it is observed that the pressure vessels 3200 I to 3200 IV are also in fluid communication with one another, i.e. the pressure fluid within each one of these vessels is in fluid communication with the pressure fluid in the other vessels. Fluid communication is provided by high-pressure connectors P 1-2 , P 2-3 and P 4-1 .
  • One of the four pressure vessels is fitted with an outlet high-pressure connector P END , through which the high pressure medium is provided to the piston units 3270 R, 3270 L.
  • the generator 3000 is shown to comprise two gradient tanks 3600 L, 3600 R, each being in fluid communication with pressure vessels 3200 via appropriate piping.
  • each of the gradient tanks 3600 R, 3600 L is fitted with a corresponding valve H, G respectively, configured for providing the gradient tanks 3600 R, 3600 L with heated/cooled work medium as previously described with respect to steps (c) and (d) above.
  • Each of the gradient tanks 3600 L, 3600 R is of generally similar construction to the gradient tanks 600, 1600 and 2600 previously described.
  • it is formed with a flow labyrinth 3610 configured for maintaining a temperature difference between consecutive portions of work medium entering the gradient tank.
  • each of the gradient tanks 3600 R, 3600 L is connected at the top to a pipeline L GO , configured for allowing a medium contained within the gradient tank to be pushed out when work medium enters the gradient tanks via valves H and G.
  • an accumulator arrangement is disclosed generally designated as 3900, configured for storing some of the energy produced by the above generator.
  • the accumulator arrangement 3900 comprises a casing 3910 which contains a storing medium (not shown) configured for being heated by heating elements 3920 located within the casing 3910.
  • the heating elements 3920 are operated using some of the electrical power generated by the generator 3000, so as to heat the storing medium.
  • the storing medium within the casing 3910 is gradually heated to a temperature similar to that of the high temperature work medium within the high temperature reservoir 3110.
  • the valves A to G of the generator 3000 are selectively switched so that high temperature storing medium from the casing 3910 is circulated through the generator 3000 instead of high temperature work medium from the high temperature reservoir 3110, defining an auxiliary operation mode.
  • the generator 3000 operates in the auxiliary mode, the high temperature reservoir 3110 is circumvented by the piping as described above, and therefore does not take part in the operation of the generator 3000. This allows temporarily shutting down the A/C unit and thereby reducing overall power consumption of the generator 3000.
  • the A/C unit is in the form of a work medium sub-system 3100 having a condenser end 3112, an evaporator end 3122, a compressor arrangement CP and an expansion valve arrangement EV.
  • the evaporator end 3122 is exposed to the environment so as to be in thermal communication therewith and absorb heat therefrom.
  • the condenser end 3112 is located within a housing constituting the high temperature reservoir 3110 containing the high temperature work medium (not shown).
  • the compressor arrangement CP and the expansion valve arrangement EV are in fluid communication with both the condenser end 3112 and the evaporator end 3122, and operate to generate a standard cooling cycle in which a carrier medium (not shown) is compressed by the compressor arrangement CP, passes through the condenser end 3112 and expands via the expansion valve arrangement EV into the evaporator end 3122.
  • the compressor arrangement CP comprises four compressors ( CP 1 to CP 4 ), and the expansion valve arrangement EV comprises corresponding four expansion valves ( EV 1 to EV 4 ) , to form four working couplets CP 1 -EV 1 , CP 2 -EV 2 , CP 3 -EV 3 and CP 4 -EV 4 .
  • Each of the compressors CP 1 to CP 4 has a different power consumption and provides a different compression ratio, and each of the expansion valves EV 1 to EV 4 are respectively configured for providing a different expansion degree.
  • the arrangement is such that the work medium sub-system 3100 is operated by at least one couplet at a time, the couplet being chosen according to the required temperature difference between the high temperature reservoir and the cold temperature reservoir, and according to the temperature of the outside environment.
  • the CP-EV couplets can be configured for operation during specific times of day/year. More specifically, one couplet can be configured for operation during summer days, another for summer nights, a third for winder days and a fourth for winter nights, providing for a more efficient operation of the generator 3000.
  • the above arrangement provides at least three backup compressors when one of the four compressors malfunctions. For example, if the summer night compressor malfunctions, the winter day compressor can be used while the summer night compressor is being repaired.
  • a linear gear mechanism generally designated as 3300 is shown, replacing the previously described power assembly 300.
  • the linear gear 3300 comprises a housing 3310 within which a rack 3320 is configured for engagement with pinion arrangements 3340R, 3340L of the gear mechanism 3300.
  • Each of the ends 3310R, 3310L is formed with a corresponding opening 3312R, 3312L respectively, being in fluid communication with an auxiliary work medium pumped into and out of the housing 3310 during operation of the generator 300 owing to pressure changes in the pressure medium contained in the pressure vessels 3200 R, 3200 L.
  • the rack 3320 is caused to reciprocate under alternating pressure between a first end 3310R and a second end 3310L of the housing 3310.
  • each of the shafts 3342L, 3342R carrying the pinions 3348R, 3348L is also fitted with bearings 3345L, 3345R at both ends thereof, so that rotation of the pinions 3348R, 3348L is uni-directional only.
  • the shaft 3342R on which the pinion 3348R is mounted revolves about its axis, entailing revolution of the pinion 3348R.
  • the pinion 3348L itself remains stationary due to the bearing 3345L.
  • the pinion 3348L revolves while the pinion 3348R remains stationary.
  • the gear mechanism 3300 is provided with two delimiting rollers 3350R, 3350L, each being positioned in front of a respective pinion arrangement 3340L, 3340R respectively.
  • the rollers 3350R, 3350L are configured for engaging the rack so as to delimit its movement only to the axial direction.
  • Each of the delimiting rollers 3350R, 3350L comprises a shaft 3352 R, 3352 L respectively, on which a roller member 3356 R, 3356 L is mounted.
  • each end of the shaft 3352 R, 3352 L is fitted with bearings 3354 R, 3354 L respectively, which are similar to the bearings 3344 L, 3344 R of the pinion arrangements 3340R, 3340L.
  • the roller members 3356 R, 3356 L are engaged with a non-threaded portion 3322 of the rack 3320, so as to allow only axial movement thereof.
  • the drive shaft 3332 itself, is also provided with a bearing 3335, allowing it to freely rotate by inertia, even if the rack 3320 has already stopped reciprocating.
  • FIG. 36A to 36D yet another example of a generator is shown generally designated as 4000.
  • the generator 4000 is similar to the previously described generator 3000, however with several differences, some of which are as follows:
  • the generator 4000 comprises a work medium sub-system 4100, pressure vessels 4200, a generator assembly 4300, a radiator 4400, gradient tanks 4600L, 4600R and an accumulator arrangement 4900.
  • the generator 4000 comprises four core distribution arrangements 4140 L, 4140 R (two of each), each pressure vessel 4200 being fitted with a core distribution arrangement 4140 L, 4140 R at each end thereof.
  • each of the pressure vessels 4200 L, 4200 R comprises five cores 4220, and each of the valves 4140 L, 4140 R is connected to the cores 4220 via five distribution lines (e.g. L A 6 to L A 10 for the front end of the left pressure vessel 4200 L as shown in Fig. 37B ), and five corresponding regulator valves (e.g. A 6 to A 10 ).
  • each pressure vessel 4200 L, 4200 R are inter-connected to form a single flow path via connectors (e.g. L AC 7-8 and L AC 9 - 10 for the front end of the left pressure vessel 4200 L as shown in Fig. 37B and L DC 8-9 and L DC 10-6 for the rear end of the left pressure vessel 4200 L).
  • connectors e.g. L AC 7-8 and L AC 9 - 10 for the front end of the left pressure vessel 4200 L as shown in Fig. 37B and L DC 8-9 and L DC 10-6 for the rear end of the left pressure vessel 4200 L).
  • the distribution arrangements 4140 L, 4140 R and the regulator valves are design to allow selective parallel/linear flow through the cores 4220.
  • the cores 4200 can operate in parallel, i.e. unidirectional flow of work medium through all cores 4220 from one end of the pressure vessel 4200 to the other, or alternatively, form a single (and considerably long) flow path through which the work medium progresses.
  • the hottest portion of the intermediate work medium in the gradient tank 4600R can be about 40°C and the coldest portion of the intermediate work medium in the gradient tank 4600R (bottom of the tank) can be about 27.5°C.
  • the temperature of the pressure medium at this point can be about 30°C.
  • the work medium in the right gradient tank 4600R gradually heats the pressure medium in the left pressure vessel 4200 L while the intermediate work medium in the left gradient tank 4600 L (ranging between about 22.5°C to 10°C) gradually cools the pressure medium in the right pressure vessel 4200R to about 15°C.
  • line L HGL shown Fig. 37C
  • the coldest portion of the intermediate work medium in the gradient tank 4600R (top of the tank) can be about 10°C and the hottest portion of the intermediate work medium in the gradient tank 4600R (bottom of the tank) can be about 22.5°C.
  • the temperature of the pressure medium at this point can be about 20°C.
  • the work medium in the left gradient tank 4600L gradually heats the pressure medium in the right pressure vessel 4200R to about 35°C while the intermediate work medium in the right gradient tank 4600R (ranging between about 22.5°C to 10°C) gradually cools the pressure medium in the left pressure vessel 4200L to about 15°C.
  • high temperature work medium e.g. 50°C
  • Each of the above described six steps can last for a predetermined amount of time, e.g. five seconds. However, under other arrangements, it can be beneficial that each steps lasts for a different period of time.
  • a controller configured to monitor any one of the following:
  • the generator 4000 comprises a pressure system which is similar to that previously described with respect to the generator 3000.
  • Each pressure vessel 4200 L, 4200 R is fitted with a work piston 4270 L, 4270 R and a compensation piston 4280 L, 4280 R respectively.
  • Each of the work pistons 4270 L, 4270 R is attached via lines 4274 L, 4274 R to the housing of the gear mechanism 4300, so as to eventually cause reciprocation of the rack 4320 (shown Fig. 47 ) therein.
  • a work medium sub-system 4100 is shown being in the form of a heat pump which is generally similar to the sub-system 3100 previously described, with the difference being that it does not make use of four different compressors but rather a single screw compressor which can operate under varying compression ratios and power consumption, and being thus able to adjust its operation to the conditions of the environment.
  • the generator 4200 further comprises an accumulator arrangement 4900, which is similar in purpose to the accumulator arrangement 3900 previously described. However, it is observed that the accumulator arrangement 4900 comprises a high temperature compartment 4910 H and a low temperature compartment 4910 C , and is connected to an auxiliary heat pump 4930 of which the condenser end 4932 is located in the first compartment 4910 H and the evaporator end 4934 is located in the first compartment 4910 C .
  • each of the compartments 4910 H , 4910 C has a respective inlet GHI, GCI and outlet GHO, GCO, to which corresponding inlet and outlet lines L GHI , L GCI , L GHO , L GCO are attached respectively.
  • the outlet GHO is located at a top end of the compartment 4910 H
  • the inlet GHI is located at a bottom end of the compartment 4910 H
  • the outlet GCO is located at a bottom end of the compartment 4910 C
  • the inlet GCI is located at a top end of the compartment 4910 C .
  • the above arrangement allows for withdrawing high temperature work medium from a high temperature zone of the high temperature compartment 4910 H , and returning the work medium to a low temperature zone of the high temperature compartment 4910 H .
  • this arrangement allows withdrawing low temperature work medium from a low temperature zone of the low temperature compartment 4910 C , and returning the temperature work medium to a high temperature zone of the low temperature compartment 4910 C .
  • auxiliary heat pump 4930 instead of simple heaters (as in the previously described example), thereby providing not only an auxiliary high temperature reservoir at 4910 H , but also yielding a low temperature reservoir at 4910 C .
  • auxiliary work medium in the compartments 4910 H and 4910 C reaches temperatures which are similar to those of the high/low temperature reservoirs respectively, it can be used in operation of the generator while the main heat pump temporarily ceases its operation.
  • the high temperature compartment 4910 H is provided with heaters which are configured for directly heating the storage fluid contained within the compartment 4910 H . It is appreciated that during operation of the auxiliary heat pump 4930, the storage medium within the high/low temperature compartment can reach a heating/cooling limit (i.e. reaching a maximal/minimal temperature limit). In such an event, the operation of the auxiliary heat pump 4930 can be interrupted, and heater are then used to further heat the storage medium in the high temperature compartment 4910 H .
  • the work medium in the high temperature compartment 4910 H can be used as a high temperature work medium, while the work medium in the low temperature compartment 4910 C is used as the low/intermediate work medium.
  • the pressure vessel 4200 comprises and external housing 4222 accommodating therein the five cores 4220.
  • the pressure vessel 4200 is also provided with a sealing arrangement comprising seals 4242, 4244 and 4246, configured for preventing leaks from the pressure vessel 4200, and maintaining a high pressure of the pressure medium.
  • Each core 4220 is fitted, within the pressure vessel 4200 with a stirring assembly 4230, configured for revolving about the core 4220 for providing better mixing of the pressure medium and thereby a more efficient heat transfer between the pressure medium and the work medium flowing within the cores 4220 during operation of the generator 4200.
  • the stirring assemblies 4230 are generally similar to those previously described, and comprise a drive gear 4234 engaged with a center gear 4232 mounted on a central shaft 4235 and driven by an external motor.
  • support arrangements 4290 are provided along the pressure vessel 4200 configured for supporting the cores 4220.
  • these support arrangements 4290 comprise support discs 4293 formed with holes for receiving therethrough the cores 4220.
  • Each such support arrangement 4290 is also fitted with sealing members 4295, 4297 for preventing any undesired leakage.
  • Figs. 42A to 45C in which various examples of core structures are shown. It is noted that these examples show the structure of the front end of the core.
  • a core 4220' is shown comprising a core body 4221' and a central core cavity 4222' accommodating a static flow axle.
  • the first portion 4223' of the flow axle is smooth and does not occupy the entire cross-section of the cavity 4222'.
  • the core body 4221' at the front portion is formed with a roughened surface 4226' only on an inner side thereof.
  • the second portion 4224' of the flow axle is formed as a spiral occupying the entire cross-section of the cavity 4222'.
  • the core body 4221' at the second portion is formed with a roughened surface 4226' both on an inner and on an outer side thereof.
  • the flow axle is hollow and is formed with inner channels 4223 O .
  • the ridges formed with the roughened surface 4226' both on an inner and on an outer side thereof are aligned with one another, so that a peak of a ridge on the outer surface is aligned against a trough on the inner surface. This provides the core with a uniform thickness at any given cross-section taken perpendicular to an axis of the core.
  • the first portion of the core is located at the area of the seals 4242, 4244, 4246, thereby not taking place in the heat exchange process with the pressure medium. As such, it is not required to have the same structure as the second portion, and costs can be reduced by maintaining it in a simplified design as shown.
  • the roughened surface 4226' is in the form of teeth which do not extend completely radially from the center of the core. Rather, the teeth extend at a slight angle, so that the work medium flowing through the core 4220 is swirled by the direction of the teeth and penetrates in between the teeth, allowing for a better heat exchange process.
  • Fig. 43 Attention is now drawn to Fig. 43 , in which a core 4220" is shown having a similar design to that shown in Figs. 42A to 42E , with the difference being that the first portion of the core 4220" is isolated using an isolating sleeve 4227", so that work medium passing through the first portion doesn't waste its energy on heating/cooling that portion of the core which does not participate in the heat exchange process.
  • FIGs. 44A to 45C two additional cores 4220'" and 4220 IV are shown, being of similar design to that of the previously described cores 4220' and 4220" (similar elements have been designated with similar reference numerals with the addition of corresponding primes).
  • the main difference between the cores 4220" and 4220 IV and the previously describe cores lies in the design of the roughened surface, which is in the form of rings rather than in the form of conical/pyramidal protrusions. Such a design is slightly easier and less costly to manufacture.
  • Figs. 46A to 46D an assembly of the pressure vessel 4200 is shown. It can be observed that the cores 4220 and all the mechanical elements relating thereto (fan arrangements, gears, drive-shaft etc., herein 'core assembly ') are all enclosed by sleeve members 4200 S .
  • the sleeve members 4200 S are formed of a rigid material and have a sufficient thickness to provide mechanical support to the entire core assembly.
  • the sleeve member 4200 S can be made of steel and have a thickness of several millimeters.
  • the sleeve members 4200 S have a semi-circular cross section (i.e. have a half-pipe shape), and when two such members enclose a section of the core assembly, there remains a gap G therebetween (see Figs. 46C, 46D ).
  • the gap G provides fluid communication of the pressure medium between an inner zone defined between the sleeve members 4200 S and the core assembly, and an outer zone between the sleeve members 4200 S and casing 4222 of the pressure vessel 4200.
  • seal arrangement comprises seals 4244 which are essentially made of three separate pieces, and once inserted into the sleeve 4220 S and mounted onto the cores 4220, these are pressed closer to one another to provide the necessary seal for the pressure vessel 4200.
  • Fig. 47 an improvement of the gear mechanism 4300 is shown, in which the gear mechanism 4300 comprises roller-pin pinions 4348R, 4348L which are engaged with the rack 4320, and gears 3349R, 3349L which are engaged with the drive shaft 4332.
  • Roller-pin pinions 3348R, 3348L provide a much higher efficiency over regular gear engagement due to an increased contact surface and simplified teeth shape. In all other aspects, the gear mechanism 4300 operates much the same way.
  • roller-pin pinions 4348R, 4348L provide the gear with the advantage of reduced friction, since the roller-pin pinions 4348R, 4348L are free to revolve about their own axis.
  • FIGs. 48A to 48C another example of a work medium sub-system 4100' is shown in which each of the high/low temperature reservoirs 4110, 4120 respectively, has been divided into several compartments.
  • the compartments are in fluid communication with one another, yet they still delay mixing between the work medium exiting the sub-system 4100 towards the pressure vessels 4200 L, 4200 R, and work medium entering the sub-system 4100 after performing its heat exchange process.
  • Such an arrangement can provide a more efficient configuration of the generator.
  • a pressure vessel 4200' is shown having a length L which is much greater than the diameter D thereof.
  • the pressure vessel 4200' also comprises support assemblies 4920' as described previously with respect to Figs. 41A to 41D , however, contrary thereto, in the present example each core 4220' is not a single core, but rather is formed of core segments. Each two consecutive segments are adjoined with one another at the support assembly 4290' located therebetween.
  • an insert is introduced between the segments and is respectively received within the cores so as to provide fluid communication therebetween. It is also observed from Fig. 49B that the core segments are fully contained within the pressure vessel and that at the ends of the pressure vessel, only the inserts are protruding.
  • the insert 4299' itself can be made of a material not requiring high heat transfer coefficients, e.g. plastic.
  • the support assembly 4290' When adjoined at the support assembly 4290' by the insert, two consecutive core segments have a certain degree of freedom for movement with respect to one another.
  • the support assembly 4290' comprises bearings 4293' which allow the fan arrangements of the cores to freely revolve about themselves.
  • the bearings 4293' are of a self-aligning type, in which the housing 4294' of the bearing balls 4295' is of a curved shape, providing the cores, and the fan arrangements mounted thereon, with a certain, yet controllable, degree of freedom.
  • the support assembly 4290' is more clearly shown having the shape of a disc formed with several openings, corresponding in number to the number of the cores and the drive shaft DS.
  • Fig. 49H in which the sleeve member 4200 S ' is shown attached to the core assembly by bolts 4285 via an opening 4287. It is observed that the opening 4287 is not circular, but rather slightly prolonged. It should be understood that the enclosed core assembly is first introduced into the pressure vessel 4200', and only then is the pressure vessel pre-loaded with the high pressure (e.g. 6000 atm. (600 MPa)). Under such pressure, the pressure vessel may elongate slightly, and therefore the openings holding the bolts should provide for a certain degree of freedom. This arrangement holds true not only for bolts of the sleeve member 4200 S ' but for other bolted elements within the pressure vessel.
  • the high pressure e.g. 6000 atm. (600 MPa
  • an amount of heat of approx. 2.60 kWh is provided by the heat differential module and an amount of heat of approx. 1.80 is provided by the recovery arrangement, yielding the amount of heat of 4.40 kWh which is required for operation of the generator at a production of 1.32 kWh.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Thermotherapy And Cooling Therapy Devices (AREA)
EP11718789.8A 2010-04-15 2011-04-14 Generator Active EP2558689B1 (en)

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US39185010P 2010-10-11 2010-10-11
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US8800280B2 (en) 2010-04-15 2014-08-12 Gershon Machine Ltd. Generator
US9540963B2 (en) 2011-04-14 2017-01-10 Gershon Machine Ltd. Generator
JP5620567B1 (ja) * 2013-12-20 2014-11-05 石川　豊治 熱機関
NL2015638B9 (en) * 2015-10-20 2017-05-17 Niki Enerji Uretim A S A power generator and a method of generating power.
WO2017130010A2 (en) * 2016-01-26 2017-08-03 Spacevital Kft. Power production at low temperatures
CN108075686B (zh) * 2017-12-12 2019-06-07 华北电力大学 利用液体温差发电的系统及其发电方法

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US3830065A (en) * 1970-07-28 1974-08-20 Alister R Mc Vapor pressurized hydrostatic drive
GB1536437A (en) * 1975-08-12 1978-12-20 American Solar King Corp Conversion of thermal energy into mechanical energy
SU1516611A1 (ru) * 1987-04-13 1989-10-23 М.С. Лабинов Способ преобразовани тепловой энергии в гидравлическую
NL1004950C2 (nl) * 1997-01-08 1998-07-13 Cyclo Dynamics B V Werkwijze en inrichting voor het omzetten van warmte-energie in arbeid.
US7331180B2 (en) * 2004-03-12 2008-02-19 Marnoch Ian A Thermal conversion device and process
US20060059912A1 (en) * 2004-09-17 2006-03-23 Pat Romanelli Vapor pump power system
AT503734B1 (de) * 2006-06-01 2008-11-15 Int Innovations Ltd Verfahren zur umwandlung thermischer energie in mechanische arbeit
US20080236166A1 (en) 2007-04-02 2008-10-02 Walter Frederick Burrows Moderate Temperature Heat Conversion Process
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RU2434159C1 (ru) * 2010-03-17 2011-11-20 Александр Анатольевич Строганов Способ преобразования тепла в гидравлическую энергию и устройство для его осуществления

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CN102844529B (zh) 2016-08-03
CA2794348C (en) 2018-09-11
JP5890826B2 (ja) 2016-03-22
RU2604408C2 (ru) 2016-12-10
BR112012026138A2 (pt) 2017-07-18
RU2012140040A (ru) 2014-05-20
CA2794348A1 (en) 2011-10-20
JP2013524101A (ja) 2013-06-17
KR20130079335A (ko) 2013-07-10
CN102844529A (zh) 2012-12-26
EP2558689A2 (en) 2013-02-20
WO2011128898A3 (en) 2012-03-29
AU2011241835B2 (en) 2016-10-13
AU2011241835A1 (en) 2012-10-18

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