Valve for pressurized fluid

Abstract

A valve comprising a valve body having a flow-out pipe, and comprising a valve seat defining a first zone of the flow-out pipe upstream of the valve seat and a second zone of the flow-out pipe downstream of the valve seat, and a cam follower movable with respect to the valve seat along an axis X between an open position, at least one partially open position and a closed position, and comprising a head movable in a fluid-tight manner against an abutment surface of the valve seat, and a bar portion fixedly linked to the head so that a through hole is defined between a lateral surface of the bar portion and an inner surface of the valve seat facing the lateral surface of the bar portion, characterized in that the through hole is equal to a first value A when the cam follower is in said at least one partially open position, and equal to a second value B when the cam follower is in the open position, with B>A.

Description

Technical Field

[0001] This invention relates to valves for pressurizing fluids. Background Technology

[0002] "Soft-opening" type valves are known in the art, that is, valves that open gradually are used for pressurized fluids that are typically contained in suitable containers—such as bottles.

[0003] The first known prior art provides a method for achieving the gradual opening of such a valve by means of throttling the flow rate of the flow itself, which is achieved by means of a mechanism that provides two concentric shut-off valves actuated sequentially by a lever; an example of this solution is, for example, the solution proposed in EP3062005A1.

[0004] However, the geometry of this structure of two concentric valves is complex from the perspective of the number of individual components, the construction and assembly of those individual components, and the maintenance of performance levels over time, both of which are related to the fluid sealing of the valve and the actuation of the valve.

[0005] Furthermore, in EP3062005A1, the gas flow also collides with multiple components of the valve, which are subject to the release of particles. These components include, for example, a compression spring 9 that facilitates the closure of the valve itself. Due to its inherent configuration, the compression spring rotates about itself during compression and relaxation to compensate for dimensional changes. During this rotation, contact friction exists on the corresponding seats, resulting in wear and thus particle formation. When these springs are located in the path of the gas itself, these particles contaminate the gas.

[0006] A second known prior art provides a mechanism comprising two levers. During the opening stroke of the first lever, the first lever actuates a closing system with a very small orifice in a first step. This closing system is calibrated and, due to its small size, allows for throttling of the fluid flow rate. The lever then actuates the closing system on the main valve seat. The travel of the first lever from the first step to the second step is blocked by the second lever. Actuation of the second lever allows the first lever to complete its opening stroke, and thus allows the pressurized fluid to pass through completely at maximum flow rate. An example of this solution is illustrated, for example, in WO2019068970A1.

[0007] A third known prior art provides a mechanism comprising two valves and two levers, the two valves being arranged in series along an outlet pipe, each valve being actuated by a corresponding lever. One of the two valves is capable of throttling the flow rate of the fluid. An example of this solution is illustrated, for example, in WO2019068972A1.

[0008] However, both mechanisms offer a large number of components and provide for operation in two or more steps and through more than one lever for actuation of the mechanism.

[0009] According to the fourth known item of the prior art, as described, for example, in US6607007B1, valve actuation is provided by relative sliding between two surfaces, specifically by relative sliding of one surface—the surface of the valve head—on the inner surface of the valve seat, until a fluid seal for closure is achieved, which in turn also applies to opening. This friction between the two surfaces involves contact friction, which can lead to the formation of particles that can contaminate the gas itself. Furthermore, the valve is particularly susceptible to wear of the sealing gaskets, thereby causing the valve's performance level to deteriorate over time.

[0010] Finally, in this solution, the potential pressure loss increases with the increase of the internal pressure of the bottle.

[0011] Therefore, in the relevant technical field, there is still a need for a valve for pressurized fluids that is improved in terms of the construction and assembly of the individual components and the complexity of their actuation. Summary of the Invention

[0012] The problem to be solved by the present invention is to provide a valve for pressurized fluids that is functionally configured to overcome the limitations of the prior art mentioned above with reference to the referenced prior art.

[0013] In the context of this problem, the object of the present invention is to provide a valve for pressurized fluids that is throttle-open and easy to construct and actuate.

[0014] Another objective is to determine the geometry of the closure with unbalanced surfaces, and the pressure range for separating the closure ensures the fluid seal itself, thereby providing a proportional increase in the separation capability offered by the fluid seal as the pressure increases.

[0015] Another object of the present invention is to provide a valve in which the use of the valve does not cause contamination of the pressurized fluid after friction or wear.

[0016] Finally, an additional object of the present invention is to provide a valve that is particularly safe in potentially dangerous situations, such as impacts on the valve or the bottle connected to the valve, accidental drops of the bottle, and fire.

[0017] The valve of the present invention solves this problem and achieves this objective.

[0018] Therefore, in a first aspect, the present invention relates to a valve for pressurizing fluid, the valve comprising a valve body having an outlet tube for distributing the pressurized fluid, and the valve comprising: A valve seat is disposed in an outlet pipe, and the valve seat defines a first region of the outlet pipe upstream of the valve seat and a second region of the outlet pipe downstream of the valve seat. A cam follower is movable relative to a valve seat along axis X between an open position, at least one partially open position, and a closed position. The cam follower moves relative to the valve seat along axis X to the open position to generate a flow of pressurized fluid discharged from the valve at maximum flow rate; the cam follower moves relative to the valve seat along axis X to the at least one partially open position to throttle the flow of pressurized fluid discharged from the valve; the cam follower moves relative to the valve seat along axis X to the closed position to prevent fluid flow through the pipe, and the cam follower includes: The valve head is movable to abut against the valve seat in a fluid-sealed manner; A rod-shaped part that performs linear motion is fixedly connected to the valve head.

[0019] Preferably, a through hole is defined between the side surface of the rod-shaped portion and the corresponding inner surface of the valve seat, the corresponding inner surface of the valve seat facing the side surface of the rod-shaped portion.

[0020] Preferably, when the cam follower is in the at least one partially open position, the through hole is equal to a first value A; and when the cam follower is in the open position, the through hole is equal to a second value B, wherein B>A.

[0021] Preferably, the abutment surface of the valve seat is located in a plane P orthogonal to the axis X.

[0022] Advantageously, the valve allows movement from a state where no flow passes through the pipe to a state of maximum flow via an intermediate step, in which the flow is throttled. Compared to the prior art, this valve is able to achieve this throttled flow with fewer components and a simpler structure.

[0023] Furthermore, those skilled in the art should understand that this technical solution ensures the fluid tightness of the closure component, which is proportional to the pressure of the bottle. Therefore, the greater the internal pressure of the bottle, the greater the sealing force of the valve itself.

[0024] Another advantage of this technical solution is that any misalignment between the rod-shaped part and the inner surface of the valve seat will not affect the fluid sealing performance of the valve itself.

[0025] Furthermore, since there is no friction between the components that make up the valve itself in the gas outlet pipe, no particles are formed. In this way, the gas maintains its initial purity.

[0026] Advantageously, the value of the throttling can be established during the planning step by changing the geometry that determines the second value A.

[0027] In some embodiments, the abutting surface has a circular crown-shaped portion.

[0028] Preferably, the center of the circular coronal portion is located on the axis X.

[0029] In one implementation, the value A is constant for any intermediate position of the cam follower between the closed and open positions.

[0030] In other words, the cam follower can move relative to the valve seat along axis X between an open position and a closed position, thereby moving through a large number of partially open positions, and for all of the large number of partially open positions, the through hole between the side surface of the rod portion and the corresponding inner surface of the valve seat facing the side surface of the rod portion remains constant.

[0031] In this way, a valve can be constructed in which the throttling value of the flow rate is predetermined and constant during the movement of the cam follower from the closed position to the open position. Preferably, 0 <A<0.1B。

[0032] This means that the valve throttles the fluid flow rate to a value greater than 0 and less than 10% of the fluid flow rate—the total flow rate—when the cam follower is in the open position.

[0033] Preferably, the cam follower is movable relative to the valve seat along axis X between an open position, a partially open position, and a closed position.

[0034] In one embodiment, the cam follower is movable relative to the valve seat along axis X between an open position, a partially open position, and a closed position. The partially open position is configured to throttle the flow rate of the pressurized fluid to a value greater than 0 and less than 10% of the flow rate of the fluid when the cam follower is in the open position.

[0035] The flow rate throttled in this way has the advantage of including the energy associated with fluid expansion. In fact, throttling allows for pressurization of the downstream portion of the valve at a minimal flow rate, and therefore the heat generated during the adiabatic transition of the fluid is extremely limited.

[0036] In this way, spontaneous combustion or deflagration is prevented, which can occur with the rapid expansion of certain types of gases, such as oxygen.

[0037] In one embodiment, the rod-shaped portion includes a first section near the valve head and a second section located away from the valve head, the second section having a radial dimension smaller than that of the first section. The cam follower is movable relative to the valve seat between a closed position, the at least one partially open position, and an open position. In the at least one partially open position, a through-hole is defined between a side surface of the first section of the rod-shaped portion and a corresponding inner surface of the valve seat facing the rod-shaped portion, and the through-hole is equal to a first value A. In the open position, the through-hole is defined between a side surface of the second section of the rod-shaped portion and a corresponding inner surface of the valve seat facing the rod-shaped portion, and the through-hole is equal to a second value B.

[0038] Advantageously, this allows for throttling of fluid flow by properly planning the relative dimensions of the first section of the rod with the inner surface of the valve seat.

[0039] Preferably, the inner surface of the valve seat and the first section of the rod-shaped portion both have a cylindrical and concentric geometry.

[0040] The term "concentric geometry" is intended to be understood as meaning that the axes of the two cylindrical components lie on axis X.

[0041] Advantageously, the geometry allows for easy manufacturing and easy mating between the two parts, while also taking into account any tolerances arising from the machining of the parts or the assembly of the valve itself.

[0042] In one embodiment, a valve head is disposed in a first region upstream of the valve seat, and the valve head is configured to be actuated to close the valve seat by a flow of pressurized fluid flowing through an outlet pipe.

[0043] This technical feature offers the advantage of improved safety for the valve itself.

[0044] In one implementation, when the cam follower is in the closed position, the force that keeps the valve closed is proportional to the pressure of the fluid in a first region upstream of the valve seat.

[0045] In this way, with respect to the valve geometry itself, the fluid tightness of the closure increases with the increase of the pressure of the pressurized fluid upstream of the valve seat. Therefore, from the perspective of inherent safety under conditions of increased danger, the valve improves its performance level.

[0046] In one embodiment, the rod-shaped portion extends slidably through the valve seat between the first and second regions of the outflow tube. Preferably, the valve head is arranged in the first region upstream of the valve seat and is configured to be pushed to close the valve seat by the flow of pressurized fluid flowing through the outflow tube, and the rod-shaped portion extends slidably through the valve seat between the first and second regions of the outflow tube.

[0047] Preferably, the valve includes a first resilient device capable of holding the cam follower in the closed position, and preferably, the first resilient device is located externally relative to the outflow pipe.

[0048] Advantageously, the condition of the first elastic device being located outside the outlet pipe prevents the fluid from being contaminated by any particles formed by friction and wear.

[0049] In one embodiment, these first elastic devices are one or more compression springs, preferably received between an abutment portion disposed on the valve body and an abutment portion disposed in the cam follower.

[0050] Preferably, the abutment portion provided on the valve body is internal.

[0051] Preferably, the abutment portion provided on the cam follower is external.

[0052] Preferably, these first elastic devices are compression springs, with the rod-shaped portion slidably received within the compression spring.

[0053] In one embodiment, the valve includes an actuation device for moving a cam follower relative to a valve seat between a closed position, the at least one partially open position, and an open position, preferably located externally relative to the outlet pipe.

[0054] This technical feature also prevents the fluid from being contaminated by any particles formed due to friction and wear.

[0055] Preferably, these actuation devices are manual control devices, including, for example, buttons or levers.

[0056] In one embodiment, these actuation devices include a rod and an eccentric connector, the rod being connected to a cam follower by means of the eccentric connector, such that rotation of the rod about a hinge axis Y causes the cam follower to move linearly relative to the valve seat along axis X between a closed position, the at least one partially open position, and an open position.

[0057] This allows for easy control of valve opening so that both the throttled flow rate and the full flow rate of the pressurized fluid can be obtained through the valve itself.

[0058] Preferably, the eccentric connector is a cam, the profile of which causes the cam follower to move relative to the valve seat between a closed position, at least a partially open position, and an open position.

[0059] Preferably, the cam follower includes a connecting element located between the actuating device and the rod-shaped portion, which is typically a spherical or wheel-shaped element.

[0060] This allows wear caused by repeated use of the actuator on the cam follower to be limited.

[0061] Preferably, the bonding element is made of molten material.

[0062] This advantageously involves the fact that, in the event of a fire, there is no longer any motion transmission from the actuating device to the cam follower.

[0063] In one embodiment, the lever is rotatable about the hinge axis Y by an angle α. When the lever rotates by 0°, the cam follower is in the closed position; when the lever rotates by an angle greater than 0° and less than or equal to α / 2°, the cam follower is in the at least one partially open position; and when the lever rotates by an angle greater than α / 2° and less than α°, the cam follower is in the open position.

[0064] Preferably, the cam has a profile portion having at least a first portion, a second portion, and a third portion. The second portion has an arcuate profile centered on the hinge axis Y and having a radius a. The third portion has an arcuate profile centered on the hinge axis Y and having a radius b, wherein b > a. The first portion corresponds to a rotation of the rod by an angle equal to 0°, wherein the cam follower is in the closed position. The second portion corresponds to a rotation of the rod by an angle greater than 0° and less than or equal to α / 2°, wherein the cam follower remains in the open position of the at least one portion. The third portion corresponds to a rotation of the rod by an angle between an angle greater than α / 2° and an angle less than or equal to α°, wherein the cam follower remains in the open position.

[0065] Preferably, the second part corresponds to the rotation of the rod through an angle greater than 0° and less than α / 2°, and a first connecting part is provided between the second and third parts of the cam profile, such that: during the rotation of the rod from an angle less than α / 2° to an angle greater than α / 2°, a force greater than the force required for the rotation of the rod from 0° to α / 2° and from α / 2° to α° needs to be applied at an angle equal to α / 2°.

[0066] This involves: an operator being able to perceive and control the travel of pressurized fluid from a throttled flow state to a maximum flow state during the opening of the valve.

[0067] Preferably, a second connecting portion and a breakable shank are disposed between the third portion and the first portion of the profile of the cam, the connecting portion having an arcuate profile centered on the hinge axis Y and having a radius c, where c < b, and the breakable shank is located between the second connecting portion and the first portion, such that: when the lever is rotated through an angle greater than α°, the breakable shank breaks and the cam follower moves from the open position to the closed position.

[0068] Advantageously, this allows further increasing the safety of the valve. In fact, in the event that the lever is rotated by an angle of approximately greater than α°, for example due to an impact or a force applied by the operator, the breakable shank breaks, for example, the breakable shank breaks after colliding with a protruding element of the valve, and the cam follower returns to the closed position.

[0069] In one embodiment, the valve comprises at least one element, preferably the valve comprises two elements, for: moving the cam follower into the closed position when the lever is rotated through an angle between 0° and α / 2° and is not manually held; and placing the cam follower in the open position when the lever is rotated through an angle between α / 2° and α° and is not manually held.

[0070] Advantageously, this relates to a bistable lever, and this further increases the safety of the valve, if the operator releases the lever itself, in the case where the lever has been rotated by an angle of approximately between 0° and α / 2, the valve automatically moves to the closed state; in the case where the lever has been rotated by an angle between α / 2° and α°, the valve automatically moves to the open state.

[0071] Preferably, said at least one element is a resilient device, more preferably, said at least one element is a tension spring, said at least one element is fixed at a first end to the eccentric motion member at a position not coinciding with the hinge axis Y of the lever, and said at least one element is connected at a second end to the cam follower.

[0072] In one embodiment, the eccentric motion member is a cam, and said at least one element is two tension springs, said two tension springs are hinged at first ends to two opposite side portions of the cam, such that the hinged positions of the tension springs relative to the cam define a hinge axis Z that is eccentric with respect to the hinge axis Y.

[0073] This embodiment is particularly balanced from the perspective of balancing the bistable mechanism and ease of construction.

[0074] In one embodiment, when the lever rotates through an angle greater than α°, the two traction springs bring the cam follower to the closed position.

[0075] In a preferred embodiment, the valve includes two traction springs and a compression spring. The two traction springs are hinged at their first ends to opposite sides of the cam, such that the hinge position of the traction springs and the cam defines an eccentric hinge axis Z relative to the hinge axis Y. The compression spring is received between an abutment portion disposed on the valve body and an abutment portion disposed in the cam follower. When the lever rotates by an angle of approximately greater than α°, the compression spring and the two traction springs bring the cam follower to the closed position.

[0076] In one embodiment, the valve head has a seat for receiving a fluid sealing element. When the cam follower is in the closed position, the seat is movable to abut against an abutment surface of a valve seat, which is spaced apart from the abutment surface and configured such that, in the absence of a fluid sealing element, the valve head can travel a maximum stroke L along axis X until the seat abuts against the abutment surface of the valve seat. When the cam follower is in the closed position, the actuator and the cam follower are spaced apart by a distance D such that D ≥ L.

[0077] Advantageously, this allows the valve to close when the fluid sealing element is no longer installed, or when the fluid sealing element is damaged, for example, after a combustion event. Attached Figure Description

[0078] The features and advantages of the present invention will be better understood from the detailed description of preferred embodiments of the invention shown by way of non-limiting example with reference to the accompanying drawings, in which: - Figure 1 This is a schematic diagram of a valve with a rod; - Figure 2 This is a schematic cross-section showing details of a valve according to the invention, wherein the cam follower is in the open position; - Figure 3 This is a schematic cross-section of a valve according to the present invention, wherein the cam follower is in the closed position; - Figure 4 This is a detailed cross-section of the valve according to the invention, wherein the cam follower is in a partially open position; - Figure 5 This is a schematic cross-section showing details of a valve according to the invention, wherein the cam follower is in the closed position; - Figure 6 This is a schematic cross-section showing details of the valve according to the invention, wherein the rotation angle of the rod is greater than α°. - Figure 7This is a schematic three-dimensional cross-section of the valve according to the invention, wherein the rotation angle of the rod is greater than α°, and - Figure 8 This is a schematic perspective view of the valve according to the present invention. Detailed Implementation

[0079] Referring to the accompanying drawings, the valve according to the present invention is generally indicated by 1.

[0080] Figure 1 A valve 1 for pressurizing fluid is shown. The valve 1 typically includes: a lever 91 for opening and closing the valve itself; an inlet 1a configured for connection to a container for containing the pressurized fluid, such as a gas cylinder; and an outlet 1b configured for connection to a device capable of receiving the fluid. The valve 1 typically preferably includes a display 200.

[0081] Figure 2 A schematic cross-sectional view depicting the details of the valve according to the invention is shown.

[0082] In the most common sense of valve 1, valve 1 may include valve body 2 and valve seat 4, valve body 2 receiving outflow pipe 3, and valve seat 4 arranged in the outflow pipe 3 itself to define a first region 3a of the outflow pipe 3 upstream of valve seat 4 and a second region 3b of the outflow pipe 3 downstream of valve seat 4.

[0083] The valve also has a cam follower 5, which can move relative to the valve seat 4 along axis X between an open position, a partially open position, and a closed position.

[0084] The valve body 1 also has a hole 3c located on the axis X, which extends between the second region 3b and the region 3d outside the outlet pipe 3.

[0085] In the open location ( Figure 2 In the partially open position, pressurized fluid flows through valve seat 4 in outlet pipe 3 at a maximum flow rate B. This maximum flow rate B is determined by the geometry of valve 1 itself when cam follower 5 is in the open position and the pressure of the fluid upstream of valve 1. Figure 4 In the valve seat 4, pressurized fluid flows through pipe 3 at a flow rate that has a defined value A, is less than the maximum flow rate, and is determined by the geometry of valve 1 itself when cam follower 5 is in the partially open position and by the pressure of the fluid upstream of valve 1. However, in the closed position ( Figure 3 In the valve 1 outlet pipe 3, there is no fluid flow at all.

[0086] The cam follower 5 includes a valve head 51, which is received in a first region 3a upstream of the valve seat 4 in the outlet pipe 3. The valve head 51 is configured to be pushed by the pressurized fluid flow in the outlet pipe 3 to close the valve seat 4. Thus, the valve head 51 moves in a fluid-tight manner to abut against the abutment surface 4a of the valve seat 4 and prevent fluid flow through the valve 1.

[0087] The abutment surface 4a lies within a plane P orthogonal to the axis X, such as... Figure 3 As can be seen, the abutting surface 4a has a circular crown shape that extends through the axis X itself.

[0088] The cam follower also includes a rod-shaped portion 52 that moves linearly along axis X. The rod-shaped portion 52 is fixedly connected at one end to valve head 51 and slides through valve seat 4 via orifice 3c between first region 3a and second region 3b of outlet pipe 3 and between second region 3b and region 3d outside outlet pipe 3. A suitable fluid sealing element 31 ensures that fluid is prevented from traveling through orifice 3c.

[0089] By controlling the movement of the cam follower 5 along the axis X, the rod-shaped part 52 slides through the hole 3c and the valve seat 4, so that the valve head 51 abuts against the abutment surface 4a of the valve seat 4, thereby preventing pressurized fluid from flowing through the outlet pipe 3, or, so that the valve head 51 is in a position away from the valve seat 4 itself, thereby allowing the fluid itself to flow in the outlet pipe 3.

[0090] If it is possible Figure 2 and Figure 3 As seen in the image, the rod-shaped portion 52 has a first portion 521 and a second portion 522. The first portion 521 has a cylindrical geometry and is fixedly connected to the valve head 52. The second portion 522 is located at a position farther from the valve head 51. The second portion 522 has a radial dimension smaller than that of the first portion 521.

[0091] The valve seat 4 includes an inner surface 4b with a cylindrical geometry between the first region 3a and the second region 3b of the outlet pipe 3, and the corresponding side surface 52a of the rod-shaped portion 52 faces the inner surface 4b.

[0092] A through hole 6 is defined between the inner surface 4b of the valve seat 4 and the corresponding side surface 52a of the rod-shaped portion 52.

[0093] When the first segment 521 engages with the inner surface 4b of the valve seat 4 ( Figure 4 The cam follower 5 is in the partially open position, and when the first section 521 does not engage with the inner surface 4b of the valve seat 4—therefore the inner surface 4b of the valve seat 4 engages with the second section 522 ( Figure 2 When engaged, the cam follower 5 is in the open position.

[0094] Therefore, when the first segment 521 of the rod-shaped portion 52 faces the inner surface 4b of the valve seat, the through hole 6 has a first value A, and when the second segment 522 of the rod-shaped portion 52 faces the inner surface 4b of the valve seat, the through hole 6 has a second value B.

[0095] Since the second segment 522 has a smaller radial dimension than the first segment 521, B>A.

[0096] This means that when the orifice 6 has a value of A, the flow rate of the pressurized fluid is throttled relative to the maximum flow rate, while when the orifice 6 is equal to a value of B, the pressurized fluid has the maximum flow rate.

[0097] Reference Figure 2 At the opposite end of the valve head 51, the cam follower 5 has an outer abutment portion 5a. The valve body 2 also has an inner abutment portion 2a. A compression spring 8a is provided between the two abutment portions 5a and 2a, which slides to receive the rod-shaped portion 51 and pushes the cam follower 5 to the closed position.

[0098] Specifically, the compression spring 8a receives the following portion of the rod-shaped part 51: this portion is located in a position opposite to the valve head 51 relative to the hole 3c of the valve body 2; therefore, the spring 8a is located outside relative to the outlet pipe 3, and is therefore no longer covered by the fluid flow flowing through the outlet pipe 3.

[0099] A suitable fluid sealing element 31 prevents pressurized fluid from traveling from the outlet pipe 3 to the compression spring 8a.

[0100] In the closed position, such as Figure 3 As shown and clearly visible, cam 92a is spaced apart from cam follower 5 by a distance equal to the value D.

[0101] The valve head 51 has a seat 51a in which a fluid sealing element 511 is received. When the cam follower 5 is in the closed position, the fluid sealing element 511 moves to abut against the abutment surface 4a of the valve seat 4.

[0102] The valve seat 4 is spaced apart from the abutting surface 4a of the valve seat 4.

[0103] The valve seat 4 and valve head 51 are configured such that, without the fluid sealing element 511, the valve head 51 can travel a maximum stroke L along the axis X until the seat portion 51a abuts against the abutment surface 4a of the valve seat 4.

[0104] Since D≥L, in the event of damage to the fluid sealing element 511, the cam follower 5 moves along axis X until valve 1 is closed.

[0105] Valve 1 also has a rod 91 that is hinged around the hinge axis Y, such that it can be Figure 1 , Figure 7 and Figure 8 As seen in the image, rod 91 can rotate by an angle α.

[0106] The lever 91 is connected to the cam 92a located outside the outlet pipe 3, and the lever 91 controls the movement of the cam follower 5 relative to the valve seat 4 along the axis X between the closed position, the partially open position, and the open position via the cam 92a.

[0107] Specifically, when lever 91 rotates by an angle equal to 0°, cam follower 5 is in the closed position; when lever 91 rotates by an angle equal to an angle greater than 0° and less than or equal to α / 2°, cam follower 5 is in the partially open position; when lever 91 rotates by an angle equal to an angle greater than α / 2° and less than or equal to α°, cam follower 5 is in the open position.

[0108] like Figures 2 to 8 As shown, the cam follower 5 includes a spherical member 53 located between the cam 92a and the rod-shaped portion 52, which is made of a fusible material.

[0109] This technical feature enables its application to other types of valves according to the invention.

[0110] like Figure 8 As shown, the valve also includes two traction springs 10a, which are hinged at a first end 101a to opposite sides of the cam 92a, such that the hinged position of the traction springs 10a and the cam 92a defines a hinge axis Z, which is eccentric relative to the hinge axis Y of the rod 91, and the two traction springs 10a are hinged at a second end 101b to the cam follower 5.

[0111] These traction springs 10a operate in conjunction with the specific geometry of the cam 92 shown below, such that the lever 91 is bistable, meaning that when the lever 91 rotates by an angle between approximately 0° and α / 2° and is not manually held, the cam follower 5 is brought back to the closed position; when the lever 91 rotates by an angle between approximately α / 2° and α and is not manually held, the cam follower 5 is in the open position.

[0112] This technical feature enables its application to other types of valves according to the invention.

[0113] like Figure 5As shown, the cam 92a has the following profile portion 100: in the rotational opening direction of the lever 91, the profile portion 100 sequentially has a first part 101, a second part 102, a first connecting part 104, a third part 103, a second connecting part 105 and a breakable handle portion 106.

[0114] When the rotation angle of lever 91 is equal to 0°, cam 92a exposes the first part 101 to cam follower 5 so that cam 92a and cam follower 5 do not contact each other. Therefore, there is no motion transmission from cam 92 to cam follower 5101. Cam follower 5 is held in the closed position by compression spring 8a and traction spring 10a.

[0115] In this situation, if the bottle equipped with the valve is subjected to dangerous overheating, the melting of the ball 53 will cause the valve to no longer be able to be opened, and thus the valve will remain in a stable closed position.

[0116] When lever 91 moves from a rotation angle of 0° to an angle of α / 2°, cam 92a exposes the second portion 102 to cam follower 5. The second portion 102 has an arcuate profile centered on the hinge axis Y and has a radius a. The contact between cam 92a and cam follower 5 makes the movement of cam follower 5 controlled in terms of movement from the closed position to the partially open position. Cam follower 5 remains in this state until the cam exposes the second portion 102 to cam follower 5. That is, for any angle between 0° and α / 2°, the cam exposes the second portion 102 to cam follower 5.

[0117] When lever 91 moves from a rotation angle equal to α / 2° to an angle between α / 2° and α°, cam 92 exposes the third portion 103 to cam follower 5. The third portion 103 has an arcuate profile centered on the hinge axis Y and has a radius b. Cam 92 and cam follower 5 are in contact; however, since b > a, cam follower 5 is controlled in its movement from the partially open position to the open position. Cam follower 5 remains in this state until the cam exposes the third portion 103 to the cam follower. That is, for any angle between α / 2° and α°, the cam exposes the third portion 103 to the cam follower.

[0118] Between the second portion 102 with radius a and the third portion 103 with radius b — where b>a — there is provided a first connection portion 104 corresponding to a rotation angle of the rod 91 equal to α / 2°, such that: when the rod is controlled in rotation to rotate from an angle smaller than α / 2° to an angle larger than α / 2°, the operator has to apply a peak force, so that the operator can identify and control the movement of the valve by himself from a state where fluid is dispensed at a throttled flow rate to a state where fluid is dispensed at a maximum flow rate.

[0119] This technical feature also enables application to other types of valves of the valve according to the present invention.

[0120] Between the third portion 103 and the first portion 101 of the profile portion 100 of the chamber 92a, a second connection portion 105 and a breakable shank 106 are sequentially disposed. The second connection portion 105 has an arcuate profile and a radius c, the center of the second connection portion 105 is located on the hinge axis Y, where c<b, such that the cam follower 5 is controlled in its movement to the closed position. Therefore, when the rod 91 is forced to rotate to an angle greater than α ( Figure 6 and Figure 7 ), the breakable shank 106 strikes the protruding element 3e of the valve 1, thereby rupturing at the position 106a, the cam 92a exposes the second connection portion 105 to the cam follower 5, and the cam follower 5 is moved into the closed position by the two tension springs 10a and by the compression spring 8a.

[0121] This technical feature also enables application to other types of valves of the valve according to the present invention.

[0122] Naturally, to meet specific and possible application requirements, those skilled in the art may make additional modifications and variations to the above invention, which still fall within the scope of protection defined by the appended claims.

Claims

1. A valve (1) for pressurizing fluid, the valve (1) comprising a valve body (2) having an outlet pipe (3) for distributing pressurized fluid along a flow direction from inlet (1a) to outlet (1b), and the valve (1) comprising: - A valve seat (4), the valve seat (4) being disposed in the outlet pipe (3), and the valve seat (4) defining a first region (3a) of the outlet pipe (3) upstream of the valve seat (4) relative to the flow direction and a second region (3b) of the outlet pipe (3) downstream of the valve seat (4) relative to the flow direction, and - A cam follower (5) movable relative to the valve seat (4) along axis X between an open position, at least one partially open position, and a closed position; the cam follower (5) moving relative to the valve seat (4) along axis X to the open position to generate a flow of pressurized fluid discharged from the valve (1) at maximum flow rate; the cam follower (5) moving relative to the valve seat (4) along axis X to the at least one partially open position to throttle the flow of pressurized fluid discharged from the valve; the cam follower (5) moving relative to the valve seat (4) along axis X to the closed position to prevent the pressurized fluid from flowing through the outlet pipe (3), and the cam follower (5) comprising: - Valve head (51), which is movable to abut against the abutment surface (4a) of the valve seat (4) in a fluid-sealed manner. - A rod-shaped portion (52) that performs linear motion, the rod-shaped portion (52) being fixedly connected to the valve head (51), such that: a through hole (6) is defined between the side surface of the rod-shaped portion (52) and the corresponding inner surface (4b) of the valve seat (4), the corresponding inner surface (4b) of the valve seat (4) facing the side surface of the rod-shaped portion (52), When the cam follower (5) is in the at least one partially open position, the through hole (6) is equal to a first value A; and when the cam follower (5) is in the open position, the through hole (6) is equal to a second value B, where B > A. The valve (1) further includes an actuation device (9) for moving the cam follower (5) relative to the valve seat (4). The actuation device (9) is located externally relative to the outlet pipe (3) and includes a rod (91) and an eccentric connector (92). The rod (91) is rotatable about a hinge axis Y by an angle α° and is connected to the cam follower (5) by means of the eccentric connector (92) such that rotation of the rod (91) about the hinge axis Y causes the cam follower (5) to move linearly relative to the valve seat (4) along the axis X between the closed position, the at least one partially open position, and the open position. The eccentric connector (92) is characterized in that it has a contour portion (100), the contour portion (100) having at least a first part (101), a second part (102) and a third part (103), the second part (102) having an arc-shaped contour centered on the hinge axis Y and having a radius a, the third part (103) having an arc-shaped contour centered on the hinge axis Y and having a radius b, wherein b>a; the first part (101) is rotated relative to the rod (91) at an angle of 0°. The cam follower (5) is in the closed position; the second part (102) corresponds to the rotation of the rod (91) through an angle greater than 0° and less than or equal to α / 2°, wherein the cam follower (5) remains in the at least one part open position; and the third part (103) corresponds to the rotation of the rod (91) through an angle between an angle greater than α / 2° and an angle less than or equal to α°, wherein the cam follower (5) remains in the open position.

2. The valve according to claim 1, wherein, The first value A is constant for any intermediate position of the cam follower (5) between the closed position and the open position.

3. The valve according to claim 1 or 2, wherein, The valve head (51) is arranged in the first region (3a) upstream of the valve seat (4), and the valve head (51) is configured to be pushed by the flow of the pressurized fluid in the outlet pipe (3) to close the valve seat (4).

4. The valve according to claim 1 or 2, characterized in that, When the cam follower (5) is in the closed position, the force that keeps the valve closed is proportional to the pressure of the pressurized fluid in the first region (3a) upstream of the valve seat (4).

5. The valve according to claim 1 or 2, wherein, 0 < A < 0.1B.

6. The valve according to claim 1 or 2, wherein, The rod-shaped portion (52) includes a first section (521) near the valve head (51) and a second section (522) located away from the valve head (51), and the second section (522) has a smaller radius than the first section (521). The cam follower (5) is movable relative to the valve seat (4) between the closed position, the at least one partially open position, and the open position. In the at least one partially open position, the through hole (6) is defined on the side surface of the first section (521) of the rod-shaped portion (52) and the valve seat (521). 4) Between the corresponding inner surfaces (4b) of the valve seat (4), wherein the corresponding inner surface (4b) of the valve seat (4) faces the side surface of the rod-shaped portion (52), and the through hole (6) is equal to the first value A. In the open position, the through hole (6) is defined between the side surface of the second segment (522) of the rod-shaped portion (52) and the corresponding inner surface (4b) of the valve seat (4), wherein the corresponding inner surface (4b) of the valve seat (4) faces the side surface of the rod-shaped portion (52), and the through hole (6) is equal to the second value B.

7. The valve according to claim 1 or 2, wherein, The rod-shaped portion (52) extends through the valve seat (4) in a sliding manner between the first region (3a) and the second region (3b) of the outflow pipe (3).

8. The valve according to claim 1 or 2, the valve comprising a first resilient device (8) capable of holding the cam follower (5) in a closed position, the first resilient device (8) being located externally relative to the outflow pipe (3).

9. The valve according to claim 8, wherein, The first elastic device (8) is one or more compression springs (8a).

10. The valve according to claim 9, wherein, The compression spring (8a) is received between the abutment portion disposed on the valve body (2) and the abutment portion disposed in the cam follower (5).

11. The valve according to claim 1 or 2, wherein, The eccentric connector (92) is a cam (92a) whose profile causes the cam follower (5) to move relative to the valve seat (4) between the closed position, the at least one partially open position, and the open position.

12. The valve according to claim 1 or 2, wherein, The cam follower (5) includes a coupling element (53) located between the actuation device (9) and the rod-shaped portion (52).

13. The valve according to claim 12, wherein, The bonding element is made of molten material.

14. The valve according to claim 1 or 2, wherein, Said second portion (102) corresponds to a rotation of said lever (91) through an angle greater than 0° and less than α / 2°, and a first connecting portion (104) is provided between said second portion (102) and said third portion (103) of said profile portion (100) of said eccentric connector (92), such that: during the rotation of said lever (91) from an angle less than α / 2° to an angle greater than α / 2°, a force greater than the force required for the rotation of said lever (91) from an angle of 0° to an angle of α / 2° and the rotation of said lever (91) from an angle of α / 2° to an angle of α° needs to be applied at the angle equal to α / 2°.

15. The valve according to claim 14, wherein, A second connecting portion (105) and a breakable shank (106) are provided between said third portion (103) and said first portion (101) of said profile portion (100) of said eccentric connector (92), said second connecting portion having an arcuate profile centered on the hinge axis Y and having a radius c, where c<b, and said breakable shank (106) is located between said second connecting portion (105) and said first portion (101), such that: when said lever (91) rotates through an angle greater than α°, said breakable shank (106) breaks and said cam follower (5) moves from the open position to the closed position.

16. The valve as claimed in claim 1 or 2, comprising at least one element (10), said at least one element (10) being configured to: move said cam follower (5) into the closed position when said lever (91) rotates through an angle between 0° and α / 2° and is not manually held; and keep said cam follower (5) in the open position when said lever (91) rotates through an angle between α / 2° and α° and is not manually held.

17. The valve as claimed in claim 1 or 2, comprising two elements, said two elements being configured to: move said cam follower (5) into the closed position when said lever (91) rotates through an angle between 0° and α / 2° and is not manually held; and keep said cam follower (5) in the open position when said lever (91) rotates through an angle between α / 2° and α° and is not manually held.

18. The valve according to claim 16, wherein, Said at least one element (10) is an elastic device, said at least one element (10) being fixed to the eccentric connector (92) at a first end (101a) at a position not coinciding with said hinge axis Y of said lever (91), and said at least one element (10) being connected to said cam follower (5) at a second end (101b).

19. The valve according to claim 18, wherein, Said elastic device is a tension spring (10a).

20. The valve according to claim 19, wherein, The eccentric connector (92) is a cam (92a), and the at least one element (10) is two traction springs (10a) that are hinged at the first end (101a) to opposite sides of the cam (92a) such that the hinge position of the traction springs (10a) and the cam (92a) determines the eccentric hinge axis Z relative to the hinge axis Y.

21. The valve according to claim 20, wherein, When the rod rotates through an angle greater than α°, the two traction springs (10a) bring the cam follower (5) to the closed position.

22. The valve according to claim 1 or 2, wherein, The valve head (51) has a seat (51a) for receiving a fluid sealing element (511), the seat (51a) being movable to abut against the abutment surface (4a) of the valve seat (4) when the cam follower (5) is in the closed position, the seat (51a) being spaced apart from the abutment surface (4a) of the valve seat (4) and configured such that: in the absence of the fluid sealing element (511), the valve head (51) is able to travel a maximum stroke L along the axis X until the seat (51a) abuts against the abutment surface (4a) of the valve seat (4), and when the cam follower (5) is in the closed position, the actuating device (9) and the cam follower (5) are spaced apart by a distance D such that D≥L.

23. The valve according to claim 1 or 2, wherein, The contact surface (4a) is located in a plane (P) orthogonal to the axis X.

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