FLUID FLOW RATE"

D E S C R I P T I O N

TECHNICAL FIELD

The present invention relates to a valve for hydraulic control and balancing of fluid flow rate.

More particularly, the present invention refers to a new technical approach to a valve or hydraulic device for static control and dynamic balancing of the fluid flow rate in a conduit, particularly and in a non-limiting way, to the use in hydronic plants and thermotechnical plants for heating and cooling residential or industrial environments.

PRIOR ART

Valves for hydraulic control and balancing of a fluid flow rate, known also as PICVs (Pressure In- dependent Control Valves) are typically used in hy- draulic and thermotechnical applications in which the availability at the inlet of a constant flow rate of a liquid fluid, generally water, inde- pendently from the upstream and downstream fluid pressure variations, is required.

Said known types of valves for hydraulic con- trol and balancing of the flow rate enable a more versatile and simplified design and implementation of hydronic plants in which it is required to keep constant the flow rate of a fluid thermal carrier to the inlets of one or more users, such as for ex- ample heat exchangers, radiators, fan convectors or similar, independently from the fluid pressure con- ditions present upstream towards the thermal source and downstream towards the user circuit or in branches or sections thereof, in order to meet the design thermal requirements of each single user and in order to prevent thermal or fluid dynamic unbal- ances, energy waste and the use of further control devices .

A conventional example of a flow rate control valve is implemented by a simple ball shutter valve provided with a through opening. The rotating ball aligns or misaligns the ball opening with the valve inlet and outlet ports consequently varying the fluid passage cross-section between a minimum and maximum values,

A further example of valves for dynamic control and balancing of the fluid flow rate is described in the European patent EP 3 201 500 (B1 ) in the name of the same Applicant and regarding a valve comprising means for static control of the fluid flow rate configured to vary the cross-section of a passage port between the valve inlet and outlet and flow rate dynamic balancing means configured to regulate the flow rate of a fluid exiting the valve as a function of a flow rate variation of an enter- ing fluid. The dynamic balancing means comprise a perforated element interposed between the inlet port and am intermediate chamber in order to enable a fluid to flow only through at least one opening of the perforated element. Moreover, an elastic el- ement is placed at a face of the perforated element facing the fluid inlet port in the valve body so that an increase of the pressure difference between the valve inlet and outlet is matched by an en- largement of the elastic element in order to shrink the passage area of the perforated element opening and to ensure a constant flow rate .

Present small and large plants of thermotech- nical and hydronic, residential or industrial plants, can operate both for heating by piping to the user circuit plant a "hot" fluid thermal carri- er and for cooling by piping to the same circuit of the user plant a "cold" fluid thermal carrier, said hot and cold fluid thermal carriers being both sup- plied by different thermal sources. Generally, the alternate delivery of a hot fluid thermal carrier and cold fluid thermal carrier in circuits of hy- dronic plants combined for heating and cooling, known also as "four pipes" circuits, is typically switched by conventional multiway valves, typically "six way" valves (three plus three ways), config- ured to pipe and control inside the same circuit the fluid delivery and return, alternatively, be- tween a hot thermal source for heating or a cold thermal source for cooling, according to the re- quirements of a user.

Moreover, nowadays in many applications the circuits of some users or some sections of the same plants can be required to operate in a heating mode while other can be required to simultaneously oper- ate in a cooling mode. Using a six-way hydraulic valve installed at the ends of each user or (deliv- ery and return) circuit section of a plant enables to alternatively switch the same users or sections from the heating mode to the cooling mode and vi- ceversa, independent1y from each other.

Some examples of multi-way diverter valves used in the state of the art are the known six ways valves obtained for example by combining two con- ventional three ways diverter valves generally used in the "four pipes" plants for managing a same area with two distinct thermal sources.

A typical example of multiway diverter valves is described in the Italian patent application IT 201700010534 in the name of the same Applicant and regarding a multiway valve comprising a valve body with a first and second diverter valves cooperating with each other and each provided with a first and second diverter members and with a triad of opening orifices in the valve body, wherein said multiway valve comprises a tubular cartridge integrating said first and second diverter member. The tubular cartridge is housed inside the valve body and can be displaced inside the valve body and is provided with command members for causing said displacement .

Other examples of these types of multiway di- verter valves are described in the following prior art documents US 2011/0303863 (A1) , CN 2402891 (Y) and CN 103133444 (A) .

The above-mentioned cited known control- balancing valves, or PICVs, have however disad- vantages and operating limitations, particularly when they are used in combined circuits and hydron- ic plants for heating and cooling, provided with diverter valves. A serious drawback of these cited types of con- trol/balancing valves, particularly in combined heating-cooling hydronic plants, is due to the size thereof and to the lack of room available for mounting them, and due to the fact that in both the delivery-return connecting manifolds of the user and the diverter valve connecting manifolds, there is a great number of hydraulic connecting conduits and pipes which must be often arranged and placed in small and narrow spaces, such as cassettes or junction boxes. Particularly, in plants made and configured to already existing buildings and hous- es, rooms are further cramped or unavailable.

A further typical limit and drawback of con- ventional combined heating-cooling hydronic plants provided with diverter multi-way valves is due on that nominal flow rates of the fluid thermal carri- er required by the user in heating mode are gener- ally different from flow rates in cooling mode, consequently it is required to use flow rate con- trol means or valves configured to change the amount of the fluid thermal carrier flow entering the diverter valve, depending on whether flow comes from a hot or a cold source.

Therefore, it is extremely difficult for an op- erator to have enough rooms in which easily install said conventional valves for hydraulic control and balancing of the flow rate and for connecting them to conduits and delivery manifolds at the inlet of the diverter valve from different thermal sources.

Moreover, it is also difficult or even impossi- ble to ensure the further handling room or conven- ience required to actuate the control/balancing valve itself, both if it's of a manual type by means of a lever, knob, wheel or tap, or it's of an automatic type by means of electric or electrome- chanical actuators or servomechanisms; therefore, even though it were possible to physically install a valve, the required room for manual handling or housing of remotely controlled electromechanical actuators or servomechanisms, will be still cramped or uncomfortable.

Still, a further limit of the conventional con- trol balancing valves, is due to the fact that said handling room or convenience and space for housing an actuator or servomechanism increase proportion- ally to the fluid passage cross-section of the valve itself. Indeed, as the valve size increases also the lever or hand command element configured to apply the torque required to move the shutter increases, otherwise the size and dimension of the analogous mechanical or electromechanical servo- mechanism have to be increased in order to generate the torque required to maneuver the shutter itself. Moreover, a further drawback of small-sized and ge- ometrically simple dynamic balancing valves which are not provided with membranes or other types of means configured to measure inlet and outlet pres- sure, is due to the fact that they regulate the fluid flow rate generally only as a function of the inlet momentum applied to regulating members in- stead of control the flow rate also as a function of the fluid pressure difference between the valve inlet and outlet ports.

A still further limit of the conventional con- trol balancing valves is due to their low ratio of the fluid passage cross-section to the outer size of the valve, and due to the fact that the presence of inner members, their size and sudden changes of direction they impose to the fluid, limits the out- let maximum flow rate so that an user is forced to choose larger valves.

The required provision of different control of the nominal flow rate of a fluid thermal carrier supplied from different sources to the diverter valve, an essential feature for securing the planned thermal exchange inside the user circuit, is typically met, in the presence of narrow rooms, by using of calibrated washers provided on pipe connecting manifolds, on the delivery openings ori- fices of the diverter valves. Said washers are pro- vided with a calibrated sized central hole in order to generate a concentrated head loss of the flow which, under designed nominal pressure conditions, ensures the required nominal fluid flow rate.

This conventional technical approach, despite being suitable in installation narrow rooms and volumes, has also limits and drawbacks because nor it makes possible further regulating due, for exam- ple, to changed conditions of a user plant after modifications or expansion, neither enables an op- erator to visually check the calibrated diameter of a beforehand installed washer.

Indeed, in up-to-date engineering type imple- mentations, it is sought the capability of a plant to be easily adaptable and modifiable as a function of changed needs of a user, for example caused by future extensions or modifications, which is not possible in the above cited examples except for disconnecting, disassembling or opening the mani- folds, connecting conduits between the ports of the diverter valve for replacing or recalibrating of control means, such as calibrated washers, such op- eration, besides being disadvantageous and uncom- fortable, entails costs and the requirement of a skilled technical operator.

OBJECTS OF THE INVENTION

An object of the present invention consists of overcoming, at least partially, the operative draw- backs and limits of the above discussed prior art. More specifically, object of the present invention consists of providing to an operator a valve for hydraulic control and balancing of fluid flow rate capable of being installed in extremely narrow rooms, typically cabinets or general manifold boxes provided with a high number of interconnected pipes or conduits.

A further object of the invention consists of providing a valve for hydraulic control and balanc- ing of fluid flow rate which can be easily ar- ranged, adjustable, and manoeuvrable by an operator in extremely narrow rooms typical of cabinets and manifold general boxes containing a high number of interconnecting pipes or conduits, without using levers, taps, wheels or other handling servomecha- nisms outside the body of the valve itself.

A further object of the invention consists of providing a valve for hydraulic control and balanc- ing of fluid flow rate , capable of being easily arranged and adaptably paired with a multiway di- verter valve or capable of being associated to al- ready existent plants.

Last but not least object of the present inven- tion is to provide a small-sized valve, a multiway diverter valve assembly or a six-way valve simulta- neously allowing hydraulic independent control and/or balancing of fluid flow rate at inlet or outlet ports.

A still further object of the present invention consists of providing an operator a valve for dy- namically balancing a flow rate capable to control a fluid flow rate as a function of the momentum of the entering fluid and also as a function of the pressure difference between the valve inlet port and outlet port.

A still further object of the present invention consists of providing to an operator a valve for control and balancing of fluid flow rate having a greater ratio between the fluid passage cross- section and therefore the flow rate and the exter- nal size of the valve.

Lastly, a further object of the present inven- tion consists of providing a valve for hydraulic control and balancing of fluid flow rate capable of ensuring a high level of strength and reliability in the long term, and such to be easily and econom- ically manufacturable.

These and other objects are met by the valve for hydraulic control and balancing of fluid flow rate object of the present invention according to the independent claim.

The structural and functional characteristics of the valve for hydraulic control and balancing of fluid flow rate can be better understood from the following detailed description in which it is made reference to the attached drawings representing some preferred non-limiting embodiments, wherein:

BRIEF DESCRIPTION OF THE FIGURES

Figure 1 is a schematic illustration of an axo- nometric view of a first simplified embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention, clearly showing the manual regulating control step performed by an operator acting on the outer sur- face of the shutter through an opening made in the valve body;

Figure 2 is a schematic illustration of a fur- ther axonometric view, from a different point of view, of a first embodiment of the valve for hy- draulic control and balancing of fluid flow rate object of the present invention;

Figure 3 is a schematic illustration of an ex- ploded axonometric view of the first embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention;

Figure 4 is a schematic representation of an axonometric view of a second embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention, clearly showing the manual regulating control step per- formed by an operator acting on the external sur- face of the shutter through an opening made on the valve body;

Figure 5 is a schematic illustration of a fur- ther axonometric view, from a different point of view, of a second embodiment of the valve for hy- draulic control and balancing of fluid flow rate object of the present invention;

Figure 6 is a schematic illustration of an ex- ploded axonometric view of the second embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention;

Figures 7 and 8 are schematic illustrations re- spectively of a front view and lateral view of the first embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the pre- sent invention;

Figures 9 and 10 are schematic illustrations respectively of a longitudinal cross-section view along the plane B-B in Figure 7 and of a longitudi- nal cross-section view along the plane A-A of Fig- ure 9 of the first embodiment of the valve for hy- draulic control and balancing of fluid flow rate object of the present invention;

Figures 11 and 12 are schematic illustrations respectively of a front view and lateral view of the second embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention;

Figures 13 and 14 are schematic illustrations respectively of a longitudinal cross-section view along the plane B-B of Figure 11 and a longitudinal cross-section view along the plane A-A of Figure 13 of the second embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention;

Figure 15 is a schematic illustration of a front view of a known multiway hydraulic diverter valve provided with two valves for hydraulic con- trol and balancing of fluid flow rate object of the present invention, disposed on the inlet openings from thermal sources;

DE TAILED DESCRIPTION OF THE INVENTION

With preliminary reference to Figures from 1 to 3, and particularly to Figures from 7 to 10, which show a first simplified embodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention, indicated by 10, and only suitable to statically control or pre- regulate fluid flow rate.

Moreover, it is made reference to Figures from 4 to 6 and from 11 to 14, which show a second em- bodiment of the valve for hydraulic control and balancing of fluid flow rate object of the present invention, generally indicated by 10' and both con- figured to statically control or pre-regulate and dynamically balance a fluid flow rate.

Said valves 10, 10' comprise:

a body 12 generally having a substantially tubular cylindrical shape provided with an inlet opening 14, outlet opening 14' disposed at the ends of said body 12 and having at least one actuating opening 16 radially formed on the body 12 itself;

a hollow rotating shutter 20 rotatively housed inside said body 12, with respect to a rota- tion axis 11, said rotating shutter 20 being con- figured to be crossed by a fluid and to rotatively change the passage cross-section of a fluid inside the body 12 itself of the valve 10, 10' .

Referring in particular to Figures 9 and 10 and 13 and 14, the valve 10, 10' comprises the novel characteristics of a rotating shutter 20 having a glass or cup shape comprising at least one first opening 22', developing along the rotation axis 11 of said rotating shutter 20 and eccentric to the same rotation axis 11, said first opening 22' coop- eratively rotating with at least one mated second opening 15' , eccentric to the same rotation axis 11 of the rotating shutter 20, said second opening 15' being formed on an inner wall 15 of said body 12, so that a rotation of said first opening 22' with respect to said second opening 15' is matched by a variation of the fluid passage cross-section. Said rotating shutter 20 is configured to be further di- rectly manually rotatively actuated, inside said body 12, by the exposed diametral surface thereof, through said actuating opening 16, so that a rota- tion of said first opening 22' with respect to said second opening 15' is matched by a variation of the fluid passage cross-section in a direction substan- tially coinciding with the rotation axis 11 of the same rotating shutter 20.

Still referring to the preferred embodiment in the figures, the body 12 can advantageously com- prise two actuating openings 16 radially and diame- trally formed oppositely to each other, so that it is possible to easily gain access to diametrally opposite portions of the outer diametral surface of the rotating shutter 20 from the outside of the body 12 so that an operator will be capable of gripping the rotating shutter 20 by his/her two op- posite fingers.

The first opening 22' is through and can be shaped in a different way and is formed on a bottom wall 22 of said rotating shutter 20, said shutter rotatively facing to seatback against said inner wall 15 of the body 12.

The second mated opening 15' is also through and can be differently shaped, preferably coincid- ing with a first opening 22. The number of said first and second openings 22 and 15' can be more than one, as in the embodiments shown in Figures 3 and 6 and they enable by rotating the first with respect to the second, by to the rotation of the rotating shutter 20, to alternatively increase or decrease the fluid passage cross-section.

Said inner wall 15 can be made and formed di- rectly in the body 12 or can be advantageously de- fined by a perforated disk-shaped element removably housed inside the body 12. Said inner wall 15 can be further provided with at least one lobed portion 17 mated to a corresponding mated recess formed in- side the body 12, said lobed portion 17 being such to prevent the same inner wall 15 from rotating and to hold the second opening 15' in a stationary po- sition with respect to the first rotatively mated opening 22' of the rotating shutter 20.

Said body 12 and said rotating shutter 20 are preferably made of a metal material, typically, copper alloys or iron alloys, however, can be also advantageously made of plastic polymeric materials and thermoplastic materials, or of materials ob- tained by sinterizing metal or ceramic powders or of materials obtained by additive manufacturing processes . The body 12 can be also preferably provided, at its ends, with known connecting means 24, 24' con- figured to connect the valve 10 to conventional el- ements for connecting pipes and conduits, such as for example threads, connectors, fittings or equiv- alent, both of a male and female types.

Advantageously, one or more clamping profiles 25, such as collars or hex key profiles configured to be mated with conventional assembling hex keys and tools, can be also further made on the outer surface of the body 12.

The rotating shutter 20 can be advantageously provided with an irregular surface portion 26 formed on an annular portion of the outer surface itself and exposed through the actuating opening 16 of the body 12, for example obtained by knurling the metal surface and configured to easily enable an operator to manually actuate it.

Referring particularly only to Figures 8 and 12, advantageously said rotating shutter 20 can be also provided with a graduated scale 27 formed again on an exposed annular portion of the outer surface thereof at the actuating opening 16 of the body 12, said graduated scale 27 being obtained by silk screen printing or stamping the metal surface and being configured, cooperatively with a nick or reference 19 formed on the body 12, to indicate to the operator, outside the body 12, the angular po- sition of the second opening 22' of the rotating shutter 20 with respect to the stationary second opening 15' of the inner wall 15 and corresponding to a greater or smaller extension of the fluid pas- sage opening.

Referring to Figures 3, 9, and 10, in the first embodiment, the valve 10 comprises a spacer 82 housed in said body 12 having substantially an an- nular shape, said spacer 82 being

configured to close the opening 14 in order to prevent the inner elements to be extracted from the body 12 of the valve 10.

Valve 10, 10' can also comprise conventional first fluid sealing elements 90 disposed between the body 12 and rotating shutter 20 and second flu- id sealing elements 90' disposed between said ro- tating shutter 20 and said spacer 82. Said first and second sealing elements 90, 90' can be further fit and housed in mated seats or recesses formed on the same rotating shutter 20 and spacer 82 or, al- ternatively, formed on the body 12 inner surface.

Valve 10, 10' can comprise also conventional third fluid sealing elements 95 disposed between the body 12 and other connecting elements, hydrau- lic devices or valves, not shown, said third fluid sealing elements 95 being generally fit and housed in suitable seats or recesses.

Referring now to Figures from 4 to 6 and from 11 to 14, and particularly to Figs 6, 13 and 14, in a second embodiment, the valve 10' further compris- es :

a sleeve 30 having a substantially tubular shape, housed inside the rotating shutter 20 and defining with it a substantially toroidal annular chamber 50, said sleeve 30 being provided with at least one first through radial opening 32 formed in the lateral wall of the sleeve itself 30 and being disposed, at an end thereof, in contact with the bottom wall 22 of said rotating shutter 20 and with the opposite end facing the inlet opening 14;

a floating piston or shutter 40, slidingly housed inside the sleeve 30, having a substantially tubular glass or cup shape, with a bottom 42 and provided with at least one second radial through opening 43 made on the lateral wall, cooperating and mated to said first radial opening 32, said floating shutter 40 defining a first inner chamber 41 and a second inner chamber 52 comprised and de- limited between the bottom 42 of the floating shut- ter 40 itself, the sleeve 30 and the bottom wall 42 of the rotating shutter 20;

so that an axial translation motion of said second radial opening 43 of the floating shutter 40 with respect to said first radial opening 32 of the sleeve 30, is matched by a variation of the fluid passage cross-section proportional to the axial sliding of the floating shutter 40.

Said fluid passage cross-section, defined be- tween said first and second radial openings 32, 43, is configured to fluidically connect said annular chamber 50 to the inlet opening 14 of the valve 10', through the first chamber 41. In contrast, said second inner chamber 52 is fluidically con- nected to the outlet opening 14' by at least one passage 55 made through the bottom wall 22 of the rotating shutter 20 and inner wall 15, so that a force determined by a pressure difference between the inlet opening 14 and outlet opening 14' acts on the bottom 42 of the floating shutter 40.

Preferably, said passage 55 is coaxially made with the rotation axis 11, so that it does not change the passage cross-section thereof or is not obstructed by the rotation motion of the rotating shutter 20 with respect to the inner wall 15.

With reference to the preferred embodiment of valve 10' of the figures, a plurality of said first and second radial openings 32, 43 are diametrally made and distributed on the lateral walls of said sleeve 30 and said floating shutter 40, so that the relative rotation between sleeve 30 and floating shutter 40 with respect to the rotation axis 11 de- termines a negligible variation of the fluid pas- sage cross-section with respect to the axial slid- ing motion of the floating shutter 40.

Valve 10' can be also provided with an elastic return element 60 disposed inside the second inner chamber 52 between the bottom 42 of the floating shutter 40 and the bottom wall 22 of the rotating shutter 20, and configured to hold the floating shutter 40 itself in a monostable position with the first radial opening 32 and second radial opening 43, in a position corresponding to the maximum flu- id flow passage.

Advantageously, said sleeve 30 can be also sta- bly coaxially housed in the rotating shutter 20 by a mouthpiece 21 formed on the bottom wall 22 of the rotating shutter 20 itself in order to improve the fluid sealing between the annular chamber 50 and second inner chamber 52.

Advantageously, the elastic element 60 can be also housed, at the ends thereof, inside a first recess 21' formed on the bottom wall 22 of the ro- tating shutter 20 and inside a second recess 42' made at the bottom end 42 of the floating shutter 40, in order to be firmly held in position with re- spect to the sleeve 30 and the floating shutter 40 itself .

Specifically, it is made reference to the pre- ferred embodiment of Figures 9 and 13, in which the sleeve 30 and floating shutter 40 can be advanta- geously formed in a "goblet" shape having a diame- tral increased cross-section at the corresponding ends facing the inlet opening 14, in order to ena- ble a greater structural size of the first and sec- ond mated radial openings 32, 43 and first and sec- ond mated openings 22', 15', with respect to a structural size obtainable by a simpler cylindrical tubular shape.

The goblet shape of the sleeve 30 and floating shutter 40 defines between them a further third chamber 53 having a volume varying with the axial sliding of the floating shutter. Said third chamber can also act as an elastic element upon compressing the air trapped inside the chamber.

One or more drain holes 44 for draining a pos- sible incompressible liquid being trapped between the walls of said third chamber 53 can be provided, and such to prevent the floating shutter 40 from freely sliding inside the sleeve 30.

Referring again to the preferred embodiment of the figures, said sleeve 30 can comprise a diame- tral increased portion 35 with a shoulder formed at the open end thereof facing the inlet opening 14, said diametral increased portion 35 being config- ured to enable the sleeve 30 to be stably housed inside the body 12. In a further alternative embod- iment, the diametral increased portion 35 can be separated from and be in contact with the sleeve 30 or can be replaced, for example, by the spacer 82 of the first simplified embodiment of the valve 10.

Referring in particular also to Figures 13 and 14, the valve 10' can comprise one or more conven- tional first fluid sealing elements 90 disposed be- tween the body 12 and rotating shutter 20 and one or more fluid sealing elements 90' disposed between said rotating shutter 20 and said sleeve 30. Said first and second sealing elements 90, 90' can be fit and housed in mated seats or recesses formed on the rotating shutter 20 and diametral increased portion 35 of the sleeve 30 or alternatively formed on the inner surface of the body 12.

Sleeve 30 and floating shutter 40 can be also preferably made of a metal material, typically cop- per alloys or iron alloys, however they can also be advantageously made of plastic polymeric materials or thermoplastic materials or materials obtained by sinterizing metal or ceramic powders or of materi- als obtained by additive manufacturing process.

Referring again to all the Figures from 1 to 14, said valve 10, 10' can be advantageously pro- vided with conventional stop elements 80, such as for example elastic retaining rings, snap rings al- so known as Seeger, washers and similar, housed in an annular recess formed on the inlet opening 14 of the body 12, said stop elements 80 being configured to prevent said spacer 82 and/or shutter 30 from axially sliding and being extracted.

Referring now just to Figures 6, 13 and 14, in the second embodiment, the valve 10' can further comprise at least one third fluid sealing element

92, such as for example gaskets or O-rings, dis- posed between the sleeve 30 and floating shutter 40 and configured to maintain the fluid sealing be- tween said first inner chamber 41 and said second inner chamber 52. Advantageously, said third seal- ing element 92 can be also fit and housed in a seat or recess 45 formed on the outer diametral surface of the floating shutter 40.

Said first and second sealing elements 90, and 90' and said other sealing elements 95 can be of the gasket type or O-ring type, preferably made of polymeric and elastomeric materials.

Referring just to Figure 15, part of the object of the present invention is also a device compris- ing a valve 10, 10' attached to a conventional mul- tiway hydraulic valve or diverter valve 100, such as for example a six way (3+3) valve, provided with a valve body 102 and a plurality of openings 104 formed on the valve body 102 itself and actuating inner members 106 capable of selectively piping the flow rate of the fluid entering the inlet openings from two distinct thermal sources to a single out- let opening towards the thermal user circuit and returning from the return opening from the user circuit selectively towards the two outlet openings returning to the sources.

The multiway valve or diverter valve 100 com- prises at least one valve 10, 10' for hydraulic control and balancing of fluid flow rate stabilized at one of the openings of the multiway valve or di- verter valve 100 itself, preferably, but in a non- limiting way, at the openings 104 connected by the thermal sources, for example hot and cold, to the multiway valve or diverter valve 100.

From the description of the valve 10, 10' for hydraulic control and balancing of fluid flow rate object of the present invention, it is understood the operation described in the following.

Referring to Figures from 1 to 3 and from 7 to 10, in the first simplified embodiment, the valve 10 is capable of providing only one static control or pre-regulation of the fluid flow rate. The stat- ic control of the fluid flow rate is the same also in the second embodiment of the valve 10' , in the same way to what is hereinbefore described with reference to the first embodiment of the valve 10.

In the valve 10, 10' of the present invention, the rotating shutter 20, for example unlike a con- ventional hollow ball shutter, is configured to ro- tate and to be crossed by a fluid with respect to an axis substantially coinciding with the fluid flow direction, between the inlet opening 14 and outlet opening 14', without the requirement of us- ing levers, knobs, taps, or wheels, and when the outer diametral surface of the shutter itself oper- ates as an actuating means.

The operator, by acting with one or more fin- gers on the irregular surface portion 26 through the actuating opening 16 of the body 12, puts in rotation the rotating shutter 20 with respect to the body 12 itself of the valve 10, 10' . A rotation of the rotating shutter 20 aligns the first open- ings 22' so that they are cooperatively oriented with the mated second openings 15' of the inner wall 15, in order to consequently vary the port or fluid flow cross-section passage inside the valve 10, 10' between a minimum or null value and a maxi- mum value respectively corresponding to the obtain- able maximum and minimum limit values of the flow rate .

The valve 10, 10' can be configured to inter- rupt the fluid flow in a position wherein the first openings 22' and second openings 15' do not over- lap, not even partially, or the valve 10, 10' can be configured in order to always ensure a minimum fluid flow passage by always leaving a minimum overlapping surface between the first and second openings 22' , 15' themselves. When the shapes of the first opening 22' of the rotating shutter 20 coincide with each other, by overlapping the shapes of the second openings 15' of the inner wall 15, the maximum opening of the fluid flow passage is obtained. The greater the offset angle between the first openings 22' and second openings 15' is, the smaller the fluid flow passage opening will be. The graduated scale 27, present on the external surface of the rotating shutter 20, shows the operator the offset angle of the openings 22' and 15'; when the offset angle is about 0°, in other words the open- ings completely overlap on each other, the maximum value of the graduated scale is positioned at the nick or reference 19. Viceversa, when the maximum offset angle between the first openings 22' and second openings 15' is the greatest and corresponds to a minimum or null passage port of the fluid, the minimum value of the graduated scale is in corre- spondence of the nick or reference 19.

Once the opening of the passage port or cross- section is adjusted by rotating the rotating shut- ter 20 in order to take the numeric value selected on the graduated scale 27 to the nick or reference

19 corresponding to the desired nominal flow rate, the flow rate exiting the valve 10, 10' therefore remains constant if there are not upstream and downstream pressure variations.

With reference to Figures from 4 to 6 and from 11 to 14, the valve 10' of the second embodiment is capable of providing, besides a static control or pre-regulation, also a flow rate dynamic balancing, in other words the valve 10' is capable of self- balancing and maintaining constant the fluid flow rate set by the graduated scale 27 by rotating the rotating shutter 20, also as a result of a varia- tion of the upstream and downstream fluid pressure conditions .

In an initial transient phase, the pressurized fluid flow enters the valve 10' through the inlet opening 14 and flows in proximity of the first in- ner chamber 41 of the floating shutter 40, striking the floating shutter 40 itself floods the annular chamber 50 by flowing through the passage cross- section defined by the first radial openings 32 of the sleeve 30 and by the second radial openings 43 of the floating shutter 40, said openings being completely overlapped.

Referring particularly to Figures 13 and 14, the increasing momentum of the entering liquid flow rate causes an increased pressure in the first in- ner chamber 41 and such to produce a force, propor- tional to its strength, on the bottom 42 of the floating shutter causing it to axially translate and overcoming the force of the elastic element 60. The increasing flow rate through the first and sec- ond radial openings 32, 43, determined by a pres- sure increase in the first inner chamber 41, in- creases also the thrusting force on the floating shutter 40 which is consequently caused leaded to translate towards the outlet opening 14' with the second radial openings 43 translating with respect to the first radial openings 32 of the sleeve 30, consequently reducing their overlapping and the passage cross-section of the liquid flow in the an- nular chamber 50, so that a flow rate reduction is caused .

The rigidity of the elastic element 50 deter- mines also a pressure range in which the floating shutter 40 is capable of compensating the pressure difference .

Still referring to the same figures, if the fluid pressure and the momentum thereof decrease, causing a reduction of the liquid flow rate through the valve 10', the elastic element 60 overcomes the opposite force exerted by the fluid on the bottom

22, translating the floating shutter 40 in an oppo- site direction and increasing the fluid passage cross-section from the first inner chamber 41 to the annular chamber 50, in order to always maintain constant the flow rate about the desired nominal value .

If the momentum of the entering fluid increas- es, and also the pressure difference between the inlet and outlet increases, they also cause an in- crease of the fluid flow rate so that the floating shutter 40 is moved to the left and the fluid pas- sage cross-section is shrank so that the increased pressure at the inlet is compensated and the preset flow rate is maintained constant.

If the upstream fluid momentum decreases and/or the downstream pressure increases at the outlet opening 14' of the valve 10', the fluid flow rate decreases. The fluid pressure at the outlet opening 14' is the same as the one inside the second inner chamber 52, since said second inner chamber 52 is always in fluid communication with the outlet open- ing 14' through the passage 55 (Figures 13 and 14) .

The fluid pressure in the outlet opening 14' is consequently transmitted into the second inner chamber 52 so that the floating shutter 40 with the elastic element 60 is thrusted to the right in or- der to increase the fluid cross-section at the first and second radial openings 32, 43, so that a greater amount of fluid is retrieved in the valve 10' and the pressure difference is reduced.

The first sealing elements 90 ensure the opera- tion of the valve 10, 10' by fluidically sealing the rotating shutter 20 from the body 12, while the third sealing element 92 fluidically seals the first and second inner chambers 41, 52.

Still referring to the same figures, the opera- tion of the present valve is innovative with re- spect to the traditional valves because a force de- termined by the fluid pressure in the second inner chamber 52 operates on the bottom 42 of the float- ing shutter 40. Said force determined by the pres- sure downstream the valve in the outlet opening 14' is added to the force of the elastic element 60 and together they thrust the floating shutter 40 in or- der to increase the fluid passage cross-section in the annular chamber 50 and a greater amount of liq- uid is retrieved in the outlet opening 14' from the annular chamber 50, through the first and second openings 22' , 15'. In this configuration, the valve 10' besides operating in dependence of the momentum of the en- tering fluid flow, also advantageously operates as a function of the pressure difference Dr measured between the pressure of the fluid entering the first inner chamber 41 and pressure of the fluid exiting the second inner chamber 52.

Referring again just to Figure 15, valve 10, 10' paired with a traditional hydraulic multiway valve or diverter valve 100, such as for example a six way (3+3) valve, enables to manage, by means of a single compact device, the static control and dy- namic balancing, at the inlet of a user hydraulic circuit, from two distinct thermal inlet sources, for example hot and cold, which generally require fluid flow rates different from each other.

The valve 10, 10' , besides being easily in- stalled and placed on the opening 104 of the multi- way valve 100, and having a compact size, enables the operator to pre-regulate the flow rate from distinct thermal sources without disconnecting de- livery conduits and manifolds from the openings 104 of the valves. Moreover, the valve 10, 10' enables the operator to advantageously see on the graduated scale 27 of the valve 10, 10' itself, the pre- regulated set of the flow rate through the differ- ent openings 104 of the multiway valve 100.

The valve 10, 10', object of the present inven- tion, can be advantageously installed on the open- ings 104 configured as an inlet from the thermal sources, independently from their position on the multiway valve 100.

The preceding illustration makes clear the ad- vantages obtained by the valve for hydraulic con- trol and balancing of fluid flow rate object of the present invention.

The valve for hydraulic control and balancing of fluid flow rate object of the present invention is particularly advantageous since can be easily installed in very narrow rooms and in general boxes where a high number of conduits and pipes are re- ceived, because said valve is geometrically simpli- fied into the shape of a segment or piece of a cy- lindrical pipe.

Specifically, the easier and smoother installa- tion in narrow rooms of the valve of the present invention makes it particularly convenient when is installed paired with a traditional multiway di- verter valve or "six way" valve.

The valve for hydraulic control and balancing of fluid flow rate object of the present invention is also particularly advantageous because enables a user to check it from the outside and adjust the flow rate, for example as a function of changed conditions or extensions of the user plant, without disassembling connecting manifolds and pipes and without the presence of a skilled operator.

A further relevant advantage of the valve for hydraulic control and balancing of fluid flow rate is that it does not have actuating members project- ing or protruding above the valve body itself, such as levers, knobs, screw down taps or electromechan- ical actuators which decrease the available instal- lation space.

A consequent further advantage of the valve for hydraulic control and balancing of fluid flow rate consists of requiring less room or space for maneu- vering the control members, levers, knobs, taps, etcetera, because this valve can be easily actuated by acting on only with one finger of the operator.

A further advantage of the valve for hydraulic control and balancing of fluid flow rate of the present invention is that during the hydraulic bal- ancing step, the valve is capable to control the flow rate as a function of the pressure difference between the inlet and outlet openings of the same and not only as a function of the momentum of the liquid fluid which moves the inner balancing mem- bers .

Another important advantage due to the valve for hydraulic control and balancing of fluid flow rate is that the same enables a substantial fluid flow rate in comparison with the small outer size due to the low load losses and the c obtained by maintaining the linear direction of the fluid with- out sudden changes of direction.

A still further advantage of the valve for hy- draulic control and balancing of fluid flow rate object of the present invention is due to the fact that while the manoeuver members and maneuvering rooms of a traditional valve increase proportional- ly to the size of the valve, in the valve object of the present invention the same remain constant be- cause it can be easily actuated by only one finger of the operator independently from the size and proportion of the same.

A further advantage of the valve for hydraulic control and balancing of fluid flow rate is due to the fact that the longitudinal size of the valve can remain substantially unchanged even though the valve radial size increases. Further, while in a traditional valve the force required for actuating the control members increases as the valve size in- creases, by the valve for hydraulic control and balancing of fluid flow rate object of the present invention the force remains constant and the valve can be easily actuated by only one finger of the operator because the lever arm of the operator act- ing on the irregular surface portion 26 increases as the diametral size of the rotating shutter 20 increases .

While the beforehand described invention was described referring particularly to some preferred embodiments, given in an exemplifying non-limiting way, many modifications and variants will be under- stood by a person skilled in the art in light of the above discussed description. Therefore, the present invention intends to encompass all the mod- ifications and variants falling in the scope of the attached claims.