WO2022172240A1

WO2022172240A1 - Valve system for the regulation of the flow of a fluid

Info

Publication number: WO2022172240A1
Application number: PCT/IB2022/051288
Authority: WO
Inventors: Francesco PICCININI
Original assignee: Piccinini Francesco
Priority date: 2021-02-12
Filing date: 2022-02-14
Publication date: 2022-08-18
Also published as: IT202100003227A1

Abstract

The valve system (1), associable with an appliance (2) provided with one working chamber (3) and with one transit channel (4) of a fluid communicating with the working chamber (3) through one transit opening (5), comprises: - one valve device (6) comprising one main valve (60) provided with one main head (9) and movable between a home configuration, wherein it interacts with the transit opening (5), and at least one working configuration wherein it is displaced towards the working chamber (3) so as to open said transit opening (5); and - movement means (7) of the valve device (6) adapted to move at least the main valve (60); where the main head (9) is provided with at least one gap (11) for the transit of a portion of the flow of fluid into/from the working chamber (3) and where the valve device (6) comprises at least one opening/closing element (12) movable with respect to the main valve (60) to open/close the gap (11).

Description

VALVE SYSTEM FOR THE REGULATION OF THE FLOW OF A FLUID

Technical Field

The present invention relates to a valve system for the regulation of the flow of a fluid.

Background Art

Valve systems applied to different types of appliances for the regulation of the flow of a fluid are used in many industrial sectors.

For example, the appliance may be an internal combustion engine, a pump, a compressor or any appliance where regulation of the flow of a fluid is required. Known appliances generally comprise a working chamber and a transit channel of a fluid, communicating with the working chamber itself through a transit opening.

Known appliances also comprise at least one valve which opens/closes to let the fluid in only at precise times in the operating process.

In a home configuration, the valve obstructs the transit opening, while in a working configuration, the valve is spaced apart from the transit opening to allow the transit of the fluid.

In detail, the flow is able to enter the working chamber through the space interposed between the valve, in the working configuration, and the transit opening.

In order to regulate the flow and allow a higher flow rate of the fluid, it is possible to adjust the movement of the valve so that the distance of the valve itself from the transit opening is increased.

This solution has, however, its drawbacks because, generally, the space available inside such appliances is limited and an excessive distance of the valve from the transit opening could also hinder the movement of other components.

Another drawback is represented by the fact that, in the appliances of known type, as e.g. in the internal combustion engines, the transit channel and the working chamber are properly designed in order to create special turbulences in the flow of the fluid inside the working chamber itself, so called “squish”, “swirl” and “tumble”, to obtain a high efficiency of the appliance itself.

The effect of such conformations is however limited by the fact that the flow of the fluid is inevitably forced to enter the working chamber through the space between the valve and the transit opening.

Therefore, there is a need to improve the valve systems of known appliances in order to make them more efficient.

Description of the Invention

The main aim of the present invention is to devise a valve system for the regulation of the flow of a fluid which allows optimizing the flow of fluid entering, and possibly also exiting, the working chamber at any phase of the operating process.

Another object of the present invention is to devise a valve system for the regulation of the flow of a fluid which allows varying the flow rate of the fluid flow entering, and possibly also exiting, the working chamber.

A further object of the present invention is to devise a valve system for the regulation of the flow of a fluid which allows achieving effective turbulence of the flow of the fluid in the working chamber.

An additional object of the present invention is to devise a valve system for the regulation of the flow of a fluid which allows increasing the flow rate of the fluid, especially at low and medium lift, i.e., the valve outflow coefficient, compared to the solutions of known type.

Another object of the present invention is to devise a valve system for the regulation of the flow of a fluid which allows the aforementioned drawbacks of the prior art to be overcome within a simple, rational, easy and effective to use as well as affordable solution.

The aforementioned objects are achieved by the present valve system for the regulation of the flow of a fluid having the characteristics of claim 1.

Brief Description of the Drawings

Other characteristics and advantages of the present invention will become more apparent from the description of a preferred, but not exclusive, embodiment of a valve system for the regulation of the flow of a fluid, illustrated by way of an indicative, yet non-limiting example, in the accompanying tables of drawings wherein:

Figure 1 is an axonometric view of an appliance provided with two valve systems according to the invention, in accordance with a first embodiment; Figures 2 and 3 are side cross-sectional views of the appliance in Figure 1, in two different operating configurations;

Figures 4-6 are axonometric views of a main valve according to the invention, in accordance with different possible embodiments;

Figure 7 is a side view of the main valve in Figure 6;

Figure 8 is a plan view of the main valve in Figure 6;

Figure 9 is a side view of an appliance provided with valve systems according to the invention in accordance with a second embodiment;

Figure 10 is a cross-sectional view along the plane X-X in Figure 9;

Figure 11 is a side cross-sectional view of the appliance in Figure 9;

Figure 12 is a cross-sectional view along the plane XII-XII in Figure 11;

Figure 13 is an axonometric view of the appliance in Figure 9;

Figure 14 is a side view of an appliance provided with valve systems according to the invention in accordance with a third embodiment;

Figure 15 is a cross-sectional view along the plane XV-XV in Figure 14;

Figure 16 is an axonometric view of the appliance in Figure 9;

Figure 17 is a detailed axonometric view of the movement means of the valve systems in accordance with the second and the third embodiments;

Figures 18 and 19 are side cross-sectional views of the appliance in Figure 9, in two different operating configurations;

Figures 20 and 21 are side cross-sectional views of the valve system according to the invention, in accordance with a fourth embodiment, in two different operating configurations;

Figures 22 and 23 are side cross-sectional views of the valve system according to the invention, in accordance with a fifth embodiment, in two different operating configurations; Figures 24 and 25 are side cross-sectional views of the valve system according to the invention, in accordance with a sixth embodiment, in two different operating configurations;

Figure 26 is a partial cross-sectional axonometric view of the valve system according to the invention in accordance with a seventh embodiment;

Figures 27 and 28 are side cross-sectional views of the valve system in Figure 26, in two different operating configurations;

Figure 29 is a partial cross-sectional axonometric view of the valve system according to the invention in accordance with an eighth embodiment;

Figures 30 and 31 are side cross-sectional views of the valve system in Figure 29, in two different operating configurations.

Fmbodiments of the Invention

With particular reference to such figures, reference numeral 1 globally indicates a valve system for the regulation of the flow of a fluid.

The valve system 1 is associable with an appliance 2 provided with at least one working chamber 3 and with at least one transit channel 4 of a fluid communicating with the working chamber 3 through at least one transit opening

5.

For example, the appliance 2 may be an internal combustion engine, a pump, a compressor, or any appliance wherein the regulation of the flow of a fluid is required.

The valve system 1 comprises at least one valve device 6 which is associated movable by sliding with the working chamber 3 and adapted to open/close the transit channel 4.

In more detail, the valve device 6 comprises at least one main valve 60 movable between a home configuration, wherein it interacts with the transit opening 5, and at least one working configuration, wherein it is displaced towards the working chamber 3 so as to open the transit opening 5.

The valve system 1 also comprises movement means 7 of the valve device 6 adapted to move at least the main valve 60 between the working configuration and the home configuration. The main valve 60 is provided with at least one main stem 8 kinematically connected to the movement means 7 and with at least one main head 9 having a larger cross-section than the main stem 8 adapted to obstruct the transit channel

4.

In the context of the present disclosure, the expression “working chamber” refers to a cavity defined in the appliance 2 wherein the main head 9 is housed and which is intended to receive/supply fluid from/to the transit channel 4. For example, in the case where the appliance 2 is an internal combustion engine, the working chamber 3 is the combustion chamber/cylinder which houses a piston and in which the combustion process takes place.

The main stem 8 extends along a first longitudinal axis Al.

The main head 9 is arranged at one end of the main stem 8, inside the working chamber 3, and is adapted to obstruct the transit channel 4 at the point where the transit opening 5 is located.

At the point where the transit opening 5 is located, the transit channel 4 may have a housing seat 10 adapted to receive the main head 9 in the home configuration.

The housing seat 10 has a conformation substantially complementary to the peripheral edge of the main head 9 and, in the home configuration, it allows for a substantially tight closure of the transit opening 5.

In the working configuration, on the other hand, the main head 9 is spaced apart from the transit opening 5 and allows the flow of the fluid to pass through the space between them.

According to the invention, the main head 9 is provided with at least one gap 11 for the transit of a portion of the flow of fluid into/from the working chamber 3. The gap 11 is of the type of a through opening and allows the communication between the transit channel 4 and the working chamber 3.

Still according to the invention, the valve device 6 comprises at least one opening/closing element 12 movable with respect to the main valve 60 to open/close the gap 11.

Thus, the present valve device 6 allows fractionating the flow of fluid entering the working chamber 3 so as to vary the flow rate and the inflow modes thereof. Usefully, the opening/closing element 12 is associated movable by sliding with the main valve 60 along the first longitudinal axis A1 between a closing configuration, wherein it closes the gap 11, and at least one opening configuration, wherein it opens the gap 11.

It should be noted that it is possible, but not mandatory, to be able to remain, for the entire movement of the opening/closing element 12, within the overall dimensions of the main valve 60. This makes it possible for the valve device 6, with appropriate modifications, to replace the already existing valve systems, in motor processing practice.

With the main valve 60 in the working configuration and the opening/closing element 12 in the opening configuration, the flow of fluid, therefore, flows into the working chamber 3 through the space between the main head 9 and the transit opening 5 and through the gaps 11. It follows that the present valve system 1 allows increasing the flow rate of the fluid and outflow coefficient compared to the valves of known type.

The movement means 7 are adapted to move both the main valve 60 and the opening/closing element 12 along the first longitudinal axis Al.

Advantageously, the movement means are adapted to move the main valve 60, between the working configuration and the home configuration, at a first speed and the opening/closing element 12, between the opening configuration and the closing configuration, at a second speed.

In the context of the present disclosure, the term “speed” means an absolute speed. The main valve 60 and the opening/closing element 12 may move at varying speeds and be subject to acceleration and deceleration.

The first speed and the second speed can be different from each other.

For example, the second speed may be greater than the first speed. In this way, the opening/closing element 12 is moved towards the opening configuration faster than the movement of the main valve 60 towards the working configuration.

In other cases, when the gaps 11 are used for the fine regulation of the flow rate, the second speed may be even lower than the first speed, in order to partly close the transit of the fluid coming from the gaps 11.

The flow of fluid enters the working chamber 3 either through the gap 11 or through the space between the main valve 60 and the transit opening 5.

The different embodiments represented in the figures are described in detail below. The elements common to all embodiments described and shown are identified below with the same reference numbers.

In the embodiments shown in Figures 1 to 25, the main valve 60 is internally hollow and the opening/closing element 12 is arranged internally to the main valve 60.

Specifically, the opening/closing element 12 is arranged internally to the main head 9.

Advantageously, the valve device 6 comprises a secondary valve 13 comprising a relevant secondary stem 14 and a relevant secondary head, wherein the secondary head corresponds to the opening/closing element 12.

In other words, the secondary head is adapted to open/close the gap 11.

At the same time, the secondary stem 14 is arranged internally to the main stem

8.

The secondary stem 14 in turn extends along a second longitudinal axis A2, and the main stem 8 and the secondary stem 14 are coaxial to each other. Conveniently, the main stem 8 and/or the secondary stem 14 may comprise surface coatings adapted to promote the sliding between their respective surfaces. Alternatively, bushings may be provided between the main stem 8 and the secondary stem 14.

In the embodiments shown in Figures 1 to 23, the main head 9 is of a substantially truncated-cone conformation converging towards the main stem 8 and the at least one gap 11 is arranged on the lateral surface of the main head 9. The opening/closing element is of a substantially complementary conformation to the main head 9 and, in the closing configuration, it is housed to size within it.

Specifically, in the closing configuration, the opening/closing element 12 adheres to the main head 9 to obstruct the gap 11, while in the opening configuration, the opening/closing element 12 is spaced apart from the main head 9 to allow the fluid to pass through the gap 11.

Advantageously, the main head 9 comprises a plurality of gaps 11.

The gaps 11 are arranged in a radial pattern with respect to the first longitudinal axis Al.

Specifically, the gaps 11 are arranged side by side along at least one circumference of the main head 9.

It cannot, however, be ruled out that the gaps 11 may be arranged on a plurality of circumferences of the main head 9.

It cannot also be ruled out that the gaps 11 may be arranged irregularly on the lateral surface of the main head 9.

Each of the gaps 11 extends along a relevant working axis W.

The term “working axis” used herein means the longitudinal axis along which the gap 11 develops, which may have a circular cross section of constant or variable size along the relevant working axis W, or may have an irregular cross section. In more detail, the working axis W may be understood as coinciding with the axis of a milling cutter intended to obtain the gap 11 on the main head 9 during the manufacturing process.

The working axis W, moreover, can be either straight or curvilinear.

The gaps 11 may be made so that the relevant working axes W are parallel or inclined to each other. In other words, the gaps 11 may develop along the relevant working axes W, each arranged differently with respect to the first longitudinal axis Al.

Conveniently, at least one of the gaps 11 is developed along a relevant working axis W substantially parallel to the first longitudinal axis Al.

Alternatively or in combination, at least one of the gaps 11 is developed along a relevant working axis W inclined with respect to the first longitudinal axis Al. Specifically, at least one of the gaps 11 develops along a relevant working axis W offset with respect to the first longitudinal axis Al.

In particular, with reference to the embodiment shown in Figures 1 to 4 and 6 to 31, the working axis W is substantially straight.

In Figure 5, on the other hand, a further embodiment of the main valve 60 is shown in which the working axis W has a curvilinear pattern and, specifically, is of helical conformation. According to this embodiment, the main stem 8 is provided with a groove 27 extending longitudinally and is adapted to convey the flow of fluid towards the gap 11.

The arrangement and conformation of the working axes W allow a particular direction to be given to the portion of the flow of fluid crossing the gap 11 towards certain areas of the working chamber 3.

For example, in the case wherein the appliance 2 is an internal combustion engine, the arrangement and conformation of the working axis W allow for the creation of predefined turbulence inside the working chamber 3 which may contribute to increasing the efficiency of the appliance itself or to optimizing the performance thereof. In particular, the conformation and arrangement of the gaps 11 allow increasing the tumble vortex and/or the swirl vortex in the working chamber 3, as will be better described later in this disclosure.

According to a first embodiment, shown in Figures 1 to 4, the main head 9 comprises a plurality of gaps 11, wherein each gap 11 is developed along a relevant working axis W substantially parallel to the first longitudinal axis Al. According to this embodiment, the movement means 7 comprise first actuating means 15 kinematically connected to the main valve 60 to move it from the working configuration to the home configuration.

The first actuating means 15 comprise at least a first cam 16 movable in rotation around a relevant axis of rotation R and adapted to interact with the main valve 60.

The movement means 7 also comprise second actuating means 17 kinematically connected to the opening/closing element 12 to move it from the closing configuration to the opening configuration.

The opening/closing element 12 is, therefore, movable independently of the main valve 60 to regulate the flow of fluid.

The second actuating means 17 comprise at least a second cam 18 movable in rotation around a relevant axis of rotation R and adapted to interact with the opening/closing element 12.

Usefully, the first cam 16 and the second cam 18 are locked to each other in rotation around the axis of rotation R and have different profiles from each other.

The actuating means 15, 17 also comprise a tappet system associated with the valve device 6 and upon which the cams 16 and 18 operate.

Specifically, the tappet system comprises at least a first cup element 19 connected to the main valve 60 and at least a second cup element 20 connected to the secondary valve 13.

The first cam 16 is adapted to operate on the first cup element 19 and the second cam 18 is adapted to operate on the second cup element 20.

In the particular embodiment shown in the figures, the second element 20 has a substantially beam shape with a rectangular cross section and is positioned between two portions of the first cup element 19. At the same time, the second cam 18 is positioned between two portions of the first cam 16.

This arrangement gives the valve device 6 a phased movement in anti-rotation which allows, therefore, to keep the gaps 11 phased at an angle with respect to the first longitudinal axis Al, thus ensuring that the flow of fluid in the working chamber 3 is always regular in a fluid- operated manner and repetitive at each cycle.

It cannot, however, be ruled out that the actuating means 15,17 comprise cams and rocker arms with recoil tappets, desmodromic controls, controls with electric motors, pneumatic controls, hydraulic controls or a combination thereof.

Furthermore, the movement means 7 comprise first return means 21, of the elastic type, adapted to move the main valve 60 towards the home configuration, which are positioned between the main valve 60 and a first fixed abutment wall 24.

The first return means 21 are positioned between the first cup element 19 and the first abutment wall 24. In detail, the first return means 21 comprise a first spring 21a developed around the main stem 8.

In other words, the axis of the first spring 21a coincides with the first longitudinal axis Al.

The movement means 7 also comprise second return means 22, of the elastic type, adapted to move the opening/closing element 12 towards the closing configuration, which are positioned between the opening/closing element 12 and a second abutment wall 28.

More specifically, the first cup element 19 internally defines the second abutment wall 28.

The second return means 22, therefore, are positioned between the second cup element 20 and the first cup element 19.

In detail, the second return means 22 comprise a second spring 22a developing around the secondary stem 14. The axis of the second spring 22a coincides with the second longitudinal axis A2.

The second return means 22 are, therefore, arranged internally to the first cup element 19.

According to the preferred embodiments shown in Figures 6 to 19, the main head 9 comprises a plurality of gaps 11, wherein the gaps 11 comprise: at least one first gap 111 extending along a first working axis W1 substantially parallel to the first longitudinal axis Al; and at least one pair of gaps 112,113 each running along a relevant working axis W2,W3 offset with respect to the first longitudinal axis Al.

The working axes W2,W3 of the at least one pair of gaps 112,113 are inclined to each other.

The working axes W2,W3 of the at least one pair of gaps 112,113 are incident to each other.

Specifically, the working axes W2,W3 of the at least one pair of gaps 112,113 are incident to each other at one reference plane PI passing between the first working axis W1 and the first longitudinal axis Al (Figure 8).

In addition, the working axes W2,W3 of the at least one pair of gaps 112,113 are symmetrical to each other with respect to the reference plane PL It follows that the also the gaps 112, 113 of the at least one pair of gaps 112,113 are arranged symmetrically with respect to the reference plane PL Advantageously, the at least one pair of gaps 112,113 comprises at least one pair of second gaps 112 each running along a second working axis W2 and at least one pair of third gaps 113 each running along a third working axis W3, inclined with respect to the second working axis W2.

Each of the second gaps 112 is positioned between the first gap 111 and one of the third gaps 113. In particular, according to the preferred embodiments, the gaps 111,112,113 are arranged in a pentagon.

The second working axes W2 are incident to each other superiorly to a base plane B perpendicular to the reference plane PI and passing through the lower end of the main head 9.

The third working axes W3, on the other hand, are incident to each other inferiorly to the base plane B.

In other words, the flows of fluid passing through the third gaps 113 tend to converge towards a single direction, while the flows of fluid passing through the second gaps 112 tend to diverge from each other.

Conveniently, the second working axes W2 and the third working axes W3 are incident to an orthogonal plane P2 substantially perpendicular to the reference plane PI and passing through the first working axis Wl, superiorly to the base plane B.

This embodiment ensures that the flow of fluid connected in the free volume between the main head 9 and the opening/closing element 12 is overall directed towards the wall of the working chamber 3 opposite the transit opening 5, thus promoting the formation of turbulence inside the working chamber 3 which can contribute to increasing the efficiency of the appliance itself or to optimizing the performance thereof.

According to a second embodiment shown in Figures 9 to 13, 18 and 19, the reference plane PI is coincident with a vertical longitudinal plane L of the transit channel 4 (Figure 10). The main valve 60 is, therefore, arranged so that the flow of fluid passing through the transit channel 4 reaches substantially at the same time all of the gaps 111, 112, 113 without having to “bypass” the main stem 8.

This arrangement allows optimizing the inflow of fluid into the working chamber 3 and the efficiency of the appliance 2.

This arrangement has also been shown to significantly increase the tumble vortex (Figure 13).

According to a third embodiment shown in Figures 14 to 16, on the other hand, the reference plane PI is rotated with respect to the vertical longitudinal plane L of the transit channel 4, around the first longitudinal axis Al, by an angle comprised between 20° and 45° (Figure 15).

With particular reference to the embodiment shown in the figures, the appliance 2 comprises a plurality of valve systems 1 , wherein the main valves 60 may be arranged with the relevant reference planes PI inclined with respect to the vertical longitudinal plane L by different angles from each other.

This arrangement causes the flow of fluid passing through the gaps 111, 112, 113 to be directed tangentially to the working chamber 3 allowing increasing the swirl vortex (Figure 16).

Still with reference to the embodiments shown in Figures 9 to 19, the movement means 7 comprise the actuating means 15,17 similarly to what has been described for the first embodiment.

The first return means 21, on the other hand, comprise a plurality of first springs 21a arranged around the main stem 8.

Unlike the first embodiment, therefore, the first springs 21a do not develop around the main stem 8 but are arranged to surround the latter. In other words, the axis of each first spring 21a is substantially parallel to the first longitudinal axis Al.

Similarly, the second return means 22 comprise a plurality of second springs 22a arranged around the main stem 8.

Unlike the first embodiment, therefore, the second springs 22a are arranged externally to the first cup element 19 and, in turn, are arranged to surround the main stem 8.

At the same time, the second abutment wall 28 is also defined externally to the first cup element 19.

This embodiment is structurally simple and easy to construct.

The axis of each second spring 22a is substantially parallel to the first longitudinal axis Al.

In detail, the axes of the springs 2 la, 22a are substantially parallel to each other. Advantageously, each of the second springs 22a is positioned between two of the first springs 21a.

In more detail, the springs 2 la, 22a are arranged in a radial pattern with respect to the first longitudinal axis Al.

According to a fourth embodiment shown in the Figures 20 and 21, the movement means 7 comprise first actuating means 15 and first return means 21 adapted to move the main valve 60 between the home configuration and the working configuration, similarly to what has been described with respect to the first embodiment.

The movement means 7 also comprise at least mechanical connection means 23 of the opening/closing element 12 to the main valve 60.

The mechanical connection means 23 are adapted to move the opening/closing element 12 between the opening configuration and the closing configuration.

The mechanical connection means 23 are of the elastic type and comprise at least one tensile spring constrained on one side to the main valve 60 and on the other side to the secondary stem 14.

It cannot, however, be ruled out that the mechanical connection means 23 be of a different type and comprise, e.g., internal compression springs.

The mechanical connection means 23 are adapted to control the displacement of the opening/closing element 12 between the closing configuration and the opening configuration due to the effect of the inertial forces determined by the acceleration of the main valve 60.

More specifically, the opening/closing element 12 is retained by the mechanical connection means 23 and is moved towards the opening configuration thanks to the only inertial forces. The movement of the opening/closing element 12 is, therefore, dependent on the actuation of the main valve 60.

The opening/closing element 12 is adapted to open and close after the main valve 60.

In particular, when the main valve 60 is decelerating to reach the working configuration corresponding to the maximum lift, the acceleration of the opening/closing element 12 is directed towards the first actuating means 15 and its inertial force has the opposite direction, i.e. it tends to move the opening/closing element itself towards the opening configuration, overcoming the pulling force of the mechanical connection means 23.

Similarly, even in the first section of the return stroke towards the home configuration of the main valve 60, the inertial force of the opening/closing element 12 tends to keep it in the opening configuration.

According to a fifth embodiment shown in Figures 22 and 23, the movement means 7 comprise only the return means 21,22 similarly to what has been described for the first embodiment.

The present embodiment provides for the second abutment wall 28 to be defined on the main valve 60.

In more detail, the second abutment wall 28 is defined internally to the main stem 8.

The opening/closing element 12 is movable from the closing configuration to the opening configuration due to the effect of the pressure difference between the transit channel 4 and the working chamber 3.

The main valve 60, in turn, is movable from the home configuration to the working configuration due to the effect of the pressure difference between the transit channel 4 and the working chamber 3 and of the action of the second return means 22 as a result of the displacement of the opening/closing element 12 towards the opening configuration.

In more detail, when the pressure in the working chamber 3 is lower than the pressure in the transit channel 4, the opening/closing element 12 is sucked towards the working chamber 3 and pulls the main valve 60 with it. When the two pressures rebalance, the return means 21,22 bring the main valve 60 and the opening/closing element 12 back to the home configuration and to the closing configuration, respectively.

Appropriately, the return means 21,22 have a predefined degree of stiffness so as to allow the movement of the main valve 60 and of the opening/closing element 12 at certain pressures.

According to a possible embodiment, not shown in detail in the figures, the valve device 6 comprises one or more intermediate valves positioned between the main valve 60 and the secondary valve 13, wherein the valves are arranged one inside the other, and provided with a relevant intermediate stem and with a relevant intermediate head.

On the intermediate head is defined at least one opening for the transit of the fluid.

The opening is substantially similar to the gap 11.

Each of the intermediate valves is movable between a relevant home configuration, wherein it obstructs at least partly the gap 11 or the opening of the valve containing it, and a relevant working configuration, wherein it allows the transit of the fluid through the gap 11 or the opening of the valve containing it.

This embodiment allows for greater portioning of the flow of fluid and is particularly advantageous especially in large-sized appliances.

According to such an embodiment, the movement means 7 are adapted to move the valves at different speeds from the main valve 60 to the secondary valve 13, between the home configuration and the working configuration.

According to a sixth embodiment shown in Figures 24 and 25, the main head 9 defines an inner chamber 25.

Specifically, the main head 9 is spheroidal in shape and is adapted to house the opening/closing element 12 which, in turn, is spheroidal in shape.

It cannot, however, be ruled out that the main head 9 and the opening/closing element 12 may have a parabolic or plate-shaped profile.

The gap 11 is defined at the point where the longitudinal end of the main head 9 is located and is adapted to place the inner chamber 25 in communication with the transit channel 4.

In the embodiment shown in Figures 24 and 25, the gap 11 is developed along a working axis W coincident with the first longitudinal axis Al.

Usefully, the main head 9 also comprises at least one through hole 26 defined on its lateral surface and adapted to place the inner chamber 25 in communication with the working chamber 3.

In the closing configuration, at least one through hole 26 is isolated from the gap 11, and in the opening configuration, at least one through hole 26 is placed in communication with the gap 11.

More specifically, in the closing configuration, the opening/closing element 12 occludes the gap 11 and does not allow the fluidic communication between the through hole 26 and the gap 11.

In the opening configuration, on the other hand, the opening/closing element 12 is moved away from the gap 11 and allows the fluid to flow from the transit channel 4 to the inner chamber 25 through the gap 11 and from the inner chamber 25 to the working chamber 3 through the through hole 26.

According to this embodiment, the movement means 7 comprise: at least one first movement assembly kinematically connected to the main valve 60 to move it between the working configuration and the home configuration; and at least one second movement assembly kinematically connected to the opening/closing element 12 to move it between the closing configuration and the opening configuration.

Each of the first movement assembly and of the second movement assembly comprises a screw movement system.

The first movement assembly comprises a first control member 30 and a first threaded member 31 kinematically connected to the main valve 60.

Similarly, the second movement assembly comprises a second control member 32 and a second threaded member 33 kinematically connected to the opening/closing element 12. The rotation of the control members 30,32 causes the shift of the main valve 60 and of the opening/closing element 12, respectively.

Usefully, at least the second threaded member 33 is provided with a fine pitch which allows precise regulation of the movement of the opening/closing element 12.

The first movement assembly also comprises a first anti-rotation system 34 associated with the main valve 60, which allows it to shift and is adapted to keep the main valve itself phased in anti-rotation.

At the same time, the second movement assembly comprises, in turn, a second anti-rotation system 35 positioned between the main valve 60 and the opening/closing element 12 which allows the shift of the latter phased in anti rotation.

With particular reference to Figures 24 and 25, the first movement assembly and the second movement assembly are manually operated.

It cannot, however, be ruled out that the first movement assembly and the second movement assembly be electrically, pneumatically, hydraulically, mechanically operated or a combination thereof.

Usefully, the first movement assembly and the second movement assembly are independent of each other.

In other words, the main valve 60 and the opening/closing element 12 are movable independently of each other. For example, it is possible to operate only the first movement assembly and vice versa.

This makes it possible, for example, to set the opening of the main valve 60 according to a predefined main flow rate and then to fine-tune it around that value by operating on the stroke of the opening/closing element 12.

According to further embodiments shown in Figures 26 to 31, the opening/closing element 12 is fitted on the main stem 8 and is positioned between the main head 9 and the working chamber 3.

The opening/closing element 12, therefore, is movable between the closing configuration and the opening configuration externally to the main valve 60.

The main valve 60 is arranged inside the working chamber 3 and has a main head 9 of substantially plate-shaped conformation.

The main valve 60 comprises a plurality of main stems 8, each of which extending along a relevant first longitudinal axis Al.

The opening/closing element 12 is also of substantially plate-shaped conformation and has at least one transit hole 29 for a relevant main stem 8. With reference to a seventh embodiment shown in Figures 26 to 28, the valve device 6 comprises a single opening/closing element 12 comprising a plurality of transit holes 29.

According to an eighth embodiment shown in Figures 29 to 31, on the other hand, the valve device 6 comprises a plurality of opening/closing elements 12, each fitted on a relevant main stem 8 and provided with a relevant transit hole 29.

The movement means 7 comprise the only return means 21,22 similarly to what has been described for the first embodiment.

The opening/closing element 12 and the main valve 60 are movable from the closing configuration to the opening configuration and from the home configuration to the working configuration respectively, due to the effect of the pressure difference between the transit channel 4 and the working chamber 3. More specifically, when the pressure in the transit channel 4 is greater than the pressure in the working chamber 3, the opening/closing element 12 and the main valve 60 are pushed towards the working chamber 3.

When the two pressures rebalance, the return means 21,22 bring the main valve 60 and the opening/closing element 12 back to the home configuration and to the closing configuration, respectively.

Suitably, the return means 21,22 have a predefined degree of stiffness so as to allow the movement of the main valve 60 and of the opening/closing element 12 at certain pressures.

With reference to the embodiments shown in Figures 26 to 31, the first abutment wall 24 is defined inside the working chamber 3. In more detail, the working chamber 3 comprises a blind channel at the point where a wall of the working chamber itself is located, inside which the first return means 21 are fitted and the base of which defines the first abutment wall 24.

The first return means 21, therefore, are positioned between the main valve 60 and the wall of the working chamber 3.

According to the seventh embodiment, the second abutment wall 28 is defined on the main valve 60.

More in detail, the second abutment wall 28 is defined on the main stem 8. The second return means 22 are, therefore, positioned between the main valve 60 and the opening/closing element 12.

According to the eighth embodiment, the second abutment wall 28 is defined on the wall of the working chamber 3.

The second return means 22, therefore, are positioned between the opening/closing element 12 and the wall of the working chamber 3.

According to a further aspect, the present invention also relates to an appliance provided with at least one valve system 1 according to the invention.

For example, the appliance 2 may be an internal combustion engine, a pump, a compressor, a control valve, a shutoff valve, or any appliance where the regulation of the flow of a fluid is required.

The appliance 2 is provided with at least one working chamber 3 and with at least one transit channel 4 of a fluid communicating with the working chamber 3 through at least one transit opening 5.

Specifically, the transit channel 4 may allow the fluid to flow in or out the working chamber 3.

The appliance 2 may comprise a plurality of valve systems 1.

Specifically, the appliance 2 may comprise a plurality of transit channels 4 afferent to the same working chamber 3 and a plurality of valve systems 1, each associated with a respective transit channel 4.

The appliance 2 may also comprise a plurality of working chambers 3, each communicating with one or more transit channels 4, and a plurality of valve systems 1, each associated with a respective transit channel 4.

It has in practice been ascertained that the described invention achieves the intended objects, and in particular the fact is emphasized that, thanks to the presence of at least one defined gap on the main head and to the possibility of regulating the opening/closing thereof, the present valve system allows optimizing the flow of fluid entering the working chamber at any phase of the operating process. The presence of the gap also makes it possible to increase the flow rate of the flow of fluid entering the working chamber.

Finally, it is also important to point out that the number of gaps and their special conformation and direction allow the present valve system to generate effective turbulence of the flow of fluid in the working chamber, which are able to increase the efficiency of the appliance.

Claims

1) Valve system (1) for the regulation of the flow of a fluid, associable with an appliance (2) provided with at least one working chamber (3) and with at least one transit channel (4) of a fluid communicating with said working chamber (3) through at least one transit opening (5), where said valve system (1) comprises: at least one valve device (6) comprising at least one main valve (60) provided with at least one main stem (8) and with at least one main head (9) having a larger cross-section than said main stem (8), where said main valve (60) is movable between a home configuration, wherein it interacts with said transit opening (5), and at least one working configuration wherein it is displaced towards said working chamber (3) so as to open said transit opening (5); and movement means (7) of said valve device (6) adapted to move at least said main valve (60) between said working configuration and said home configuration; characterized by the fact that said main head (9) is provided with at least one gap (11) for the transit of a portion of said flow of fluid into/from said working chamber (3) and by the fact that said valve device (6) comprises at least one opening/closing element (12) movable with respect to said main valve (60) to open/close said gap (11).

2) Valve system (1) according to claim 1, characterized by the fact that said main head (9) comprises a plurality of said gaps (11), wherein each of said gaps (11) develops along a relevant working axis (W).

3) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main stem (8) extends along a first longitudinal axis (Al) and by the fact that at least one of said gaps (11) develops along a relevant working axis (W) substantially parallel to said first longitudinal axis (Al).

4) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main stem (8) extends along a first longitudinal axis (Al) and by the fact that at least one of said gaps (11) extends along a relevant working axis (W) which is inclined with respect to said first longitudinal axis (Al).

5) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main stem (8) extends along a first longitudinal axis (Al) and by the fact that at least one of said gaps (11) develops along a relevant working axis (W) offset from said first longitudinal axis (Al).

6) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said gaps (11) comprise: at least one first gap (111) developing along a first working axis (Wl) substantially parallel to said first longitudinal axis (Al); and at least one pair of gaps (112,113) each running along a relevant working axis (W2,W3) offset with respect to said first longitudinal axis Al.

7) Valve system (1) according to one or more of the preceding claims, characterized by the fact that the working axes (W2,W3) of said at least one pair of gaps (112,113) are symmetrical to each other with respect to a reference plane (PI) passing through said first working axis (Wl) and said first longitudinal axis (Al).

8) Valve system (1) according to one or more of the preceding claims, characterized by the fact that the working axes (W2,W3) of said at least one pair of gaps (112,113) are incident to each other, respectively.

9) Valve system (1) according to one or more of the preceding claims, characterized by the fact that the working axes (W2,W3) of said at least one pair of gaps (112,113) are incident to each other at one reference plane (PI) passing between said first working axis (Wl) and said first longitudinal axis (Al).

10) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said at least one pair of gaps (112,113) comprises at least one pair of second gaps (112) each developing along a second working axis (W2) and at least one pair of third gaps (113) each developing along a third working axis (W3), inclined with respect to said second working axis (W2).

11) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said second working axes (W2) are incident to each other superiorly to a base plane (B) perpendicular to said reference plane (PI) and passing through the lower end of said main head (9).

12) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said third working axes (W3) are incident to each other inferiorly to a base plane (B) perpendicular to said reference plane (PI) and passing through the lower end of said main head (9).

13) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said second working axes (W2) and said third working axes (W3) are incident to an orthogonal plane (P2) substantially perpendicular to said reference plane (PI) and passing through said first working axis (Wl), superiorly to said base plane (B).

14) Valve system (1) according to claim 7, characterized by the fact that said reference plane (PI) is coincident with a vertical longitudinal plane (L) of said transit channel (4).

15) Valve system (1) according to claim 7, characterized by the fact that said reference plane (PI) is rotated with respect to a vertical longitudinal plane (L) of said transit channel (4), around said first longitudinal axis (Al), by an angle comprised between 20° and 45°.

16) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main head (9) is of a substantially truncated- cone conformation converging towards said main stem (8) and by the fact that said at least one gap (11) is defined at the point where the lateral surface of said main head (9) is located.

17) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said gaps (11) are arranged in a radial pattern with respect to said first longitudinal axis (Al).

18) Valve system (1) according to claim 1 or 2, characterized by the fact that said main stem (8) extends along a first longitudinal axis (Al) and by the fact that said opening/closing element (12) is associated movable by sliding with said main valve (60) along said first longitudinal axis (Al) between a closing configuration, wherein it closes said at least one gap (11), and at least one opening configuration, wherein it opens said at least one gap (11).

19) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main valve (60) is internally hollow and said opening/closing element (12) is arranged internally to said main head (9).

20) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said valve device (6) comprises a secondary valve (13) comprising a relevant secondary stem (14) and a relevant secondary head, wherein said secondary head corresponds to said opening/closing element (12).

21) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said secondary stem (14) extends along a second longitudinal axis (A2) and by the fact that said main stem (8) and said secondary stem (14) are coaxial to each other.

22) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said valve device (6) comprises one or more intermediate valves positioned between said main valve (60) and said secondary valve (13), wherein said valves are arranged one inside the other, and provided with a relevant intermediate stem and with a relevant intermediate head, where on said intermediate head is defined at least one opening for the transit of said fluid, each of said intermediate valves being movable between a relevant home configuration, wherein it obstructs at least partly the gap (11) or the opening of the valve containing it, and at least one relevant working configuration, wherein it allows the transit of said fluid through the gap (11) or the opening of the valve containing it.

23) Valve system (1) according to claim 1, characterized by the fact that said main head (9) defines an inner chamber (25), by the fact that said gap (11) is defined at the point where the longitudinal end of said main head (9) is located and is adapted to place said inner chamber (25) in communication with said transit channel (4) and by the fact that said main head (9) comprises at least one through hole (26) defined on its lateral surface and adapted to place said inner chamber (25) in communication with said working chamber (3), wherein, in said closing configuration said at least one through hole (26) is isolated from said gap (11) and in said opening configuration said at least one through hole (26) is placed in communication with said gap (11).

24) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said movement means (7) comprise first actuating means (15) kinematically connected to said main valve (60) to move it from said working configuration to said home configuration, and comprising at least a first cam (16) movable in rotation around a relevant axis of rotation (R) and adapted to interact with said main valve (60).

25) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said movement means (7) comprise at least mechanical connection means (23) of said opening/closing element (12) to said main valve (60), said mechanical connection means (23) being of an elastic type and being adapted to control the displacement of said opening/closing element (12) between the closing configuration and the opening configuration due to the effect of the inertial forces determined by the acceleration of said main valve (60).

26) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said movement means (7) comprise second actuating means (17) kinematically connected to said opening/closing element (12) to move it from said closing configuration to said opening configuration and comprising at least a second cam (18) movable in rotation around a relevant axis of rotation (R) and adapted to interact with said opening/closing element (12), wherein said first cam (16) and said second cam (18) are locked to each other in rotation around said axis of rotation (R) and have different profiles from each other.

27) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said movement means (7) comprise first return means (21), of the elastic type, adapted to move said main valve (60) towards said home configuration, which are positioned between said main valve (60) and a first fixed abutment wall (24).

28) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said first return means (21) comprise a plurality of first springs (21a) arranged around said main stem (8).

29) Valve system (1) according to claim 28, characterized by the fact that said movement means (7) comprise second return means (22), of the elastic type, adapted to move said opening/closing element (12) towards said closing configuration, which are positioned between said opening/closing element (12) and a second abutment wall (28).

30) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said second return means (22) comprise a plurality of second springs (22a) arranged around said main stem (8).

31) Valve system (1) according to one or more of the preceding claims, characterized by the fact that each of said second springs (22a) is positioned between two of said first springs (21a).

32) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said springs (2 la, 22a) are arranged in a radial pattern with respect to said first longitudinal axis (Al).

33) Valve system (1) according to one or more of the preceding claims, characterized by the fact that at least one of either said opening/closing element (12) or said main valve (60) is movable from the closing configuration to the opening configuration and from the home configuration to the working configuration, respectively, due to the effect of the pressure difference between said transit channel (4) and said working chamber (3).

34) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said main valve (60) is further movable from the home configuration to the working configuration due to the effect of the action of said second return means (22), as a result of the displacement of said opening/closing element (12) towards said opening configuration.

35) Valve system (1) according to one or more of the preceding claims, characterized by the fact that said movement means (7) comprise: at least a first movement assembly kinematically connected to said main valve (60) to move it between said working configuration and said home configuration; and at least a second movement assembly kinematically connected to said opening/closing element (12) to move it between said closing configuration and said opening configuration; wherein said first movement assembly and said second movement assembly are independent of each other.

36) Appliance (2) comprising at least one working chamber (3) and at least one transit channel (4) of a fluid, communicating with said working chamber (3) through a transit opening (5), characterized by the fact that it comprises at least one valve system (1) according to one or more of the preceding claims.