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Title:
DESIGNER RADIATOR AND PLANT FOR HEATING ENVIRONMENTS INCORPORATING SUCH A DESIGNER RADIATOR
Document Type and Number:
WIPO Patent Application WO/2020/104983
Kind Code:
A2
Abstract:
A designer radiator (50) for heating an environment comprises a container body, or casing, (55) having a tubular shape and defining a longitudinal housing (56) configured to be positioned along a substantially vertical direction and providing a first aperture (57) in a lower portion and a second aperture in an upper portion (58). The designer radiator (50) furthermore, comprises a condensing group (60) positioned within the longitudinal housing (56) and provides at least an inlet (61) for feeding the heat transfer fluid in the compressed gaseous state and at a predetermined initial temperature Ti, and at least an outlet (62) for discharging the heat transfer fluid once the same moves from the gaseous state to the liquid state by desuperheating and related transferring of a predetermined quantity of heat to the outside environment, thus generating of an airflow (150) arranged to move along the longitudinal housing (56) between the first and the second aperture (57, 58), and a following undercooling of the heat transfer fluid in the liquid state up to a determined exit temperature Tu, with Tu

Inventors:
VANNUCCI ROBERTO (IT)
Application Number:
PCT/IB2019/060018
Publication Date:
May 28, 2020
Filing Date:
November 21, 2019
Export Citation:
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Assignee:
VANNUCCI ROBERTO (IT)
International Classes:
F24D19/06; A47K10/06; F24F1/0003; F24F11/83; F28D1/04
Attorney, Agent or Firm:
DE MILATO, Francesco et al. (IT)
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Claims:
CLAIMS

1. A designer radiator (50) for heating an environment, said designer radiator (50) being characterized in that it comprises:

— a container body, or casing, (55) having a tubular shape and defining a longitudinal housing (56) configured to be positioned along a substantially vertical direction and providing a first aperture (57) in a lower portion, and a second aperture (58) in an upper portion;

— a condensing group (60) positioned within said longitudinal housing (56) and providing at least an inlet (61) for feeding said heat transfer fluid in the compressed gaseous state, and at a predetermined initial temperature Ti, and at least an outlet (62) for discharging said heat transfer fluid once that this has been moved from the gaseous state to the liquid state by desuperheating said heat transfer fluid in the gaseous state and related transferring of a predetermined quantity of heat to the outside environment, thus generating an airflow (150) arranged to move along said longitudinal housing (56) between said first and said second aperture (57,58), said condensing group (60) being, then, configured to cause said heat transfer fluid in the liquid state to undercool up to reach a predetermined exit temperature Tu, with Tu<Ti at which exits said longitudinal housing (56) through said outlet (62) .

2 . Designer radiator, according to claim 1, wherein said condensing group (60) comprises at least a finned pack heat exchanger (65) arranged, in use, to be passed through by said heat transfer fluid, said, or each finned pack heat exchanger (65) being constituted by a plurality of main ducts (68) that are connected each other by a plurality of connection ducts (69) and positioned within of a finned pack (70), and wherein at least two of said main ducts (68) are hydraulically connected through a secondary duct (78) positioned outside said finned pack (70) and protruding, in use, from said container body, or casing, (55) having a tubular shape, in such a way to form a support element.

3 . Designer radiator, according to claim 1, or 2, wherein said condensing group (60) comprises a plurality of finned pack heat exchangers ( 65a, ..., 65h) positioned one above the other within said longitudinal housing (56), each finned pack heat exchanger ( 65a, ..., 65h) providing a respective inlet ( 61a, ..., 61h) and a respective outlet ( 62a, ..., 62h) for said heat transfer fluid.

4 . Designer radiator, according to claim 3, wherein at least a finned pack heat exchanger of said plurality of finned pack heat exchangers ( 65a, ..., 65h) is positioned within said longitudinal housing (56) inclined at a predetermined angle (a) with respect to the horizontal direction, in such a way to increase the heat exchange surface for said airflow (150) which passes through said longitudinal housing (56) .

5 . Designer radiator, according to claim 3, wherein at least two finned pack heat exchangers of said plurality ( 65a, ..., 65h) are arranged inclined with respect to the horizontal direction, but in the opposite directions, i.e. respectively forming a first angle (a) and a second angle ( b ) .

6. Designer radiator, according to claim 5, wherein said second angle (b) and said first angle (a) have the same amplitude, i.e. b=-a.

7 . Designer radiator according to any claim 4 a 6, wherein said angle is comprised between 30° and 60°, in particular between 35° and 55°.

8. Designer radiator according to any claim 3 a 7, wherein at least two finned pack heat exchangers of said plurality ( 65a, ..., 65h) are connected in series by connecting an outlet of the finned pack heat exchanger arranged upstream, with respect to the advancing direction of said heat transfer fluid, with the inlet of the finned pack heat exchanger arranged downstream.

9 . Designer radiator according to any claim 3 a 7, wherein at least two finned pack heat exchangers of said plurality ( 65a, ..., 65h) are connected in parallel by connecting the outlet of the finned pack heat exchanger arranged upstream, with respect to the advancing direction of said heat transfer fluid, with the outlet of the finned pack heat exchanger arranged downstream, and the inlet of the finned pack heat exchanger arranged upstream with the inlet of the finned pack heat exchanger arranged downstream.

10 . Designer radiator, according to any of the previous claims, wherein at least a ventilation device (80) is, furthermore, provided positioned within said longitudinal housing (56) and configured to force said airflow (150) da said first aperture (57) a said second aperture (58) of said container body, or casing, (55) having a tubular shape.

11. Designer radiator, according to any of the previous claims, wherein a third aperture (59) is, furthermore, provided positioned between said first and said second aperture (58), said airflow (150) being arranged to pass through said longitudinal housing (56) of said container body, or casing, (55) between said third aperture (59) and said first and second apertures (57,58) .

12. Designer radiator, according to claim 11, wherein a first ventilation device (80a) is provided positioned within said longitudinal housing (56) and configured to force a first part (150a) of said airflow (150) between said third aperture (59) and said first aperture (57), and a second ventilation device (80b) positioned within said longitudinal housing (56) and configured to force a second part (150b) of said airflow (150) between said third aperture (59) and said second aperture (58) .

13. Designer radiator according to any claim 2 to 12, wherein a protection carter (75) is, furthermore, provided configured to cover said, or each, secondary duct (78) .

14. Designer radiator, according to claim 13, wherein said container body, or casing, (55) having a tubular shape provides at least an additional aperture (86) through which a part of said airflow (150) passing through said longitudinal housing (56) between said first aperture (57) and said second aperture (58) is arranged to exit said container body, or casing, (55) having a tubular shape .

15. Designer radiator, according to claim 14, wherein at least a flow directing flap (85) is, furthermore, provided associated to said additional aperture (86) configured to direct said part of said airflow (150), towards said, or each, secondary duct (78) .

16 . Designer radiator, according to claim 15, wherein said, or each, flow directing flap (85) is configured to move from a closing position, in which is arranged to close said additional aperture (86) and is not arranged to divert said airflow passing through said longitudinal housing (56) of said container body, or casing, (55) between said first and said second aperture (57,58), and an opening position of said additional aperture (86), in which said flow directing flap (85) is arranged to divert said determined part of said airflow (150) passing through said longitudinal housing (56) of said container body, or casing, (55) between said first and said second aperture (57,58) towards said, or each, secondary duct (78) .

17 . Designer radiator, according to any of the previous claims, wherein a heating group (160) is, furthermore provided positioned within said longitudinal housing (56) of said container body, or casing, having a tubular shape above, or below said condensing group (60), said heating group (160) providing at least an inlet (161) for feeding a determined flow of water at an initial temperature Ti produced by a boiler (180) and of at least an outlet (162) for discharging said flow of water at a final temperature T2, with T2<Ti, said heating group (160) being arranged to transfer a predetermined quantity of heat to said airflow which passes through said longitudinal housing (56) between said first aperture (57) and said second aperture (58) .

18. Designer radiator, according to any of the previous claims, wherein said exit temperature (Tu) of said heat transfer fluid in the liquid state, which is discharged from said condensing group (60) through said outlet (62), is less than a predetermined value DT of the saturation temperature at the pressure of exercise of said heat transfer fluid.

19. Designer radiator, according to claim 18, wherein said predetermined value DT is comprised between 4°C and 7°C.

20. Designer radiator, according to any of the previous claims, wherein said container body, or casing, (55) has a predetermined width (L) and a predetermined height (H) and wherein said predetermined width (L) is less than said predetermined height (H) .

21. Plant (100) for heating of environments providing a hydraulic circuit (1) comprising:

— an external unit (10) comprising a compressor (20) configured to compress said heat transfer fluid in the gaseous state to a predetermined pressure P*, and at least an evaporator (30) configured to cause said heat transfer fluid to move from the liquid state to the gaseous state;

— at least a designer radiator (50) according to any claim 1 to 7 arranged to be installed in a predetermined environment to be heated, wherein said inlet (61) of said condensing group (60) of said designer radiator (50) is hydraulically connected to said compressor (20) through a feeding branch (2), and said outlet (62) of said condensing group of said designer radiator (50) is hydraulically connected to said evaporator (30) through a return branch (3) .

22 . Plant for heating of environments, according to claim

21, wherein said return branch (3) is associated to a determination group (110) arranged to determine the undercooling value of said heat transfer fluid in the liquid state, and wherein a primary control unit (200) is provided configured to receive a corresponding undercooling signal from said determination group (110) and to adjust the electric power supplied to said compressor (20) in such a way to maintain, or to bring back, said determined undercooling value of said heat transfer fluid in the liquid state within a predetermined range of reference value.

23 . Plant for heating of environments, according to claim

22, wherein said hydraulic circuit (1) comprises a plurality of designer radiators (50a, 50b, 50c) each of which associated to a respective primary control unit (200a, 200b, 200c) and providing a respective condensing group ( 60a, 60b, 60c) hydraulically connected to a compressor (20) and to an evaporator (30) of a same external unit (10) through a respective sub-feeding branch (2a, 2b, 2c) hydraulically connected to said feeding branch (2) through a respective electro-valve ( 120a, 120b, 120c) arranged to move from an opening position, to a closing position, or vice versa and a respective sub-return branch (3a, 3b, 3c) hydraulically connected to said return branch (3), each said sub return branch (3a, 3b, 3c) being associated to a respective determination group (110) configured to determine the undercooling value of the heat transfer fluid in the liquid state, and wherein a secondary control unit (300) is, furthermore, provided configured to selectively open, or close, one, or more, of said electrovalves ( 120a, 120b, 120c) in said opening position, or in said closing position, in such a way to selectively feed said heat transfer fluid in the gaseous state to a determined number of condensing groups ( 60a, 60b, 60c) of said designer radiators ( 50a, 50b, 50c) for adjusting the undercooling value of said heat transfer fluid in the liquid state passing through said, or each, sub-return branch (3a, 3b, 3c) of said hydraulic circuit (1), if said, or each, primary control unit (200a, 200b, 200c) is not able to maintain, or bring back, said undercooling value of said heat transfer fluid in the liquid state within said predetermined range of reference value by adjusting said power of said compressor (20) .

Description:
DESIGNER RADIATOR AND PLANT FOR HEATING ENVIRONMENTS

INCORPORATING SUCH A DESIGNER RADIATOR

DESCRIPTION Field of the invention

The present invention relates to the heating plants and in particular it relates to an improved designer radiator for heating an environment as a room of a public, or private, building .

The invention, furthermore, relates to a plant for heating environments comprising the aforementioned designer radiator.

Background of the invention

As known a designer radiator is a particular typology of radiators that in addition to be able to heat the environments where they are installed with an efficiency that is equal to, or higher than the traditional radiators, have a modern design and, therefore, are able to meet the particular aesthetic needs of the users, increasingly looking for radiators that are real furnishing complements able to harmonize with the furnishing of the environment where they have to be installed. Furthermore, from the point of view of the materials, the designer radiators can be manufactured using materials that, with respect to the materials that are used for manufacturing the traditional radiators, have the advantage that allow to reduce encumbrance and to be shaped in order to obtain curved lines, which provides an additional value to the home furnishings . A designer radiator is commonly seen as an evolution of the traditional wall radiator. In fact, generally, a designer radiator has a body developing for a certain height and comprising a determined number of tubular elements. Furthermore, analogously to the traditional radiators, a designer radiator can use the convective motions due to the density difference between volumes of water at different temperatures, for heating the environment where it is installed. Therefore, in this type of designer radiator is necessary to have a boiler for producing hot water, normally at a temperature between 55°C and 65°C that has to be feed in the tubular elements of the designer radiator by connecting the same to the water network. Generally the thermal yield of a water radiator is about 1500 Watt, but the most expensive models can reach and in some cases overcome 3000 Watt.

Another typology of designer radiator, instead, provides the use of at least an electrical resistance and, therefore, needs to be connected to the electrical network. The power output of an electrical radiator is normally low with respect to the power output of a water radiator and seldom is able to overcome 300-350 Watt. Therefore, this typology of designer radiator is commonly used as a towel-warmer rather than for heating an environment even if small.

However, all the known typologies of radiators have a energy costs very high in order to be able to provide the heat that is sufficient to heat the environment where they are installed.

A further disadvantage is that, in order to have a high efficiency it is not possible to reduce, below a determined limit value, the size of the tubular elements forming the structure .

In light of the above, the radiators of prior art are, anyway, bulky and does not allow to achieve, with respect to the traditional radiators, economic and energy savings.

Summary of the invention

It is therefore an object of the present invention to provide an improved designer radiator that is able to overcome the aforementioned disadvantages of the designer radiators of the prior art.

It is also an object of the present invention to provide a plant for heating environments which comprises a similar designer radiator and that has a high effectiveness and advantageous from an economic point of view with respect to the heating plants of prior art.

These and other objects are achieved by a designer radiator, according to the invention, for heating environment, said designer radiator comprising:

— a container body, or casing, having a tubular shape and defining a longitudinal housing configured to be positioned along a substantially vertical direction and providing a first aperture in a lower portion and a second aperture in an upper portion;

— a condensing group positioned within said longitudinal housing between said first and said second aperture, said condensing group providing at least an inlet for feeding a heat transfer fluid in the compressed gaseous state and at a predetermined initial temperature Ti, and at least an outlet for discharging said heat transfer fluid once this has moved from the gaseous state to the liquid state by desuperheating said heat transfer fluid in the gaseous state and related transferring of a predetermined quantity of heat to the outside environment thus generating an airflow arranged to move along said housing from said first to said second aperture, said condensing group being configured to cause said heat transfer fluid in the liquid state to undercool up to a predetermined exit temperature Tu, with Tu<Ti at which said heat transfer fluid in the liquid state exits through said second outlet.

Other technical characteristics of the present invention and related embodiments are set out in the dependent claims.

In a preferred embodiment of the invention, the aforementioned condensing group comprises at least a finned pack heat exchanger passed through, in use, by the heat transfer fluid and comprising a plurality of main ducts connected in series, or in parallel, and positioned within a finned pack. More in detail, the main ducts are hydraulically connected in series, or in parallel, each other through a plurality of connection ducts.

According to an advantageous embodiment of the invention, at least two main ducts of said plurality can be hydraulically connected each other through at least a secondary duct positioned outside the finned pack and protruding, in use, from the covering having a tubular shape. In this way, the, or each, secondary duct is arranged to form a support element, in particular for towels, or clothes.

Preferably, a protection carter is provided arranged to cover said, or each, secondary duct. For example, the protection carter can be made of plastic, or metallic material, in case painted with the same color of the container body.

Advantageously, at least a ventilation device is, furthermore, provided positioned within the longitudinal housing and configured to force, advantageously to push, the airflow passing through the container body, or casing, and having a tubular shape, from the first aperture to the second aperture .

In particular, the container body, or casing, having a tubular shape can provide at least an additional aperture through which a part of the airflow which passes through the longitudinal housing from the first aperture to the second aperture is arranged to exit the container body, or casing, having a tubular shape, and wherein at least a flow directing flap is, furthermore, provided associated to the additional aperture and configured to direct the aforementioned part of airflow in a predetermined direction, in particular towards the, or each, secondary duct.

In particular, the, or each, flow directing flap can be configured to move from a closing position in which is arranged to close the aforementioned additional aperture and in which is not arranged to divert said airflow which passes through the container body, or casing, along a vertical direction, from the first aperture to the second aperture towards the, or each, secondary duct, and an opening position of the aforementioned additional aperture, in which is arranged to direct the aforementioned part of airflow towards the, or each, secondary duct.

According to another aspect of the invention, a plant for heating of environments comprises a hydraulic circuit constituted by:

— an external unit comprising a compressor configured to compress said heat transfer fluid in the gaseous state to a predetermined pressure P*, and of at least an evaporator configured to cause said heat transfer fluid to move from the liquid state to the gaseous state;

— at least a designer radiator, as described above, arranged to be installed in a predetermined environment to be heated, wherein said inlet of said condensing group of said designer radiator is hydraulically connected to said compressor through a feeding branch and wherein said outlet of said condensing group of said designer radiator is hydraulically connected to said evaporator through a return branch.

As known, the undercooling of the heat transfer fluid in the liquid state takes place when the liquid is cooled below the saturation temperature. Advantageously, according to the present invention, the temperature of the heat transfer fluid in the liquid state, which is discharged from the condensing group through the aforementioned outlet, is less than the saturation temperature at the pressure of exercise, of a predetermined value DT set between 4°C and 7°C.

In particular, the condensing group can comprise a plurality of finned pack heat exchangers positioned one above the other along the container body, or casing, having a tubular shape, each finned pack heat exchanger providing an inlet and an outlet for said heat transfer fluid. In a possible embodiment, a predetermined number of the aforementioned plurality of finned pack heat exchangers can be arranged in series by connecting the outlet of the heat exchanger arranged upstream to the inlet of the heat exchanger arranged downstream. Alternatively, a predetermined number of finned pack heat exchangers of the aforementioned plurality of finned pack heat exchangers can be arranged in parallel by connecting the inlet of the heat exchanger arranged upstream to the inlet of the heat exchanger arranged downstream, and the outlet of the heat exchanger arranged upstream to the outlet of the heat exchanger arranged downstream.

Advantageously, the return branch can be associated to a determination group configured to determine the value of undercooling of the heat transfer fluid in the liquid state, and wherein a control unit is provided configured to receive a corresponding undercooling signal da said determination group and to adjust the electric power supplied to the compressor if the value determined of undercooling of heat transfer fluid in the liquid state does not belong to a predetermined range of reference value. In other words if the detected undercooling condition does not correspond to the desired undercooling condition. For example, the range of reference value can be comprised between 4°C and 7°C below the saturation temperature of the heat transfer fluid in the liquid state.

In an embodiment of the invention, the hydraulic circuit comprises a plurality of designer radiators each of which provides a respective condensing group hydraulically connected to a compressor, through a respective sub-feeding branch providing a respective electro-valve to hydraulically connect, or alternatively disconnect, the corresponding sub- feeding branch with the feeding branch, and with an evaporator, through a respective sub-return branch, of the same external unit. In particular, each sub-return branch can be associated to a respective determination group of the undercooling value of the heat transfer fluid in the liquid state. More in particular, a secondary control unit is provided configured to selectively open, or close one, or more, of the aforementioned electrovalves in order to selectively feed the heat transfer fluid in the gaseous state to a determined number of designer radiators of the aforementioned plurality in such a way to adjust the undercooling value of the heat transfer fluid in the liquid state passing through the, or each, return branch, if the, or each, primary control unit is not able to maintain, or bring back, the undercooling value determined by the aforementioned determination groups within the aforementioned predetermined range of reference value by adjusting the power of the compressor. More in particular, the undercooling value can be measured as difference between the condensing temperature that is read on a manometer positioned in a point of the condensing group, the detected temperature by a temperature probe positioned downstream of the outlet of the heat transfer fluid in the liquid state dal designer radiator.

Advantageously, a heating group can be, furthermore, provided, in particular comprising at least a finned pack heat exchanger, arranged to be positioned within the longitudinal housing of the container body, or casing, having a tubular shape above or below the aforementioned condensing group. More precisely, the heating group provides at least an inlet for feeding a predetermined flow of hot water at a predetermined initial temperature Ti produced by a thermal group, as for example a boiler. The heating group furthermore provides at least an outlet for discharging the flow of water at a final temperature T2 that is less than the initial temperature Ti. More precisely, the hot airflow generated by the heating group can be used for heating the environment within which the designer radiator, according to the invention, is installed, in addition, or alternatively to the hot airflow generated by the condensing group.

According to another aspect of the invention, the container body, or casing, of the designer radiator provides a plurality of first apertures through which an airflow is arranged to enter the longitudinal housing. In particular, a plurality of walls can be provided positioned within the aforementioned longitudinal housing and arranged to define a determined path for the airflow passing through the longitudinal housing, between the aforementioned plurality of first apertures and the, or each, second aperture. For example, the aforementioned plurality of first apertures can be distributed along one, or more, of the lateral walls of the container body, or casing.

Brief description of the drawings

The invention will be now illustrated with the following description of an exemplary embodiment thereof, exemplifying but not limitative, with reference to the attached drawings wherein :

— Fig.l diagrammatically shows a longitudinal section of a first embodiment of an improved designer radiator, according to the invention, for heating environments;

— Fig.2 diagrammatically shows an enlargement in a partially sectioned view of a portion of the condensing group of the designer radiator of Fig.l in order to highlight some technical characteristics of the same;

— Figures 3 to 5 diagrammatically show a longitudinal section of some alternative embodiments of the improved designer radiator of figure 1;

— Fig.6 shows a perspective side elevational view of a further alternative embodiment of the designer radiator of figure 1;

— Fig.7 shows a perspective side elevational view of still another alternative embodiment of the designer radiator according to the invention, with a removed portion to show some components;

— Figures 8 and 9 show a perspective view of a further alternative embodiment according to the invention;

— Fig.lOA diagrammatically shows a first embodiment of a plant for heating environments, incorporating a designer radiator according to the invention;

— Fig.lOB diagrammatically shows a possible alternative embodiment of the plant of figure 10A;

— Fig.11 diagrammatically shows another alternative embodiment of the designer radiator according to the invention installed within a bathroom;

— Figures 12A to 12D diagrammatically show some possible alternative embodiments of the designer radiator according to the invention installed within a bathroom;

Figures 13A to 15B diagrammatically show some further alternative embodiments for the condensing group of the designer radiator according to the invention.

Description of preferred exemplary embodiments

With reference to figure 1, a designer radiator 50, according to the invention, for heating of environments, for example a bathroom, but also other rooms of a public, or private, building as a kitchen, or a bedroom, comprises a container body, or casing, 55 having a tubular shape and defining a longitudinal housing 56 configured to be positioned according to a substantially vertical direction. In particular, the container body, or casing, can have a predetermined width (L) and a predetermined height H. More in particular, the predetermined width L can be less than predetermined height H, advantageously less than half of the aforementioned predetermined height H. The container body 55, advantageously, provides a first aperture 57 arranged in a lower portion 55a, for example at the lower base, or of at least a lateral wall 55c, or 55d, and a second aperture 58 in a upper portion, for example at the top 55b, or at least at the lateral wall 55c, or 55d. The first and the second aperture 57 and 58 are arranged to put in communication the longitudinal housing 56 with the surrounding environment. A condensing group 60 is positioned within the longitudinal housing 56 providing at least an inlet 61 for feeding the heat transfer fluid in the compressed gaseous state and at a predetermined initial temperature Ti, and at least an outlet 62 for discharging the heat transfer fluid, once this has moved from the gaseous state to the liquid state due to a transfer of a predetermined quantity of heat to the outside environment. More in detail, the aforementioned transfer of heat to the outside environment genera an airflow 150 arranged to move along the longitudinal housing 56 from the first aperture 57 to the second aperture 58. In particular, the condensing group 60 is configured to cause the heat transfer fluid in the gaseous state to desuperheat in such a way to cause the heat transfer fluid to condense thus heating the airflow 150 which passes through the aforementioned housing 56. Once the heat transfer fluid has been condensed, the condensing group is, furthermore, configured to cause undercooling of the heat transfer fluid in the liquid state up to reach a determined exit temperature Tu, with Tu<Ti at which is discharged from the longitudinal housing 56 through the outlet 62.

As will be described in detail in the following with reference to figures 10A and 10B, the aforementioned designer radiator 50 can be installed within a plant 100 for heating environments. The plant 100 can comprise a hydraulic circuit 1 providing an external unit 10 arranged to be positioned in an outside area and comprising a compressor 20 configured to compress the aforementioned heat transfer fluid in the gaseous state to a predetermined pressure P*, and at least an evaporator 30 configured to cause the aforementioned heat transfer fluid to move from the liquid state to the gaseous state. Downstream of the evaporator 30 a device of expansion can be, advantageously, provided, for example a capillary valve 25, or a valve of expansion. Preferably, the external unit 10 can, furthermore, provide a fan 12 arranged to generate an airflow through an aperture 13 provided in the support body 15 of the external unit 10. It is to be noted that the heat transfer fluid is, advantageously, a refrigerant fluid of the kind that is normally used in the plants for conditioning environments, for example the refrigerant gas R32, or the refrigerant gas R410, etc. In particular, the inlet 61 of the condensing group 60 can be arranged to be connected to the compressor 20, through a feeding branch 2, and the outlet 62 with the evaporator 30 through a return branch 3. More in detail, the heat transfer fluid in the gaseous state compressed by the compressor 20 is fed, at a predetermined initial temperature Ti, to the condensing group 60 through the aforementioned feeding branch 2. The heat transfer fluid, after having passed through the condensing group 60 is, then, discharged from the longitudinal housing 56 through the outlet 62 and, then, sent to the evaporator 30 through the return branch 3, once this has been moved from the gaseous state to the liquid state due to the transfer of a predetermined quantity of heat to the outside environment. More in detail, the condensing group 60 is configured to cause, at first, the heat transfer fluid in the gaseous state to desuperheat and, once this has been completely condensed, the heat transfer fluid in the liquid state to undercool up to an exit temperature Tu<Ti. As above described, the transfer of heat from the heat transfer fluid passing through the condensing group 60 generates a hot airflow 150 which passes through the longitudinal housing 56 of the container body 55 between the first aperture 57 and the second aperture 58, advantageously from the first aperture 57 to the second aperture 58, through which exits the container body 55. The container body, or casing, 55, advantageously, provides apertures 51 and 52, that, in use, are respectively passed through the feeding branch 2 and the return branch 3 of the hydraulic circuit 1 of plant 100. Furthermore, the container body, or casing, 55 can provide at least a further aperture, that is not shown in figure for reasons of simplicity, for wiring the electronic card, which controls the designer radiator 50.

In the preferred embodiment of the invention, the condensing group 60 comprises at least a finned pack heat exchanger 65. More precisely, with reference to the scheme of figure 2, each finned pack heat exchanger 65 comprises a plurality of main ducts 68 connected in series and positioned within a finned pack 70, i.e. a series of lamellar elements which allow to maximize the heat exchange surface between the air of the surrounding environment and the heat transfer fluid passing in the main ducts 68. More in detail, the main ducts 68 are hydraulically connected in series through a plurality of connection ducts 69.

In a preferred embodiment of the invention, that is shown for example in figure 3, at least a ventilation device 80 is provided, in particular a fan, or a predetermined number of fans, for example 4 fans 80a-80d, configured to force the airflow 150 passing within the longitudinal housing 56 from the first aperture 57 to the second aperture 58 of the container body, or casing, 55 having a tubular shape. More in particular, the, or each, fan 80 can be a tangential fan. In the example that is shown in the figures 3 to 5 the, or each, fan is always shown near the first aperture 57, in particular arranged upstream of the same. However, the possibility is also provided that the, or each, fan 80 is arranged in another position, for example at, advantageously downstream of, the second outlet 58. As diagrammatically shown in the figures 4 and 5, the condensing group 60 can comprise a plurality of finned pack heat exchangers.

For example, in figure 4 the condensing group 60 provides 2 heat exchangers 65a and 65b positioned one above the other within the longitudinal housing 56 of the container body, or casing, 55 having a tubular shape. Each finned pack heat exchanger 65a, 65b provides a respective inlet 61a, 61b and a respective outlet 62a, 62b for the heat transfer fluid. In the example of figure 4, the inlet 61a of the finned pack heat exchanger 65a arranged upstream and the inlet 61b of the finned pack heat exchanger 65b arranged downstream are hydraulically connected one another by pipe fitting 63 to the feeding branch 2. Analogously, the outlets 62a and 62b of the aforementioned finned pack heat exchangers 65a and 65b can be hydraulically connected by a pipe fitting 64 to the return branch 3. Alternatively, or in combination to the aforementioned arrangement, the inlet and/or the outlet of each finned pack heat exchanger of the condensing group 60 can be directly connected, respectively, to the feeding branch 2, and to the return branch 3.

In the alternative embodiment of figure 5, 4 finned pack heat exchangers 65a-65d are provided positioned within the longitudinal housing 56. More in detail, in the example of figure 5, the first finned pack heat exchanger 65a is connected in series with the second finned pack heat exchanger 65b, i.e. the outlet 62a of the first finned pack heat exchanger 65a is connected to the inlet 61b of the second finned pack heat exchanger 65b, and the outlet of this latter is connected to the return branch 3. Analogously, the outlet 62c of the third finned pack heat exchanger 65c is connected in series with the inlet 61d of the fourth finned pack heat exchanger 65d and the outlet of this latter is connected to al return branch 3. The inlets 61a and 61d of the first and fourth finned pack heat exchangers 65a and 65d are connected to the feeding branch 2. It is to be noted that the scheme above described with reference to figure 5 has to be considered only one of the possible embodiments of the condensing group 60 of the designer radiator 50 that will be adapted to the different needs, in particular the available space and the volume of the room to be heated.

As diagrammatically shown in figure 6, in an embodiment of the invention, at least two main ducts 68a and 68b can be hydraulically connected through at least a secondary duct 78 positioned outside the finned pack 64. In particular, the, or each, secondary duct 78 can be substantially parallel to the main ducts 68. More in particular, the, or each, secondary duct 78 can be arranged, in use, to protrude from the container body 55 having a tubular shape, for example through holes 53a and 53b provided at the lateral surface 54 of the container body 50, in particular positioned at the front side of the lateral surface 54 same, in such a way to form a support element, for towels, or clothes, or similar articles. More in particular, a protection carter 75 is, advantageously provided arranged to cover the, or each, secondary duct 78. In the figures 8 and 9, the aforementioned support is shown at the front wall 55e of the designer radiator 50. Anyway, in a possible alternative embodiment of the invention that is not shown in the figure for reasons of simplicity, the designer radiator 50 can provide hooks, or support, for towels, or clothes, also, or only, at the lateral walls 55c, or 55d of the container body 55. For example, the aforementioned secondary duct 78 can have a portion protruding from at least a lateral wall 55c, or 55d.

In the example of figure 7, the secondary duct 78 is substantially "U"-shaped. Therefore, in this case with respect to the case of figure 6, the inlet of the main duct 68b arranged downstream is arranged on the same side of the outlet of the main duct arranged upstream 68a. In this case, furthermore, the first aperture 57 and the second aperture 58 are provided at the front side of the external surface 54 of the container body 50. Again in figure 7 the display 95 is diagrammatically shown with which the designer radiator 50 can be equipped with for displaying determined parameters, such as working temperature and pressure, or mode of working. These can be set, for example, by means of a remote control that is not shown in the figure for reasons of simplicity.

In a further embodiment that is diagrammatically shown in the figures 8 and 9, the container body, or casing, 55 can provide at least an additional aperture 86, advantageously at the front side of the lateral surface 54, through which a part of hot air passing through the longitudinal housing 56 is arranged to exit the container body 55. More in particular, as shown in the figures 8 and 9 a flow directing flap 85 can be, furthermore, provided configured to direct the aforementioned part of hot airflow 150 exiting the container body, or casing, 55 having a tubular shape through the additional aperture 86, towards the, or each, secondary duct 78. In this way, the heat that is directly transferred to the towel, or to the cloth, supported by the secondary duct 78 is highly increased, in order to speed up its drying.

More in particular, as diagrammatically shown in the figures 8 and 9, the flow directing flap 85 can be configured to move from a closing position (figure 8), in which closes the additional aperture 86 provided at the lateral surface 54 of the container body 55 and, therefore, is not arranged to divert the hot airflow 150 which passes through the longitudinal housing 56 of the first aperture 57 of the second aperture 57, and an opening position (figure 9), in which the flow directing flap 85 is arranged to open the additional aperture 86 and arranged inclined at a predetermined angle with respect to the aforementioned external surface 54, in such a way to divert the airflow 150 which passes through the longitudinal housing 56 of the container body, or casing, 55 for directing the same towards the secondary duct 78. In the case in which the designer radiator 50 provides supports for clothes, or towels at the lateral walls 55c and/or 55d, the aforementioned additional aperture 86 is, advantageously, provided at the same lateral wall 55c, and/or 55d.

As diagrammatically shown in figure 10A, the return branch 3 of the plant 100 within which one, or more, designer radiators 50 according to the invention are installed, can be associated to a determination group 110 configured to determine the undercooling value of the heat transfer fluid in the liquid state. For example, the determination group 110 can comprise a temperature probe 111 arranged to detect the temperature of the heat transfer fluid in the liquid state in a determined point of the return branch 3, and a measurement device for measuring the condensing temperature 112, preferably positioned at the condensing group 60. More in particular, a primary control unit 200 is provided configured to receive a corresponding undercooling signal from the aforementioned determination group and to adjust, i.e. increase, or decrease, the electric power supplied to the compressor 20, if the determined undercooling value, i.e. if the temperature of the heat transfer fluid in the liquid state, does not belong to a predetermined range of reference value Tmin-Tmax. More precisely, if the temperature of the heat transfer fluid in the liquid state belongs to the aforementioned range of reference value means that the undercooling value that is obtained does not correspond to the desired one, and, therefore, that the efficiency of plant 100 is not the highest efficiency that can be obtained. More precisely, if the temperature of the heat transfer fluid in the liquid state in the return branch 3 is higher, or less, than a predetermined undercooling value, the primary control unit 200 is arranged to adjust the number of turns of the compressor 20, in such a way that the electric power supplied to the compressor 20 is able to bring the undercooling value of the heat transfer fluid back within the aforementioned range of value. Still as diagrammatically shown in figure 10A, the return branch 3, or the feeding branch 2, can provide a one way valve 140. In this way, it is possible to use as external unit 10, a commercial external unit of the kind that is normally used for heat pumps.

In a particular alternative embodiment of the invention diagrammatically shown in figure 10B, the heating plant 100 comprises a plurality of designer radiators 50, for example 3 designer radiators 50a, 50b and 50c, each hydraulically connected to compressor 20 of the same external unit 10 through a respective sub-feeding branch 2a-2c and to the evaporator 30 of the external unit 10 same through a respective sub return branch 3a-3c. More precisely, each sub-feeding branch 2a, 2b, 2c provides a respective electro-valve 120a, 120b, 120c arranged to be positioned in an opening position, or in a closing position, in order to hydraulically connect, or disconnect, the feeding branch 2 with the respective sub feeding branch 2a-2c. In this case, each sub-return branch Sa le, advantageously, provides a respective determination group 110a, 110b, 110c arranged to determine the undercooling value of the heat transfer fluid in the liquid state and to send a corresponding signal to the primary control unit 200. Analogously to what has been described above for the plant 100 of figure 10A, each determination group of the undercooling value 110a, 110b, 110c can, for example, provide a temperature probe 111a, 111b, 111c arranged to detect the temperature of the heat transfer fluid in the liquid state at the outlet of the sub-return branch 3a, 3b, 3c, from the respective design radiator 50a, 50b, 50c, and a device for measuring the condensing temperature that is positioned at the respective condensing group 60a, 60b, 60c. Alternatively, each determination group of the undercooling value 110a, 110b, 110c can comprise the aforementioned temperature probe 111a, 111b, 111c at each sub-return branch 3a, 3b, 3c, and a respective device for measuring the pressure, that is not shown in the figure for reasons of simplicity, for measuring the pressure at, or anyway near, the point where the temperature is measured. In particular, from the measured pressure value, knowing the type of heat transfer fluid that has been used, it is possible to determine the condensing temperature, or this can be derived from temperature-pressure tables provided for each type of heat transfer fluid. More in detail, when a determination group 110a, 110b, 110c detects the undercooling value of the heat transfer fluid in the liquid state does not belong to the aforementioned predetermined range of value, the corresponding primary control unit 200a, 200b, or 200c, controls, at first, the possibility to overcome the drawback by adjusting the number of turns of the compressor 20, as described above with reference to figure 10A. If the result of the aforementioned control that is carried out by the primary control unit 200a, 200b, or 200c is negative, and, therefore, it is not possible to bring the undercooling back to a value comprised within the aforementioned predetermined range of value by adjusting the number of turns of the compressor 20, a secondary control unit 300 operates. This is configured to selectively open, or close, one, or more, of the aforementioned electrovalves 120a, 120b, 120c, i.e. to command the movement in the opening position, or in the closing position of the same, in order to selectively feed said heat transfer fluid in the gaseous state to a determined number of condensing groups 60a, 60b, 60c of the designer radiators 50a, 50b, 50c, in such a way to adjust the undercooling value of the heat transfer fluid in the liquid state passing through the, or each, sub-return branch 3a, 3b, 3c of the hydraulic circuit 1, thus assuring in this way that the temperature of the heat transfer fluid in the liquid state is comprised within a predetermined range of value T max eT min .

In general, if only a designer radiator, for example the designer radiator 50a, is fed, at the beginning, with the heat transfer fluid in the gaseous state, and, therefore, se solo the electro-valve 120a in opening position, and the undercooling value of the heat transfer fluid in the liquid state is less than the desired one, the secondary control unit 300 remains in a stand-by state, whilst the primary control unit 200a will change the number of turns of the compressor 20 as described above. Instead, if the undercooling value is higher than the aforementioned desired range of value, at first the primary control unit 200a operates, and if this is not enough, the secondary control unit 300 command the opening of one, or more, of the electrovalves 120a-120c by feeding one, or more, of the condensing groups 60b, 60c of the designer radiators 50b and 50c up to bring the undercooling value back within the predetermined range of value.

In the further embodiment that is diagrammatically shown in figure 11, within the longitudinal housing 56 of the container body, or casing, 55 having a tubular shape, above, or below of the condensing group 60, a heating group 160 is, advantageously, positioned. More in particular, the heating group 160, for example a finned pack heat exchanger, provides an inlet 161 for feeding a flow of water at a determined temperature Ti higher than the environment temperature, that is advantageously, produced by a boiler 180, and an outlet 162 for discharging a flow of water at an exit temperature It that is less than the entering temperature Ti. In this way, the designer radiator 50, according to the invention, can heat the environment where the same is installed, by operating alternatively, or at the same time, the condensing group 60 and the heating group 160. In the figures 12A to 12D, some possible embodiments of the designer radiator 50 according to the invention are diagrammatically shown arranged in a determined environment, in the case shown in the figure a bathroom. More precisely in the case of figure 12A, it is shown that it is possible to install the designer radiator 50 in such a way that the same is built-in, i.e. with the front side of the lateral surface 54 that is substantially flush with the surface 200 of the room where it is installed. Instead, in the alternative embodiment diagrammatically shown in figure 12B, the designer radiator 50 can be shaped as desired in order to provide substantially any design for the same, for example in figure 12B the designer radiator 50 has a curved shape at the top, i.e. at the portion where the second aperture 58 is provided through which the hot airflow 150 exits the housing 56 of the container body 55, in the example of figure 12C, instead, the designer radiator 50 has not a substantially prismatic shape, as in the case of figure 12A, but has a curved geometry, substantially half cylindrical. At last, in figure 12D a further embodiment of the designer radiator 50 is diagrammatically shown that provides a third aperture 59 through which, in use, the airflow 150, in particular, the airflow entering the longitudinal housing 56, passes and then exits hot from the apertures 57 and 58.

Therefore, as diagrammatically shown in particular in the figures 11 to 12D, it is possible to manufacture different designs of the designer radiator 50 in order to satisfy the need of space of the user, but also to meet the different aesthetic need of the client. At this regard it is to be noted that with the expression "casing having a tubular shape" that is used for describing the shape of the container body it is intended a hollow casing having a polygonal, or circular, or oval, cross section or a mixed geometry comprising straight and curvilinear segments.

In the figures 13A to 15B some further alternative embodiments are shown of the designer radiator 50 according to the invention. In particular, in the alternative embodiment of figure 13A, at least a finned pack heat exchanger of the plurality of heat exchangers, which form the condensing group 60, in the example of figure 13A, the heat exchanger 65c, is positioned inclined at a predetermined angle with respect to the horizontal direction. This constructive solution allows to increase the heat transfer surface with the airflow 150 which passes through the longitudinal housing 56 and, therefore, to optimize the heat exchange provided by dal designer radiator 50. Advantageously, angle has an amplitude set between 30° and 60°, in particular between 35° and 55°.

In the alternative embodiment that is diagrammatically shown in figure 13B, at least two finned pack heat exchangers of the aforementioned plurality, in figure the heat exchangers 65b and 65c, are arranged inclined with respect to the horizontal direction. More in particular, the heat exchangers 65b and 65c can be inclined in the opposite directions. In a possible embodiment, the first inclined heat exchanger 65b forms a first angle with the horizontal direction, whilst the second inclined heat exchanger 65b forms a second angle b with respect to the horizontal direction. The first and the second angles and b can have, in particular, the same amplitude, but opposite signs, i.e. b=- . As diagrammatically shown in the figures 14A and 14B, according to a further embodiment of the invention, all the heat exchangers of the condensing group 60, for example 6 heat exchangers 65a-65f (figure 14A) , or 8 heat exchangers 65a-65h (figure 14B) , positioned within the housing 56 can be provided inclined with respect to the horizontal direction. More precisely, the heat exchangers are alternately inclined at a first angle and at the second angle b, as described above with reference to the figures 13A and 13B. In particular, as diagrammatically shown in figure 14B, each couple 65a, 65b; 65c, 65d; 65e, 65f; and 65g, 65h, are connected in series. More in particular, the outlet 62a, 62c, 62e, and 62g of each heat exchanger arranged upstream 65a, 65c, 65e and 65g is connected to the inlet 61b, 61d, 61f and 61h of the respective heat exchanger 65b, 65d and 65f arranged downstream of the same, with respect to the advancing direction of the heat transfer fluid through the condensing group 60.

In the further alternative embodiments diagrammatically shown in figures 15A and 15B, the container body, or casing, 55 of the designer radiator 50 has a third aperture 59 provided between the first aperture 57 and the second aperture 58. In this case, the airflow 150 is arranged to pass through the container body, or casing, 55 between la third aperture 59 and la first aperture 57, and between la third aperture 59 and la second aperture 58. Advantageously, a first ventilation device 80a can be provided positioned within the longitudinal housing 56, preferably in the upper portion of the same, and configured to force a first part 150a of the airflow 150 between the third aperture 59 and the first aperture 57, and a second ventilation device 80b positioned within the longitudinal housing 56, preferably in the lower portion of the same, and configured to force a second part 150b of the airflow 150 between the third aperture 59 and the second aperture 58. In particular, the third aperture 59 can be associated to a grid 159 arranged to avoid that dust, or particles suspended in the air can enter the longitudinal housing 56 thus damaging the components that are housed within the same. Advantageously, the first outlet 57, that in this case is used for exiting the hot air from the designer radiator 50 is positioned on a side of the container body 55, in such a way that is possible to install the same on the floor of the room where it is arranged without compromising the correct functioning of the same.

It is to be noted that all the embodiments of the invention described above with reference to the figures 1 to 15B can be combined each other without modifying the inventive concept of the invention. In particular, the embodiment of the designer radiator 50 that is shown in figure 15B can provide at least a support for towels, or clothes, as diagrammatically shown in the figures 6 and 7, or the additional aperture 86 configured to direct a part of the airflow 150 in a predetermined direction, or both the components (figure 9) .

The foregoing description of a specific embodiment will so fully reveal the invention according to the conceptual point of view, so that others, by applying current knowledge, will be able to modify and/or adapt for various applications such an embodiment without further research and without parting from the invention, and it is therefore to be understood that such adaptations and modifications will have to be considered as equivalent to the specific embodiment. The means and the materials to realise the different functions described herein could have a different nature without, for this reason, departing from the field of the invention. It is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation.