The present invention is an innovative system for liquid heating, especially for the production of domestic hot water and/or for heating, for household and/or industrial use.
More precisely, the object of the present invention is an innovative system for liquid heating based on the so-called “cavitation principle” with a high efficiency and energy performance.
Therefore, the invention is included in the field of devices and systems for heating fluids, and in particular liquids.
More precisely, the present invention is applicable within the field of devices using rotating elements to generate heat in the liquid passing through them, such as the so-called “hydrosonic pumps”, also known as “hydrothermal turbine systems”, schematically shown in the example in
It is well known that “hydrosonic pumps” 2 for liquid heating were conceived and industrially developed in the late 1980s and early 1990s.
For this purpose, the aforementioned pumps 2, which can be crossed by a liquid to be heated, and generally water, include a perforated cylindrical “rotor” 23, i.e. equipped with a plurality of cavities 231, assembled with a rotation shaft 24, and a “stator” 22 within the mentioned rotor 23, the stator is able to rotate at high speed driven by an electric motor 21 (e.g. three-phase and powered indifferently by electric, solar, wind, pneumatic energy, etc.), it is connected and works together in a known procedure with said shaft 24.
The stator 22 is also a cylindrical body which includes a crimped inner surface and a pair of metal discs/covers 25 and 26 for the airtightly closing of its ends (from now on “end plates” or “closing flanges” 25, 26).
The rotor 23 and the stator 22, which constitute the so-called “turbine” 20 of the hydrosonic pump 2, are installed coaxially. They have a specifically dimension and diameter, so the gap or interspace between them can be filled and crossed by the liquid to be heated (more precisely, the gap between the internal crimped surface of the stator and the external surface of the rotor)
A specific pipe system connects the abovementioned hydrosonic pump 2 to a primary circuit 3, and in particular to at least one of its liquid storage 30, for the production of domestic hot water and/or to a secondary circuit 4 which includes, for example, a heat exchange unit to heat up a room (see
It is also useful, because the mentioned liquid storage 30 may be implemented to the level of the heat exchange unit, for example a plate unit or a coil unit.
Since the characteristics and the operating process of said hydrosonic pumps 2 are well known to the technicians of the sector, we will not go into a detailed description, instead we will refer for further details to document U.S. Pat. No. 5,188,090 A.
A prior art document disclosing a system for heating water for domestic purposes based on a cavitation turbine is KR 2011 0032112 A.
However, it is herein useful to point out that these machines heat the liquid mainly through the cavitational effect. It is well known that, this effect is based on the creation of areas or bubbles within the liquid that, due to variation of pressure blow up; during this process they release energy, and precisely heat, moreover the energy is absorbed by the liquid itself.
In other words, the heating of the cited hydrosonic pumps is achieved thanks to the very high turbulence of the liquid caused by the particular geometric and structural conformation of the rotor 23, and by its cooperation with the stator 22.
It has been experimentally found that, due to this turbulence, these hydrosonic pumps 2 are able to achieve a much higher efficiency than the traditional thermal generators, the ones generally used for the production of domestic hot water and/or for space heating (e.g., common household boilers).
However, performance obtained so far has not proved to be fully satisfactory, it is also due to the significant complexity of architecture of a hydrosonic pump 2 and due to the issues linked to it; this deficiency has negatively influenced its industrialisation and commercialisation.
For example, it has been highlighted that such a hydrosonic pump 2 for the production of domestic hot water and/or for space heating is able to reach its maximum efficiency only when the temperature of the input liquid inside the mentioned pump 2 is not “too far” (with respect to the quantity/flow rate of the circulating liquid) from the one of the same liquid output from the cited pump 2; indeed, under such conditions, the maximisation of the cavitational effect is ensured.
For this purpose, as extensively described with the previous Italian patent application No. 10201800006358, to which reference is made for further details, a specific mode of activation and management of the hydrosonic pump 2 is considered and implemented, the main purpose is to optimise and maximize the efficiency and performance. This mode, during the initial process of activation of the hydrosonic pump 2 (i.e. before reaching full operation), has a series of heating phases of the liquid, each phase is bound to another; in particular, during the first phase, the hydrosonic pump 2 is activated for a first rapid heating of the liquid loaded in it, moreover, during this phase, the circulation towards the primary circuit 3 is locked, as well as a subsequent phase where is passed between the hydrosonic pump 2 and the storage 30 of the primary circuit 3, once this has reached the desired temperature (see
These phases are repeated until the gradient between the inlet and outlet temperature of the in/out liquid of the abovementioned hydrosonic pump 2 matches or deflect from an optimal value that ensures the best and maximum energy performance. (As an alternative to this procedure of activation and management of the hydrosonic pump with repeated interruptions of the liquid flow, it would be possible to heat the liquid circulating in the hydrosonic pump 2 and the storage tank 30 of the primary circuit 3, but only as a whole, and much more slowly, with no benefit and less efficiency).
From what has just been said, it is clear the complexity of managing the hydrosonic pump 2 of the prior art, especially during the initial and temporary phases of the procedure, and also the difficulties related with the connection and cooperation with the primary and secondary circuits.
The achievement of optimal operating conditions and their retention take a long time to implement, it also causes a considerable delay in order to achieve full availability and operability of the liquid heating system for sanitary use and/or for indoor heating.
The results may also reflect an increase of the operating costs of the system itself.
The aim of the present invention is to delete the disadvantages of the known technique listed above, through an innovative system for liquid heating, and preferably for the production of domestic hot water and/or for space heating, and capable of achieving and ensuring maximum efficiency and energy performance quickly and in a simple and reliable manner.
These and other goals are achieved in accordance with the invention, its features are listed in the attached independent claim 1.
Further features of the present invention will be better evidenced in the following description of a preferred embodiment, and in accordance with the patent claims; it will be illustrated, for explanation only, in the attached drawing figures, wherein:
In order to describe the elements of the device according to the invention, it is useful to make reference to the attached figures. It should be noted that any dimensional and spatial word (such as “lower”, “upper”, “right”, “left” and the like) refers, unless it is differently specified, to the correct setting of the invention, as indicated in the drawings, and it does not necessarily correspond with the setting of the invention during working conditions.
In order to highlight certain features rather than others, what is shown on the attached drawings is not necessarily drawn to scale.
Furthermore, the elements illustrated on the drawings cannot be considered all essential to the invention; the ones which are essential are explicitly indicated. Moreover, like references will correspond to components of the system of the invention as those already described with reference to the state of the art.
As clearly shown in
According to the invention, of such a system
The system 1 of the present invention may further include a secondary circuit 4 (see
Henceforth, both the hydrosonic pump 2 and the optimizer 5 may also be referred to as “high efficiency cavitation boiler”.
The above-mentioned cavitation boiler may further include an expansion vase (which is not shown in the attached figures) which, as is well known, has the function of containing the volume increase of the liquid heating and the resulting pressure variations, it also avoids pressure surges and water hammer, otherwise they would be absorbed, by the system, and cause a potential damage.
The reciprocal connection between said pump 2 and said optimizer 5, included of the high-efficiency cavitation boiler, is ensured by respective flow 51 and return 50 pipes as shown in
It is also useful to specify that, for reasons which will be further clarified hereinafter, there are also flow and return pipes 31, 32 between said optimizer 5 and said storage tank 30 of the primary circuit 3; in particular, a flow pipe 31 from the optimizer 5 to the storage tank 30 and a return pipe 32 that, conversely, carries the liquid from the storage tank 30 back to the optimizer 5; otherwise a flow pipe 31 from the optimizer 5 to the heat exchanger 45 and a return pipe 32 that, conversely, carries the liquid from the heat exchanger 45 back to the optimizer 5.
The circulation of the liquid between the optimizer 5 and the primary circuit 3 can be ensured by at least one first pump 33 and its flow rate regulated by at least one suitable solenoid valve 34.
More precisely, the abovementioned solenoid valve 34 is able to interrupt and/or re-establish, in accordance with the detected temperature, the circulation of the liquid from the optimizer 5 towards the abovementioned primary circuit 3, and it is able to set its circulation temperature.
For this purpose, the solenoid valve 34 is linked to sensors and/or temperature probes 35 which are placed in correspondence with the hydrosonic pump 2 within the internal circuit 501 and along the outflow pipe 51 from the optimizer 5.
As clearly shown in
Optionally, a second circulation pump may also be provided within the cavitation boiler, it can ease liquid's flow to be heated between its cavitational turbine 20 and the optimizer 5.
As discussed in the following, the circulation within the cavitation boiler may take place directly through natural flow, without the aid of mechanical pushing devices.
In both cases a flow disconnector 8, see
The secondary circuit 4 has the function of dissipating heat generated by the high efficiency cavitation boiler, it consists of:
At least one circulation pump which ensures the flow of the abovementioned liquid within the secondary circuit 4.
It has been already partially explained that the cavitation boiler of the invention achieves its maximum energy performance and efficiency when the temperature of the liquid, which goes into the turbine 20 of the hydrosonic pump 2 to be heated, has a temperature “not far” (with reference to the amount of the circulating flow) from the one of the same liquid when it is heated and exits the hydrosonic pump 2. Under such conditions, the hydrosonic pump 2 does not suffer any thermal “shock”, and thus avoids any possible slowdowns or unfavourable conditions for liquid heating.
In other words, it has been observed that the cavitation boiler of the invention reaches maximum operating efficiency when the differential (or gradient) between the inlet and outlet temperatures of the liquid in/from the turbine 20 of the hydrosonic pump 2 is kept constant and equal to a value defined from now on as ΔTideal.
For this purpose, i.e. to manage the flow of the circulating liquid and keep the abovementioned ΔTideal, as an alternative to the storage 30 of the primary circuit 3 of the state of the art, it is envisaged to use a specific and dedicated inertial accumulation of the liquid treated in the hydrosonic pump 2 having a reduced volume and able to avoid the leakage of the heat already stored therein and to withstand fairly high pressures (in fact, during working conditions, the liquid can be at high temperatures a thus be in a vapour state if not circulated at a suitable pressure).
According to the invention, the abovementioned inertial storage is therefore a “small” storage, it corresponds with the optimizer 5 mentioned above.
Indeed, the optimizer 5 is arranged to allow the cavitation boiler (and in particular its cavitation turbine 20) to exchange heat with the primary circuit 3 and/or with the secondary circuit 4 without substantial variations of the abovementioned gradient ΔTideal (which is kept constant).
As previously highlighted, the ΔTideal is the gradient that ensures the maximum efficiency of the hydrosonic pump 2, it can be advantageously chosen as a fixed and optimal threshold, it can be set through probes or thermostats.
The experiments have shown that the abovementioned ΔTideal is a function of at least the delivery temperature of the hydrosonic pump 2 (or equivalently of the outlet temperature of its turbine 20), that is, it can increase as said temperature increases.
On the other hand, indicating by ΔToptimizer the temperature gap between the inlet and outlet liquid of the optimizer 5, it is desired that this gradient never falls below the aforementioned threshold ΔTideal, so the performance of the cavitation boiler can be maximized.
For this purpose, the aforesaid solenoid valve 34 (or technically equivalent means) “manages” the flow of the liquid, between the optimizer 5 and the primary circuit 3, as follows:
In other words, the abovementioned optimizer 5 works in order to keep the ΔToptimizer, on operating conditions, equal to ΔTideal.
Such operating mode of the system 1 of the invention will be discussed shortly in a more specific and detailed manner.
It will suffice herein, to repeat how the abovementioned optimizer 5 substantially behaves as a sort of “thermal flywheel”, thus, it allows the liquid heated by the hydrosonic pump 2 to transfer part of its heat to the primary circuit 3 and/or secondary circuit 4 without any substantial change or variations of the ΔToptimizer.
In other words, the abovementioned optimizer 5 is a device able to work between a first and a second operating temperature, wherein:
Generally, the first operating temperature is lower than the second operating temperature, indeed their gap defines the abovementioned ΔToptimizer.
According to the invention, the aforementioned optimizer 5 has a storage tank 52 with a lowered volume, but it is resistant to high pressures in order to allow a swift or a sudden heating.
More precisely, the aforementioned optimizer 5 has a capacity intermediate the traditional storages for liquids (generally the tanks have different volumes and they start from 20-30 litres, moreover they do not operate at high operating pressure) and a hydraulic compensator (it is well known to the skilled in the art and with a maximum volume between 2-3 litres, but it withstands at high operating pressure).
The optimizer 5 is thermally insulated in order to reduce the unavoidable heat losses of the liquid processed and contained within it; in other words, the insulation is able to reduce heat losses when the hydrosonic pump 2 stalls, it preserves high temperatures inside the tank 52 even for many consecutive hours.
In this respect, just by way of example and with no limiting intents, the tank 52 of the abovementioned optimizer 5 has a volume between 7 and 15 litres and it is able to withstand pressures of even more than 20 bar.
As clearly shown in the diagram of
Moreover, reference 53 in
The hydrosonic pump 2, its motor 21 and the optimizer 5 can be settled and placed side by side or stacked vertically on several levels on a frame (also known as a chassis or the housing of the cavity boiler).
The abovementioned chassis may also fit a control panel and a screen for the setting, as well as managing and displaying the other working and functional parameters of the system 1 of the invention and the related boiler.
Once finished to describe the liquid heating system 1 in all its technical and constructive aspects, we may now move on and describe specifically the optimisation procedure of the relatively high-efficiency cavitation boiler, this efficiency can be achieved thanks to the presence of at least the aforementioned optimizer 5.
Without any limiting purpose, it has been experimentally observed that the optimisation of the performance of the cavitation boiler can be achieved when the following working and/or temporary conditions are fulfilled:
This circulation between the accumulation 30 of the primary circuit 3 and the optimizer 5 inevitably leads to a lower temperature inside the optimizer 5 itself, up to measures far below the aforementioned turbine return temperature of 100° C.
It has been observed experimentally that this circulation leads to a drop of the return temperature up to 90-97° C.; therefore, under these conditions the thermostat sensor closes the solenoid valve 34, the one that was previously opened.
Once the ideally abovementioned return temperature of 100° is reached again, and thanks to the continuous flow of heated liquid between the optimizer 5 and the hydrosonic pump 2, the solenoid valve 34 starts again the circulation towards the primary circuit 3 and the circulation, so the heat exchange process is repeated.
The secondary circuit 4 for heat dispersion (as already discussed, the aforesaid radiators and/or exchangers inside the storage 30, etc.), can exchange heat with the storage tank 30, once the right temperature for the room “served” thereby has been reached, the secondary circuit will control the switching off or the stand-by of the high-efficiency cavitation boiler, through a special and specific thermostat, until the gradient ΔToptimizer and the ΔTideal have substantially the same value.
Just in case the secondary circuit needs more heat, the scheme 1 of the invention is able to supply it immediately, due to the fact that the ΔToptimizer has remained steady and equal to ΔTideal.
Therefore, the circulation between the optimizer 5 and the hydrosonic pump 2 is never stopped and the hydrosonic pump does not suffer from any thermal shock; consequently, the liquid heating, which can be used for hygienic purposes and/or for room heating, has a gradient ΔTideal and a temperature at the inlet and the outlet from/to the abovementioned hydrosonic pump 2 which is substantially steady, so the ideally temperature is:
During the time of practical implementation of the invention, various modifications and further changes are considered, because they all fall back into the same inventive concept; indeed, all the several components and details described above may also be replaced by technically equivalent elements.
In conclusion, the system for liquid heating, especially for the production of domestic hot water and/or for heating, and the relative method for optimising its energy performance and efficiency, have achieved its targets; in particular, it is possible to ensure high efficiency and performance by using mechanical components which have the following characteristics: they are simple to construct, economical and highly reliable; all this in a quick, easy and reliable manner.
Moreover, the system 1 of the invention is suitable for many other purposes; in fact, as well as its application for the production of domestic hot water for civil or industrial use and for space heating, it can be used, as a non exhaustive examples, for climatization, for the supply of hot water in household appliances (e.g., washing machines and dishwashers), for the supply of industrial machines (e.g., hot printing machines, and other), and heat pumps, etc.
Number | Date | Country | Kind |
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102020000013645 | Jun 2020 | IT | national |
Filing Document | Filing Date | Country | Kind |
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PCT/IB2021/054976 | 6/7/2021 | WO |