CONTROLLED RETURN FLOW VALVE FOR HYDRAULIC BRAKING SYSTEMS

Description

DESCRIPTION of the patent for industrial invention from title: “Controlled return flow valve for hydraulic braking systems” in the name of: IRC Srl with 5 headquarters in Genoa, Via Inferiore Riomaggiore 8C, 16138, designated inventor: Giovanni LANDRO of nationality Italian. Technical field 10 This invention relates to a flow valve controlled return particularly suitable, but not uniquely intended for applications within a hydraulic brake system. This valve is can be used advantageously as a drainage element 15 controlled and possibly partially internal of a hydraulic braking circuit. Said finding allowing you to attenuate and compensate for any sudden changes pressure induced by mechanical stress external to the braking system and allowing it 20 timely and safe operation. State of the art Disc brakes are widely used components and used to slow down various types of 25 vehicles proving to be of fundamental importance for the security and control of the same. In line with at most these devices are made up of a disk metal mounted and made integral with the wheel of a half. On the said disk are made to act some 30 so-called tablets, i.e. pieces of material high coefficient of friction that places directly contact with the lateral surfaces of the disc they produce the slowdown by converting the energy kinetics of the medium in dissipated thermal energy. The braking effect due to the pressure of the pads on the disk is typically generated using a device called a caliper that pushes said pads 5 through one or more typically hydraulic pistons. regarding the control and activation of the system braking this usually occurs via a circuit hydraulic or a system of pipes that they transport a pressurized liquid to the clamp 10 through a manual or servo-assisted actuator in generally in the form of a lever and / or pedal with an attached pump hydraulics. Further the hydraulic circuit of a disc brake can have different valves used regulate the flow and facilitate implementation 15 advantageous braking action; said valves including but not limited to non-return valves, as well as check valves control, as well as solenoid valves controlled by a electronic control unit for system activation 20 anti-lock braking system (ABS) or for activation of assisted braking or stability systems vehicle. From the hydraulic point of view, braking occurs when fluid is pumped into the caliper producing 25 expanding the pistons and pressing the pads on the disk. Subsequently, when the user interrupts the braking effect by releasing the pump, a the suction effect of the liquid causes it to retract caliper piston returning it to its position 30 original. The piston retraction is minimal but enough to release the pads from the disc and cancel the braking effect. More precisely said piston retraction defines a gap or clearance between the pads in their resting position and the disc braking. This game is crucial for the correct and balanced functioning of the system because it affects the activation time of the action 5 braking but at the same time affects the correct release and free sliding of the disc when it is not the braking action or the braking action is exerted It just ended. In fact, if the pills were too close to the disk they could slide when the 10 wheel turns, producing permanent wear and tear friction performance and causing wear and overheating progressive. On the other hand, if the pads in their rest position are too far from the disc, increase the running time and therefore the time needed to 15 expand the pistons and bring the pads into contact with the disc inducing the desired braking effect. This is because with the same hydraulic flow rate it will be necessary inject a greater quantity of liquid into the caliper and act in a more intense and prolonged manner on the 20 levers / pedals for the operation before to achieve the necessary braking effect. Identifying the technical problem For the correct functioning of the braking systems, 25 It is crucial that the tablets in current use are kept at a correct and adequate distance of intervention from the disk and that they can be activated quickly and in a reliable and repeatable manner if necessary. As anticipated in the previous paragraph 30 in the current use of braking systems the actuation of the caliper is controlled by the pedal or the lever of the brake that operates a brake pump suitable for pressing on the fluid present in the braking circuit, which transfers pressure to one or more hydraulic pistons housed in the body of the clamp itself which go to press on the back of the pads. This causes a bistable hydraulic equilibrium condition between two 5 braking configurations with impulse pressure exerts load on the clamp and a configuration of brake release and / or rest configuration of the brake with piston retraction and re-housing of the pads within a pre-set intervention threshold. 10 In the face of widespread, consolidated and massive use reasonably reliable disc brakes according to the above mentioned usage pattern is still found today various unresolved issues relating to the above mentioned condition of hydraulic equilibrium between 15 actuation and release of the braking system. In in particular, they are sadly known for the possible severity of the consequences of some problems attributable to pressure changes affecting the hydraulic circuit with impaired effect 20 braking. Among these are the accidental blocking of the braking system or the total or partial loss of braking capacity that can be induced by unwanted mechanical stresses external to the braking system itself which in fact can 25 seriously alter its functioning and effectiveness. It is I note, in fact, that external stresses such as by way of example and not by way of limitation sudden jolts, potholes, collisions with obstacles of the road surface can cause a widening 30 forced and unwanted pads from the disc that they thus tend to move away from the aforementioned position of equilibrium. From the hydraulic point of view these stresses induce compression on the pistons and cause a sudden movement of oil in the opposite direction to the normal operating direction that is, towards the brake pump. This phenomenon it happens because, as anticipated in the previous paragraph, 5 pistons suitable for pressing against the back of the brake pads are usually associated with retraction devices, e.g. gaskets elastic, suitable for quickly retracting the piston in the its cylinder by detaching it from the back of the tablet 10 brake at the end of the braking action and then allowing the pad to move away from the disc. The aim is, as anticipated, to avoid the generation of an unwanted residual braking torque due to a continuous, albeit slight, friction of the pads 15 on the brake disc braking band at the end of braking. Unfortunately, this release system in presence of the aforementioned external stresses on the pills ends up assisting a dangerous and uncontrolled reverse flow of an impulsive nature. 20 This can cause water hammer to occur in the portion of the circuit upstream of the valve, i.e. placed between the valve and the brake pump. This phenomenon in addition to introducing possible damage and / or wear of the hydraulic braking circuit 25 poses a real threat to the safety as it may cause partial or total loss even total braking capacity in particular interfering with the correct functioning of the pump. In fact, if the pads widen 30 moves more oil than its volumetric capacity of the brake pump, this at the next braking, does not will be able to reposition the pads in contact with the disc but it will require more than one run; this is because the normal travel of the brake pump during a common braking action with lever and / or pedal not it will be enough to inject a sufficient amount of liquid to fill / rebalance the circuit 5 hydraulic brake and bring back the detached pads in the contact position with the brake disc. From from the driver's point of view this phenomenon is translates into the classic effect of the pedal and / or brake lever that slide towards the end of the stroke without having any effect 10 braking and in the worst cases with the consequent requires you to act several times on the levers and / or pedals in order to to restore the pumping capacity and above all bring the pads back into contact with the disc, that is, in a position to adequately brake the vehicle. 15 This last case concerns the repeated pumping at the for the purpose of restoring the braking action induces understandably a situation of grave danger for the driving of the vehicle: the driver being unexpectedly with the actuator (lever or pedal) to 20 bottom out, during braking, can get caught from panic, not being ready or accustomed to giving up brake to brake again. This situation occurs in prevalence in car and motorcycle races but also in everyday use due to potholes or bumps. 25 In the previous state of the art, the following have been proposed: various findings that aim to solve the aforementioned technical problem through a distance control between the pads and the brake disc; this control is aimed at to prevent the excessive increase in their distance 30 reciprocal. Among the proposed techniques we recall pressure systems in which a pressure is maintained constant pressure by inserting a pump electric in the braking circuit; this allows for to oppose the so-called reverse flow generated by unwanted stress. Other solutions are instead focus on release and retention systems of the tablets and provide for a variation of the 5 characteristics of elasticity of the piston oil seal of pliers in order to reduce the effect of the brake stresses. In other cases (where (realistically feasible) a reduction of the mass of the brake discs, main 10 responsible for the binding reaction capable of open the pads in case of sudden acceleration axial. Further or using some elastic devices used in conjunction with cylinders and in order to maintain the highest possible level of 15 pads in contact with or near the brake disc. Finally, there are several valve-based solutions hydraulic type that can be inserted into the braking circuit and used as non-return valves, called check valves aiming to prevent the rapid reverse flow of 20 brake fluid. Among these solutions we remember the patent GE2012A000051, patent EP-464389 and the US patent 2003-0127140. They are generally known non-return valves comprising a shutter ball-shaped mobile which, when influenced, tends to place itself in 25 position such as to occlude the passage channel of the valve preventing unwanted flow of return caused by any external stresses that tend to over-widen the pads compared to the disk. Solutions of this type are 30 simple and economical to make, however not are free of drawbacks. In particular, when the mobile ball shutter subjected to effect external impulsive (potholes, bumps, collisions) closes the passage channel of the valve can be determined by the pressures at play in the braking circuit and fluid flow inertia brakes, the formation of a pressure shock wave, 5 also known as water hammer and which in the case of high intensity phenomena can induce damage to the valve or hydraulic circuit overall. The above-mentioned patents and other techniques to the state of the art while mitigating some of the 10 previously mentioned issues related to overpressures and water hammers leave numerous issues still open in terms of reliability and effective restoration of the braking system, particularly the aforementioned problem of the lunge 15 of the levers / pedals at the end of the travel or, even worse, of the multiple and repeated pumping which can become necessary to restore the full capacity of the pump in the face of the aforementioned unwanted flow reverse. Purposes of the invention This patent intends to overcome the above mentioned critical issues of the prior art and provide a solution to them needs complained about in the previous paragraph and in the 25 issues left open by the cited patents. The main objective of the proposed patent is to create a conveniently usable system for prevent the gap between pads and discs from being too large excessive while still ensuring the necessary small gaps 30 in order not to leave the pads in contact with the discs resulting in their overheating or sudden wear of the pads. A further objective of the proposed patent is to to create a system that allows to prevent, or at least strongly limit the formation of strokes of ram or over-pressures affecting the circuit 5 hydraulic and, above all, prevent excessive flow retrograde from the caliper to the brakes on the occasion of unwanted and harmful external stresses such as bumps, jolts, jolts and the like. A further objective of the proposed patent is 10 create a system that can be inserted without modifications invasive and ductile structural (possibly in different places depending on the convenience) of a hydraulic circuit of a brake; said system being adaptable to the brake models 15 existing discs regardless of type (floating, fixed, etc.). A further objective of the proposed patent is create a system with simplified assembly, robust and possibly adjustable according to the changes in the 20 stresses to deal with and variable to depending on the type of final use (motorcycle, automotive, road, track, etc.). A further purpose of the proposed patent is to create a simplified assembly system, 25 robust and characterized by a small number of elements, which do not require electrified parts. Finally, the purpose of the proposed patent is to provide a solution that allows for rapid turnaround times braking system response and full restoration 30 efficiency of the same in the face of disturbances external. Summary of the invention The above mentioned objectives and other purposes which will become clearer later on, they are achieved by a return flow valve 5 controlled with shutter element and passages secondary fluid conveniently usable for hydraulic braking systems according to the claim main 1. Some advantageous forms of implementation and some implementation alternatives are represented 10 from dependent claims. In an advantageous implementation the check valve of controlled flow according to the proposed invention achieves the proposed objectives through a valve characterized by an opening on the pump side and a 15 opening on the clamp side and used to regulate the flow hydraulic passing between said openings. Said valve being usable to allow or limit the flow hydraulic in the two opposite directions of crossing the valve body and being 20 characterized by a plurality of ducts and / or construction measures that can be used separately and / or jointly and such as to allow one or more flows return during the limiting action of the valve. Said return flow or flows being employable 25 individually and / or jointly and being possibly adjustable and / or partially adjustable; said measures allowing simultaneously to ensure a minimum flow rate of the return flow, of ensure a compensatory discharge in case of 30 excessive stresses and to further allow an adaptive regulation of the overall flow rate of the said return flow through a further channel with adjustable flow rate; called multiple system and with variable flow rate allowing the valve to be adapted to different contexts of use and to different types and entities of expected solicitations. More precisely, this system is composed of four 5 main elements that can be used synergistically for obtain a flexible, progressive regulation and compensation of the return flow determined by external disturbances that cause enlargement unwanted caliper pistons. These four 10 items including: • A shutter element in preferably shaped but not exclusively in the form of a sphere; said shutter element being used as 15 non-return valve; called shutter element being capable depending on the direction of the flow inside the valve conduit to pass from two alternative passing positions fluid to the clamp and obstruction with partial 20 return flow. These opposite situations being obtained when said shutter element due to the opposite directions of flow in the valve duct is dragged alternatively towards a perforated ring 25 (i.e. allowing hydraulic flow) or, alternatively, when due to a intense reverse flow goes into a seat of conflict that insists on the portion peripheral of the valve duct and which subsequently 30 upon adhesion of said shutter element comes obstructed in its central passage; • A first duct obtained in the portion peripheral of said clash location and employee to form a secondary minimum passage of fluid between the pump side opening and the opening clamp side of said valve when the element the shutter is in contact with the said striker seat. 5 • A second duct created in the portion peripheral of said clash location and employee to constitute a further secondary passage of fluid between the pump side opening and the opening caliper side of said valve; said second 10 duct being provided with a regulating screw transverse used to reduce the cross-section of passage of the fluid and regulate said second secondary flow passage. • A third fluidic passage consisting of a 15 incomplete duct obtained on the circumference of the collision site or, alternatively, from a scratch made in the contact surface between said element shutter and said striker seat; said third 20 fluid passage allowing for further secondary minimum passage of fluid between the pump side opening and the caliper side opening said valve when said shutter element adheres to the striking surface of the said 25 crash blocking the central passage principal. Brief description of the attached drawings Additional features and benefits of the 30 proposed technical solution, will be more evident in the following description of a form preferred, but not exclusive, implementation represented, by way of example and not limited to limiting, in the three tables of drawings attached in which: • Fig.1 illustrates in axonometric view and 5 front front an embodiment for controlled return flow valve according to the invention; • Fig.2 represents the elements in section main and the operating scheme of the 10 valve according to the proposed invention; • Fig.3 shows a front view of the detail inside of the valve duct with view of the closing shutter element and of the three further fluid passages used for 15 allow a return flow; • Fig.4 illustrates one embodiment of the proposed valve conveniently usable for the insertion of a braking circuit on the caliper side hydraulic; 20 • Fig. 5 illustrates an implementation alternative of the valve conveniently proposed usable for the pump-side insertion of a hydraulic braking circuit; 25 Please note that the figures attached to this document illustrated question are one of the possible forms executives of the system, to better understand its advantages and features described. These executive forms are therefore to be understood as 30 purely illustrative purposes and not limiting the concept inventive, that is, the realization of one or another controlled return flow valve for systems hydraulic brakes that allow you to overcome the issues of prior art, in particular allowing you to preserve the correct and timely operation of the braking capacity when necessary external disturbances that tend to produce 5 the temporary and unwanted removal of the pads from their preferred position proximity to the brake disc. Best way to implement the invention 10 With reference to the attached drawing tables and in particular, Fig.1 illustrates a form of realization of the return flow valve checked (100) for hydraulic braking systems according to the proposed invention. Said valve (100) 15 being conveniently employable for a plurality of types and shapes of braking systems (disc, drum, skate and / or other functional systems equivalents) in which the braking action is controlled by means of a hydraulic circuit. Said circuit 20 hydraulic typically including a brake pump operable by a control device, such as a by way of example and not as a limitation, a brake pedal for motor vehicles or a handlebar control lever for motor vehicles; said drives being used for 25 hydraulically control a braking device, e.g. for example a brake caliper connected to said brake pump by means of connecting pipes. The valve controlled return flow according to the invention proposal being usable at any point of 30 said braking circuit but preferably in proximity to the brake caliper or alternatively in proximity of the brake pump; these alternatives implementation being conveniently described in the followed and represented in Fig.4 and Fig.5 of the drawings attachments. This valve allows you to adjust in both directions (200), (300) the hydraulic flow between said pump and said caliper. 5 With reference to the attached drawings and particularly in Fig.2 the structure is illustrated and the operating scheme of the valve (100) according to the proposed invention. From a structural point of view the valve (100) is characterized by at least one opening 10 pump side (301) and at least one opening on the caliper side (201), said openings being provided respectively of means of connection with a brake fluid supply line coming from the brake pump and means of connection with a pipe 15 of brake fluid flow to the brake caliper. Furthermore the valve comprises at least one conduit valve (101) which connects hydraulically said pump side opening (301) with said pump side opening clamp (201) and regulates the flow passing through the two 20 opposite directions (200), (300). In particular, said valve (100) allowing the fluid present in the hydraulic circuit ducts to flow freely (200) from the pump side opening (301) to the pump side opening clamp (201) and said valve (100) allowing to 25 obstruct by partially limiting the reverse flow (300) from the caliper side opening (201) to the pump side opening (301). This bidirectional flow regulation is realized according to the proposed invention by means of a 30 system similar to a non-return valve however characterized by a reverse passage of minimum. Like a common non-return valve the system provides internal valve conduit (101) the presence of a shutter element (102) in preferably but not necessarily spherical in shape. The said shutter element being capable depending on of the direction and intensity of the flow in the 5 valve duct (101) to pass from two alternative configurations: • a first configuration of the passage of the fluid in the valve duct in the direction from pump to caliper (200); 10 • a second obstruction configuration of the valve duct with reverse flow of minimum from the caliper to the pump (300). The first fluid passage configuration towards the brake caliper is typically determined when 15 the braking system is activated and, as a result of the flow introduced from the pump side opening (301), the shutter element (102) moves towards a seat of strike in the form of a perforated ring (103) and characterized by one or more passages (104) towards 20 the caliper side opening (201). Since said shutter element (102) is characterized by dimensions smaller than the section main valve duct (101) the liquid injected by the pump through the pump-side opening 25 (301) can easily fit into the remaining space between the shutter element (102) and the valve duct (101) and then scroll through the steps (104) in the perforated ring (103), this allowing the flow of brake fluid towards the aforementioned opening 30 caliper side (201). Ultimately when it is carried out the braking action the shutter element (102) goes into hit on the perforated ring (103) and allows the passage of the fluid (200) towards the caliper by starting the braking action. Note that when the brake stops of the braking action the shutter element (102) for the effect of its inertia remains in this position that is, it remains in contact with the said perforated ring nut 5 (103), this allowing that partial suction of the liquid that causes the piston or pistons of the clamps in their resting position. The reverse flow caused by the cessation of the braking action is in fact of modest scope and intensity and not sufficient to 10 interfere with the inertia of the shutter element (102) located in contact with the ring nut (103) and which in this stopping position remains. The reverse flow caused by the natural suction after braking therefore retraces the steps (104) of the ring 15 (103) and the gap between the valve duct (101) and the shutter element (102). The second obstruction configuration of the valve duct (101) with minimum reverse flow from the clamp to the pump (300) is typically determined 20 when due to unwanted external interference tends to produce a sudden, abrupt widening of the caliper pistons. This produces a flow intense and impulsive flow of brake fluid from the caliper at the pump. Under these conditions and as a result of the 25 reverse impulsive flow introduced from the side opening clamp (201), the shutter element (102) is dragged and moves in the opposite direction to the first striking position on perforated ring (103). In In particular, the shutter element (102) moves 30 along the valve duct (101) and comes to a stop towards a collision seat (105) that partially obstructs the section of the valve duct (101) reducing it to a first main fluidic passage (106). In following the adhesion of the element in the abutment shutter (102), called stop seat (105) is blanket causing obstruction to the passage of fluid in said first main fluid passage (106). A 5 By way of example and not as a limitation, it should be noted that, if the shutter element (102) is made of sphere-shaped, as typically occurs in valves of non-return commercial and according to the specimen of realization described in the attached drawings, said 10 the place of conflict (105) may reasonably be consisting of a conical flare with passage central circular section, this allowing to the shutter element to go into position stable and central stop with respect to the duct 15 valve. When due to an impulsive flow and intense directed from the opening on the pliers side (201) towards the pump side opening (301) the shutter element (102) goes into battle on the aforementioned site of collision (105) and the main fluid passage is blocked (106) 20 generating a significant reduction in flow that therefore opposes the impulsive expansion of the pistons. This reduction is as anticipated significant but not complete because in order to avoid damage, jamming and malfunctions at the expense of the 25 braking system the proposed valve (100) allows for to ensure in such circumstances a reverse passage of minimum. Said reverse passage of minimum being made through one or more ducts used as fluid connection passages and allowing the 30 passage of a limited amount of brake fluid between the two openings on the caliper side (201) and the pump side (301) that is, compensating and partializing the effect of obstruction generated by the shutter element (102) when it is in contact with the collision seat (105). These additional connection steps fluidic being obtained in the external portion and 5 peripheral of the collision site (105) i.e. in proximity of the valve duct (101) or alternatively in a position adjacent to the passage main fluidic (106) connecting the two openings (201), (301) mentioned above and being made 10 in the form of conduits which in one embodiment exclusive but not imitative include: • A first duct (107) obtained in the portion peripheral of said collision site (105); said peripheral portion exceeding the overall dimensions 15 of the shutter element (102) when in stop on the said collision site (105). Said first duct (107) being employed to provide a minimal, alternative and secondary passage of fluid between the pump side opening (301) and 20 the opening on the caliper side (201) of said valve (100) when the shutter element (102) is in the stop position on the said collision site (105). • A second duct (108) obtained in the portion peripheral of said collision site (105) and 25 used to form a further step of minimum secondary fluid between the side opening pump (301) and the caliper side opening of said valve (100); said second duct (108) being provided with a regulating grain (109) 30 transverse or of a limitation system of the equivalent flow conveniently employed for reduce the fluid passage section and regulate said second secondary passage of flow for example depending on the circumstances implementation, expected flows and possible external stresses to be compensated for. • A fluidic passage (110) obtained in the 5 contact surface between said element shutter (102) and said striker seat (105); said fluidic passage (110) allowing a further secondary passage of fluid between the pump side opening (301) and the side opening 10 clamp (201) of said valve (100) when said shutter element (102) comes into contact with said collision site (105) obstructing the passage main fluidic (106). 15 With reference to the attached drawings and particularly in Fig.3 the sections are illustrated valve configuration (100) in the above case of obstruction of the valvular conduit with reverse flow minimum from the caliper to the pump. As can be seen 20 when due to a reverse impulsive flow from pump clamp the shutter element (102) stops on the collision site (105) and blocks the passage main fluidic (106) of the valve duct (101) there are three possible ducts (107),(108),(110) of 25 limited section; said ducts being usable either jointly or alternatively according to the invention to generate three draws namely three further minimum fluid passages; called minimum fluid passages being employed for 30 allow for a minimum return flow and mitigate the impulsive and deleterious effects of a reverse flow excessive which could cause blockage of the shutter element (102) on the stop seat (105) and consequently the blocking of the valve (100). The first duct (107) providing a minimum flow rate guaranteed reverse flow, the second duct (108) providing a variable flow rate through grain 5 flow regulator (109). Said two ducts (108), (109) being obtained in the external portion and peripheral of the collision site (105) in the form of passages that allow the fluid connection directly between the pump side opening (301) and the opening 10 caliper side (201). For example and not limited to limiting said passages being obtainable by drilling a hole in the lateral portion of the main passage (106) which exceeds the encumbrance of the shutter element (102). Finally, it is 15 a further fluidic passage is represented in Fig.3 (110) which introduces a leakage near the striking surface between shutter element (102) and site of the clash (105). Said further passage fluidic (110) being obtained on the interface between 20 shutter element (102) and stop seat (105) or, alternatively, be obtained on the sealing seat of the valve (100), in this case licking it and not piercing it along its entire section. Said further fluid passage (110) between the element 25 shutter (102) and the striker seat (105) providing a third additional contribution to the minimum flow rate reverse and generating further leakage that slides between the shutter element (102) and its seat of collision (105) allowing the fluid connection 30 direct between the pump side opening (301) and the opening caliper side (201). This third and further leakage allowing to avoid blockages of the shutter element (102) on the stop seat (105). With reference to the attached drawings and particularly in Fig.4 and Fig.5 are represented 5 two implementation alternatives related to the valve positioning and connection (100) proposed in a hydraulic braking circuit. In in particular, Fig.3 represents the configuration of the valve proposed for insertion and use in 10 proximity of the clamp while Fig.5 illustrates the proposed valve configuration for insertion and use near the pump. These configurations being functionally equivalent and regulating in a similar manner the 15 fluid connection between the pump side opening and the opening on the caliper side but obviously varying for the orientation of the constituent elements and for the means of connection (111), (112) used for the connection on the caliper side and pump side and the pipes 20 fluid connections that insist between pump and caliper. Advantages of the invention The advantages of the invention according to the patent The proposed invention is multiple and evident both in 25 terms of efficiency both in terms of improvement of hydraulic braking systems. The solution proposal resulting conveniently usable as controlled flow element and possibly partially within a braking circuit 30 hydraulic, this allows to prevent excessive removal of the braking elements from their seats operational and ensure the rapid restoration of the full efficiency of the same in the face of disturbances external. Industrial applicability and implementation alternatives 5 While the invention is susceptible of various modifications and alternative constructions, some forms of favorite realizations were shown in the drawings and described in detail in the example of implementation previously illustrated. 10 It must be understood, however, that there is no intention to limit the invention to the specification embodiment illustrated, but, on the contrary, It is intended to cover all modifications, constructions alternatives, and equivalents that fall within the scope 15 of the invention as defined in the claims attached. The use of “for example”, “etc.”, “or” indicates non-exclusive alternatives without limitation unless not otherwise indicated. 20 The use of “include” means “include, but not limited to” unless otherwise indicated. In particular, the invention may be realized with technical equivalents, with materials or devices supplements suitable for the purpose and application area. 25 Conformation and sizing of the parts constituents and products made may vary in an appropriate manner, but consistent with the solution proposal. Any changes to the specimen of 30 proposed realizations, including adjustments and sizing appropriate to specifications and further applications, will be easily deducible from a adequately trained technician in the field and without leaving from the scope of protection of the claimed patent. This without invalidating or eluding the inventive core of the invention and its application to any type of hydraulic braking circuits. 5 The system can further be adapted and further equipped with systems and accessories common use in the application field and also in the availability of a technician in the field and further the possibility of realizing the system is claimed 10 even in partial form. The applicant John LANDRO 15 Legal Representative. IRC SRL (Digitally Signed Document)

Claims

1) Controlled return flow valve (100) for hydraulic braking systems; said valve (100) being used to regulate hydraulic flow in a braking circuit connecting a brake pump to a brake caliper; said valve (100) allowing flow to said brake caliper (200) and limiting, with minimum fluid passage, flow to said brake pump (300); said valve (100) comprising a valve conduit (101) connecting an opening on the brake pump side (301) to an opening on the brake caliper side (201); said valve (100) being characterised by the fact that: a shutter element (102) housed within said valve duct (101) which, depending on the intensity and direction of the hydraulic flow, is capable of moving between: - a first flow position towards the brake pump (300) in which said shutter element (102) abuts on a perforated ring nut (103) provided with at least one passage (104) towards the opening on the brake caliper side (201);- a second position of limited flow towards the brake pump (300) in which said shutter element (102) abuts on a stop seat (105) opposite to said perforated ring nut (103) obstructing the main fluid passage (106) of the valve duct (101) towards said opening on the brake pump side (301); said stop seat (105) comprising at least one duct (107) which runs between the portion of the stop seat (105) not obstructed by the shutter body (102) and the opening on the brake pump side (201).; 2) Valve (100) according to claim 1) wherein said shutter element (102) is a sphere or spheroid and said seat (105) is a conical flare terminating in said main passage (106). 3) Valve (100) according to claim 1) comprising a second conduit (108) running between the portion of the stop seat (105) which is not obstructed by the shutter body (102) and the opening on the brake pump side (200); said second conduit (108) being provided with flow rate adjustment means. 4) Valve (100) according to claims 1) and 3) wherein said flow rate regulation means comprise a regulating screw (109). 5) Valve (100) according to claim 1) comprising a fluid passage (110) obtained on at least one of the two contact surfaces between said shutter element (102) and said contact seat (105); said fluid passage (110) determining a secondary leakage of fluid between said perforated ring nut (103) and said main fluid passage (106) towards the brake pump side (301). 6) Valve (100) according to claims 1) and 5) wherein said fluid passage (110) is obtained by means of scratches, grooves and incisions - 2 made on at least one of said two contact surfaces between said shutter element (102) and said contact seat (105).