EP2372167B1 - A device for controlling a piloting pressure, in particular of a balance valve. - Google Patents
A device for controlling a piloting pressure, in particular of a balance valve. Download PDFInfo
- Publication number
- EP2372167B1 EP2372167B1 EP20100425101 EP10425101A EP2372167B1 EP 2372167 B1 EP2372167 B1 EP 2372167B1 EP 20100425101 EP20100425101 EP 20100425101 EP 10425101 A EP10425101 A EP 10425101A EP 2372167 B1 EP2372167 B1 EP 2372167B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- opening
- valve
- obturator
- piloting
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/01—Locking-valves or other detent i.e. load-holding devices
- F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
- F15B2211/30515—Load holding valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
Definitions
- the invention relates to a device for controlling a piloting pressure, in particular the piloting pressure of a balance valve.
- the prior art contains hydraulic activating circuits for hydraulic actuators, for example for a cylinder of an arm of a lifting apparatus, in which a first circuit branch connects a hydraulic distributor, in turn associated to a pump, with the chamber of the actuator being associated to the lifting of the load and a second branch connects the distributor with the chamber associated to the descent of the load.
- the circuit is provided with a balance valve predisposed for controlling the fluid flow along the first branch during the descent stage of the load.
- a piloting conduit removes a piloting pressure from the second branch which piloting pressure acts by opening the balance valve during the descent stage of the load.
- chokes have been placed on the piloting conduit. These chokes determine a localised load loss by effect of which the increase in the piloting pressure P PIL commanding the opening of the balance valve is gradual and controlled with respect to the increase in pressure P B in the second branch (i.e. the branch which during the lowering stage of the load is the delivery branch).
- the curve S approximately represents the progress of the piloting pressure P PIL as a function of the pressure P B in the second branch using a choke.
- a drawback of the above-cited known solution is the delay in the activation of the cylinder with respect to the operator's command, especially evident when the operating liquid in the hydraulic circuit is very viscous (for example when cold).
- This delay is due to the presence of the choke and can be schematised in figure 1 by observing that the piloting pressure P PIL reaches value P V of opening of the balance valve (a value predetermined by the calibration of the valve spring) when the delivery pressure P B to the cylinder has already reached a relatively high level P S .
- P V of opening of the balance valve a value predetermined by the calibration of the valve spring
- a check valve is located along the piloting conduit, in parallel with the choke.
- the valve normally open, enables passage of the piloting fluid up to reaching a determined pressure downstream of the valve. On reaching the determined pressure, the valve closes and the piloting fluid flow continues via the choke.
- the presence of the check valve, located in parallel with the choke enables a rapid increase of the piloting pressure in the first stages of sending the piloting signal to the balance valve. In this way, the lowering of the load begins promptly in response to the lowering command.
- the above-described solution exhibits however a not entirely satisfactory aspect.
- the check valve exhibits a certain tendency to closure following pressure peaks or flow peaks along the piloting conduit. As these pressure or flow peaks are rather frequent, so are the closures of the check valve, which undesirably slow down the opening of the balance valve.
- JP 59016022 An example of prior art device suffering the same drawback above is given in JP 59016022 .
- the device comprises a coupling part provided between a load and an actuator.
- the coupling part has a gap acting as a backlash.
- a changeover valve is provided to a hydraulic driving circuit closer to the actuator, a check valve, pressure reducing valve and relief valve are provided successively in front of the changeover valve, and maximum pressure for operating the actuator is set to the relief valve.
- the load does not operate on the pressure reducing valve, but enough pressure to operate the actuator is set.
- the aim of the present invention is to realise a device for control of a piloting pressure of a balance valve which enables reduction of the delay in response of the balance valve or, more in general, of a hydraulically-piloted organ.
- An advantage of the invention is that is provides a device which enables prompt and progressive activation of the piloted organ.
- a further advantage of the invention is to considerably reduce the delay in opening of the balance valve in an activating circuit for a hydraulic actuator and to prevent onset of instability and oscillation phenomena of the valve.
- the hydraulic actuator 9 has a first chamber 10 and a second chamber 11 respectively associated to the raising and lowering of a load 12.
- the activating circuit comprises a hydraulic distributor 13 in turn connected to a source of operating fluid under pressure, typically a pump.
- a first branch 14 connects the distributor 13 with the first chamber 10, while a second branch 15 connects the distributor 13 with the second chamber 11.
- a balance valve 16 is arranged along the first branch 14 to regulate the flow rate of operating fluid which unloads from the first chamber 10 during the descent stage of the load 12.
- a piloting conduit 17 takes from the second branch 15 a piloting pressure which acts to open the balance valve 16.
- the balance valve 16 exhibits a first connection which is connected to the first chamber 10 and a second connection connected to the distributor 13.
- the balance valve has a obturator which is mobile between the open position, in which the first connection is set in communication with the second connection, and a closed position, wherein the first and the second connections are not in communication with one another.
- the obturator of the balance valve 16 is pushed towards the closed position thereof by means of a spring, while it is pushed towards its open position by the force exerted thereon by the pressure exerted by the piloting fluid removed from the second branch 15.
- the balance valve comprises a single-acting valve connected in parallel to the obturator for enabling free flow of the piloting fluid from the second to the first connection.
- the function of the balance valve 16 is to enable, during raising of the load, free flow of the operating liquid to the first chamber 10 of the actuator 9. During the descent of the load, the balance valve 16 controls and limits the flow rate of the operating fluid which unloads from the first chamber 10 towards the distributor 13, such as to slow down the descent of the load.
- the device of the present invention illustrated in figure 2 , is predisposed to be positioned along the piloting conduit 17. It comprises a choke 8, predisposed to be interposed between a piloting fluid source and an organ 16, in particular the balance valve 16, which is activatable by the piloting fluid.
- the device further comprises a pressure reducer valve 2, arranged in parallel with the choke 8, which is normally open and is predisposed to close when the piloting fluid pressure reaches a determined level.
- the reducer valve 2 is provided with an obturator 21 which is mobile between an open position, in which the piloting fluid flow is enabled through the reducer valve 2, and a closed position, in which the piloting fluid flow is not enabled through the reducer valve 2.
- the obturator 21 is pushed towards the open position thereof by effect of the thrust exerted by an elastic element 25, while it is pushed towards the closed position thereof by effect of the thrust exerted by the piloting fluid pressure on a thrust surface 210 of the obturator 21.
- the thrust surface 210 is defined by the front section of the obturator 21, i.e. by the area of the circle delimited by the external edge of the obturator 21.
- the obturator 21 is advantageously conformed and arranged such that the thrust surface 210 is not exposed to the direct flow of the piloting liquid in inlet to the reducer valve 2.
- the thrust surface 210 is exposed directly only to the piloting fluid pressure downstream of the reducer valve 2.
- the conformation of the obturator 21 and the arrangement of the thrust surface 210 are such that any peaks of flow rate and/or pressure of the piloting fluid in inlet to the reducer valve 2 do not have the effect of nudging the obturator 21 towards the closed position.
- the obturator 21 is only subject to the effect of the pressure present downstream of the reducer valve 2, which pressure also acts on the balance valve 16. In this way any peaks of flow rate and/or pressure of the piloting fluid in inlet to the reducer valve 2, as they do not nudge the obturator 21 to closure, do not slow down the flow of the piloting fluid towards the balance valve 16.
- the obturator 21 is sealedly slidable along a longitudinal axis x internally of a seating 22.
- the seating 22 exhibits at least an inlet opening 23, predisposed to be connected to the piloting conduit 17, and at least an outlet opening 24 predisposed to be connected to the balance valve 16.
- the obturator 21 is mobile between at least an open position ( figure 2 ), in which the inlet opening 23 and the outlet opening 24 are in communication and the piloting fluid can flow from the inlet opening to the outlet opening, and at least a closed position ( figure 3 ), in which communication between the inlet opening and the outlet opening is prevented.
- An elastic element 25, preferably a helical spring possible provided with a calibrating organ 26 is predisposed to push the obturator 21 towards the open position. Differently, the pressure downstream of the outlet opening 24, which unloads on the thrust surface 210, pushes the obturator 21 towards the closed position.
- the obturator 21 exhibits a communicating conduit 211 arranged longitudinally and parallel to the sliding direction of the obturator 21.
- the communicating conduit 211 is provided with a first opening 212 and a second opening 213.
- the second opening 213 is set in communication with the outlet opening 24 of the reducer valve 2.
- the first opening 212 in the open position of the obturator 21, is in communication with the inlet opening 23 of the reducer valve 2, such that the inlet opening 23 is in communication with the outlet opening 24 via the first opening 212, the communicating conduit 211 and the second opening 213.
- the first opening 212 In the closed position of the obturator 21, the first opening 212 is not in communication with the inlet opening 23 of the reducer valve 2.
- the first opening 212 is arranged at an annular groove 214 located on the lateral surface of the obturator 21.
- the annular groove 214 delimits, in cooperation with the internal wall of the seating 22, an annular chamber into which the first opening 212 opens.
- the annular chamber In the open position of the obturator 21, the annular chamber at least partly faces the inlet opening 23 of the reducer valve 2, while in the closed position of the obturator 21 the annular chamber is not in communication with the inlet opening 23.
- the first opening 212 develops perpendicular to the communicating conduit 211, such that the piloting fluid coming from the inlet opening 23 of the reducer valve 2 flows internally of the communicating conduit 211 from a transversal direction with respect to the longitudinal development of the communicating conduit 211. In this way, the dynamic effect due to the flow of the piloting fluid in inlet to the communicating conduit 211 is directed perpendicular to the sliding direction of the obturator 21, and the obturator 21 is therefore not pushed to slide.
- the inlet opening 23 and the first opening 212 are substantially facing in the same direction.
- the outlet opening 24 and the second opening 213 are reciprocally aligned.
- the directions of orientation of the inlet opening and the first opening are in turn perpendicular to the orientation direction of the outlet opening and the second opening.
- the special conformation of the obturator 21 is such that the obturator 21 does not suffer from any pressure or flow rate peaks on opening the inlet 23 of the reducer valve 2.
- the displacement of the obturator 21 towards the closed position is determined only by the pressure present at the outlet opening 24 of the reducer valve 2.
- the reducer valve 2 does not perform undesired and unexpected closures, but closes only when the pressure present at the outlet opening 24 reaches a determined value, in particular a value determined by the force exerted by the elastic element 25.
- the elastic element 25 or spring is housed in a low-pressure chamber 27.
- the chamber 27 of the spring 25 is set in communication with the first branch 14 of the circuit connecting the distributor 13 with the first chamber 10 of the actuator 9, which chamber 10 is associated to the raising of the load.
- this branch is normally at low pressure, and the spring chamber of the reducer valve is also at low pressure.
- the eventual presence of pressure in the chamber 27 would raise the calibration value of the reducer valve 2, i.e. the pressure required for determining the displacement of the obturator 21 towards the closed position. This might effectively occur by effect of a pressurised oil flow present in the first branch 14 of the circuit during the descent. In this condition the calibration of the reducer valve 2, i.e.
- the pressure required for displacing the obturator 21 towards the closed position would increase slightly and, consequently, the pressure transmitted to the piloting of the balance valve would also increase, in this way facilitating the opening of the valve.
- the chamber 27 containing the spring 25 might also be ventilated by air.
- a single-acting valve 3 can be interposed between the reducer valve 2 and the balance valve 16, which single-acting valve 3 has a function of enabling flow of the fluid only from the reducer valve 2 towards the piloting of the balance valve 16, while reverse flow is prevented. In this way all unexpected back-flow of the piloting fluid in outlet from the piloting of the balance valve 16 is prevented. This unexpected flow might obtain in a case of a pressure drop in the second branch 15 of the circuit, and might lead to an undesired closing of the balance valve 16.
- the obturator 21 displaces into the closed position and the piloting fluid flow proceeds through the choke 8, such that the piloting pressure P PIL further increases through the choke up to reaching the value P V at which the balance valve 16 opens. Thereafter, on closure of the reducer valve 2, the piloting pressure P PIL increases from value P X to value P V at a smaller inclination with respect to a situation in which the reducer valve 2 is open, as shown by the curve T of figure 1 . This smaller inclination depends on the pressure drop caused by the choke 8.
- the curve S of figure 1 denotes the progress of the piloting pressure P PIL for a control device comprising only the choke 8 but not the reducer valve 2.
- the curve S clearly shows how the piloting pressure P PIL reaches the start value P V of the opening of the balance valve 16 when the pressure P B in the second branch 15 is at a decidedly greater value than the curve T. This means that, thanks to the device of the invention, the balance valve 16 opens decidedly before, such that the lowering of the load follows very rapidly on from the operator's descent command.
- the choke 8 which has the task of stabilising the functioning of the actuator 9 during the descent stage of the load, effectively performs this task even where the passage section is relatively large.
- the choke 8 of the device of the invention can be decidedly more open with respect to a stabilising choke in a device lacking the reducer valve 2. Consequently it can be seen from figure 1 that the inclination of the curve S, relative to a more accentuated choke, is less than the inclination of the second tract of the curve T, which relates to the choke used in the present device, in which P PIL is greater than P X . This enables the operator to have an even more direct and immediate control of the actuator 9, as the response of the actuator 9 is even more prompt for each positional variation of the distributor 13.
- the balance valve 16 the obturator of which has been piloted, i.e. pushed, into the open position by the piloting fluid, has to return to the closed position, sending at least a part of the piloting fluid in discharge.
- the piloting fluid can be discharged only passing through the choke 8, due to the presence of the single-acting valve 3. This might cause an undesired delay in the closure of the obturator of the balance valve 16, and therefore an excessive delay in the halting of the load.
- the device of the present invention can advantageously be provided with a pressure limiter valve 4 arranged in parallel with the choke 8 and the reducer valve 2.
- the limiter valve is provided with an obturator which is mobile between an open position, in which the operating fluid flow through the valve is enabled, and a closed position, in which the flow is not enabled.
- the obturator is pushed towards the closed position by effect of the thrust exerted by an elastic means, while it is pushed towards the open position by the piloting fluid pressure.
- the limiter valve 4 enables the piloting fluid flow only from the balance valve 16 to the second branch 15, while it prevents the reverse flow, and enables flow only if the piloting fluid pressure rises above a determined value corresponding to the thrust exerted by the elastic means. At least a part of the piloting fluid can be rapidly discharge through the limiter valve 4, such as to enable the obturator of the balance valve 16 to displace rapidly towards the closed position thereof, at least for a considerable part of the run towards the closed position.
- the device of the invention can be used for controlling the piloting pressure towards any hydraulically-piloted organ, with the aim of having a very rapid start-up of the piloted organ in response to an external command supplied via the piloting pressure supply.
- the device obviates delays in start-up of the hydraulically-piloted organ while at the same time preventing instability phenomena in the functioning of the piloted organ after start-up.
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- Engineering & Computer Science (AREA)
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Description
- The invention relates to a device for controlling a piloting pressure, in particular the piloting pressure of a balance valve.
- The prior art contains hydraulic activating circuits for hydraulic actuators, for example for a cylinder of an arm of a lifting apparatus, in which a first circuit branch connects a hydraulic distributor, in turn associated to a pump, with the chamber of the actuator being associated to the lifting of the load and a second branch connects the distributor with the chamber associated to the descent of the load. The circuit is provided with a balance valve predisposed for controlling the fluid flow along the first branch during the descent stage of the load. A piloting conduit removes a piloting pressure from the second branch which piloting pressure acts by opening the balance valve during the descent stage of the load.
- In a circuit of this type instability and oscilation phenomena occur in the balance valve on activation of the cylinder for the descent of the load or the inversion of motion thereof. In particular, on lowering the load there can be a frequent succession of blocks and free-ups of the actuator before stabilisation occurs, which causes dangerous oscillation of the load.
- To resolve the problem chokes have been placed on the piloting conduit. These chokes determine a localised load loss by effect of which the increase in the piloting pressure PPIL commanding the opening of the balance valve is gradual and controlled with respect to the increase in pressure PB in the second branch (i.e. the branch which during the lowering stage of the load is the delivery branch). In the diagram of
figure 1 the curve S approximately represents the progress of the piloting pressure PPIL as a function of the pressure PB in the second branch using a choke. - A drawback of the above-cited known solution is the delay in the activation of the cylinder with respect to the operator's command, especially evident when the operating liquid in the hydraulic circuit is very viscous (for example when cold). This delay is due to the presence of the choke and can be schematised in
figure 1 by observing that the piloting pressure PPIL reaches value PV of opening of the balance valve (a value predetermined by the calibration of the valve spring) when the delivery pressure PB to the cylinder has already reached a relatively high level PS. This means that the activation of the cylinder during the lowering stage starts from the moment in which the pressure PB reaches the value PS. The time required for the pressure PB to reached value PS (to which value PV of the piloting pressure PPIL corresponds) can be relatively high, which determines the mentioned delay. - In patent
EP 1178219 the present Applicant provided a satisfactory solution to the technical problem described above. In that solution, a check valve is located along the piloting conduit, in parallel with the choke. The valve, normally open, enables passage of the piloting fluid up to reaching a determined pressure downstream of the valve. On reaching the determined pressure, the valve closes and the piloting fluid flow continues via the choke. The presence of the check valve, located in parallel with the choke, enables a rapid increase of the piloting pressure in the first stages of sending the piloting signal to the balance valve. In this way, the lowering of the load begins promptly in response to the lowering command. - The above-described solution exhibits however a not entirely satisfactory aspect. The check valve exhibits a certain tendency to closure following pressure peaks or flow peaks along the piloting conduit. As these pressure or flow peaks are rather frequent, so are the closures of the check valve, which undesirably slow down the opening of the balance valve.
- An example of prior art device suffering the same drawback above is given in
JP 59016022 - The aim of the present invention is to realise a device for control of a piloting pressure of a balance valve which enables reduction of the delay in response of the balance valve or, more in general, of a hydraulically-piloted organ.
- An advantage of the invention is that is provides a device which enables prompt and progressive activation of the piloted organ.
- A further advantage of the invention is to considerably reduce the delay in opening of the balance valve in an activating circuit for a hydraulic actuator and to prevent onset of instability and oscillation phenomena of the valve. Further characteristics and advantages of the present invention will more fully emerge from the detailed description that follows of some preferred though not exclusive embodiments, which are illustrated purely by way of example in the accompanying figures of the drawings, in which:
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figure 1 is a diagram indicating the piloting pressure PPIL according to the pressure PB in the delivery conduit during the lowering stage of the load, - respectively for a known valve (curve S) and for a valve made according to the invention (curve T);
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figure 2 is a schematic illustration of an embodiment of the invention, combined to an activating circuit for a hydraulic actuator, wherein a pressure reducer valve is in an open configuration; -
figure 3 shows the device offigure 2 in which the pressure reducer valve is in a closed configuration; -
figures 4 and5 show a variant of the device illustrated infigures 2 and3 , wherein the pressure reduction valve is respectively in an open and closed configuration. -
Figure 2 illustrates an activating circuit for ahydraulic actuator 9 which, merely by way of example, is constituted by a cylinder. - The
hydraulic actuator 9 has afirst chamber 10 and asecond chamber 11 respectively associated to the raising and lowering of aload 12. - The activating circuit comprises a
hydraulic distributor 13 in turn connected to a source of operating fluid under pressure, typically a pump. Afirst branch 14 connects thedistributor 13 with thefirst chamber 10, while asecond branch 15 connects thedistributor 13 with thesecond chamber 11. Abalance valve 16 is arranged along thefirst branch 14 to regulate the flow rate of operating fluid which unloads from thefirst chamber 10 during the descent stage of theload 12. A pilotingconduit 17 takes from the second branch 15 a piloting pressure which acts to open thebalance valve 16. - The
balance valve 16, of known type, exhibits a first connection which is connected to thefirst chamber 10 and a second connection connected to thedistributor 13. The balance valve has a obturator which is mobile between the open position, in which the first connection is set in communication with the second connection, and a closed position, wherein the first and the second connections are not in communication with one another. The obturator of thebalance valve 16 is pushed towards the closed position thereof by means of a spring, while it is pushed towards its open position by the force exerted thereon by the pressure exerted by the piloting fluid removed from thesecond branch 15. The balance valve comprises a single-acting valve connected in parallel to the obturator for enabling free flow of the piloting fluid from the second to the first connection. - The function of the
balance valve 16 is to enable, during raising of the load, free flow of the operating liquid to thefirst chamber 10 of theactuator 9. During the descent of the load, thebalance valve 16 controls and limits the flow rate of the operating fluid which unloads from thefirst chamber 10 towards thedistributor 13, such as to slow down the descent of the load. The device of the present invention, illustrated infigure 2 , is predisposed to be positioned along the pilotingconduit 17. It comprises a choke 8, predisposed to be interposed between a piloting fluid source and anorgan 16, in particular thebalance valve 16, which is activatable by the piloting fluid. The device further comprises apressure reducer valve 2, arranged in parallel with the choke 8, which is normally open and is predisposed to close when the piloting fluid pressure reaches a determined level. - The
reducer valve 2 is provided with anobturator 21 which is mobile between an open position, in which the piloting fluid flow is enabled through thereducer valve 2, and a closed position, in which the piloting fluid flow is not enabled through thereducer valve 2. Theobturator 21 is pushed towards the open position thereof by effect of the thrust exerted by anelastic element 25, while it is pushed towards the closed position thereof by effect of the thrust exerted by the piloting fluid pressure on athrust surface 210 of theobturator 21. Thethrust surface 210 is defined by the front section of theobturator 21, i.e. by the area of the circle delimited by the external edge of theobturator 21. - The
obturator 21 is advantageously conformed and arranged such that thethrust surface 210 is not exposed to the direct flow of the piloting liquid in inlet to thereducer valve 2. Thethrust surface 210 is exposed directly only to the piloting fluid pressure downstream of thereducer valve 2. - The conformation of the
obturator 21 and the arrangement of thethrust surface 210 are such that any peaks of flow rate and/or pressure of the piloting fluid in inlet to thereducer valve 2 do not have the effect of nudging theobturator 21 towards the closed position. Theobturator 21 is only subject to the effect of the pressure present downstream of thereducer valve 2, which pressure also acts on thebalance valve 16. In this way any peaks of flow rate and/or pressure of the piloting fluid in inlet to thereducer valve 2, as they do not nudge theobturator 21 to closure, do not slow down the flow of the piloting fluid towards thebalance valve 16. - The
obturator 21 is sealedly slidable along a longitudinal axis x internally of aseating 22. Theseating 22 exhibits at least an inlet opening 23, predisposed to be connected to the pilotingconduit 17, and at least an outlet opening 24 predisposed to be connected to thebalance valve 16. Theobturator 21 is mobile between at least an open position (figure 2 ), in which the inlet opening 23 and the outlet opening 24 are in communication and the piloting fluid can flow from the inlet opening to the outlet opening, and at least a closed position (figure 3 ), in which communication between the inlet opening and the outlet opening is prevented. Anelastic element 25, preferably a helical spring possible provided with acalibrating organ 26 is predisposed to push theobturator 21 towards the open position. Differently, the pressure downstream of the outlet opening 24, which unloads on thethrust surface 210, pushes theobturator 21 towards the closed position. - The
obturator 21 exhibits a communicatingconduit 211 arranged longitudinally and parallel to the sliding direction of theobturator 21. The communicatingconduit 211 is provided with afirst opening 212 and asecond opening 213. - The
second opening 213 is set in communication with the outlet opening 24 of thereducer valve 2. Thefirst opening 212, in the open position of theobturator 21, is in communication with the inlet opening 23 of thereducer valve 2, such that theinlet opening 23 is in communication with theoutlet opening 24 via thefirst opening 212, the communicatingconduit 211 and thesecond opening 213. In the closed position of theobturator 21, thefirst opening 212 is not in communication with the inlet opening 23 of thereducer valve 2. To this end, thefirst opening 212 is arranged at an annular groove 214 located on the lateral surface of theobturator 21. The annular groove 214 delimits, in cooperation with the internal wall of theseating 22, an annular chamber into which thefirst opening 212 opens. - In the open position of the
obturator 21, the annular chamber at least partly faces the inlet opening 23 of thereducer valve 2, while in the closed position of theobturator 21 the annular chamber is not in communication with theinlet opening 23. Thefirst opening 212 develops perpendicular to the communicatingconduit 211, such that the piloting fluid coming from the inlet opening 23 of thereducer valve 2 flows internally of the communicatingconduit 211 from a transversal direction with respect to the longitudinal development of the communicatingconduit 211. In this way, the dynamic effect due to the flow of the piloting fluid in inlet to the communicatingconduit 211 is directed perpendicular to the sliding direction of theobturator 21, and theobturator 21 is therefore not pushed to slide. - The
inlet opening 23 and thefirst opening 212 are substantially facing in the same direction. Theoutlet opening 24 and thesecond opening 213 are reciprocally aligned. The directions of orientation of the inlet opening and the first opening are in turn perpendicular to the orientation direction of the outlet opening and the second opening. - As already mentioned herein above, the special conformation of the
obturator 21 is such that theobturator 21 does not suffer from any pressure or flow rate peaks on opening theinlet 23 of thereducer valve 2. The displacement of theobturator 21 towards the closed position is determined only by the pressure present at the outlet opening 24 of thereducer valve 2. In this way, thereducer valve 2 does not perform undesired and unexpected closures, but closes only when the pressure present at theoutlet opening 24 reaches a determined value, in particular a value determined by the force exerted by theelastic element 25. - The
elastic element 25 or spring is housed in a low-pressure chamber 27. In particular thechamber 27 of thespring 25 is set in communication with thefirst branch 14 of the circuit connecting thedistributor 13 with thefirst chamber 10 of theactuator 9, whichchamber 10 is associated to the raising of the load. During the stages of supporting and lowering the load, this branch is normally at low pressure, and the spring chamber of the reducer valve is also at low pressure. The eventual presence of pressure in thechamber 27 would raise the calibration value of thereducer valve 2, i.e. the pressure required for determining the displacement of theobturator 21 towards the closed position. This might effectively occur by effect of a pressurised oil flow present in thefirst branch 14 of the circuit during the descent. In this condition the calibration of thereducer valve 2, i.e. the pressure required for displacing theobturator 21 towards the closed position, would increase slightly and, consequently, the pressure transmitted to the piloting of the balance valve would also increase, in this way facilitating the opening of the valve. Alternatively to the connection with thefirst branch 14, thechamber 27 containing thespring 25 might also be ventilated by air. - A single-acting
valve 3 can be interposed between thereducer valve 2 and thebalance valve 16, which single-actingvalve 3 has a function of enabling flow of the fluid only from thereducer valve 2 towards the piloting of thebalance valve 16, while reverse flow is prevented. In this way all unexpected back-flow of the piloting fluid in outlet from the piloting of thebalance valve 16 is prevented. This unexpected flow might obtain in a case of a pressure drop in thesecond branch 15 of the circuit, and might lead to an undesired closing of thebalance valve 16. - The functioning of the
reducer valve 2 and the activating circuit of thehydraulic actuator 9 are as follows. - On starting the load lowering stage, i.e. when the
distributor 13 is brought into a configuration in which the operating fluid is sent to thesecond chamber 11 of theactuator 9 through thesecond branch 15, the pressure PB is in thesecond branch 15 is raised, and therefore also in the pilotingconduit 17. The piloting pressure PPIL on connection of piloting of thebalance valve 16 reaches the predetermined value for the opening of the valve in a relatively brief time. This pressure increases rapidly up to the predetermined calibrated pressure of thereducer valve 2, which is normally open. On reaching the predetermined calibrated pressure PX of thereducer valve 2, theobturator 21 displaces into the closed position and the piloting fluid flow proceeds through the choke 8, such that the piloting pressure PPIL further increases through the choke up to reaching the value PV at which thebalance valve 16 opens. Thereafter, on closure of thereducer valve 2, the piloting pressure PPIL increases from value PX to value PV at a smaller inclination with respect to a situation in which thereducer valve 2 is open, as shown by the curve T offigure 1 . This smaller inclination depends on the pressure drop caused by the choke 8. - The curve S of
figure 1 denotes the progress of the piloting pressure PPIL for a control device comprising only the choke 8 but not thereducer valve 2. The curve S clearly shows how the piloting pressure PPIL reaches the start value PV of the opening of thebalance valve 16 when the pressure PB in thesecond branch 15 is at a decidedly greater value than the curve T. This means that, thanks to the device of the invention, thebalance valve 16 opens decidedly before, such that the lowering of the load follows very rapidly on from the operator's descent command. - It has further been observed that the choke 8, which has the task of stabilising the functioning of the
actuator 9 during the descent stage of the load, effectively performs this task even where the passage section is relatively large. In particular, the choke 8 of the device of the invention can be decidedly more open with respect to a stabilising choke in a device lacking thereducer valve 2. Consequently it can be seen fromfigure 1 that the inclination of the curve S, relative to a more accentuated choke, is less than the inclination of the second tract of the curve T, which relates to the choke used in the present device, in which PPIL is greater than PX. This enables the operator to have an even more direct and immediate control of theactuator 9, as the response of theactuator 9 is even more prompt for each positional variation of thedistributor 13. - During the descent manoeuvre it can happen that the load has to be sharply halted, either by a command of the operator or following an eventual fault or breakage of a tube. In order to enable rapid halting, the
balance valve 16, the obturator of which has been piloted, i.e. pushed, into the open position by the piloting fluid, has to return to the closed position, sending at least a part of the piloting fluid in discharge. - For closure of the
balance valve 16, the piloting fluid can be discharged only passing through the choke 8, due to the presence of the single-actingvalve 3. This might cause an undesired delay in the closure of the obturator of thebalance valve 16, and therefore an excessive delay in the halting of the load. - To obviate this delay, the device of the present invention, as illustrated in
figures 4 and5 , can advantageously be provided with a pressure limiter valve 4 arranged in parallel with the choke 8 and thereducer valve 2. The limiter valve is provided with an obturator which is mobile between an open position, in which the operating fluid flow through the valve is enabled, and a closed position, in which the flow is not enabled. The obturator is pushed towards the closed position by effect of the thrust exerted by an elastic means, while it is pushed towards the open position by the piloting fluid pressure. The limiter valve 4 enables the piloting fluid flow only from thebalance valve 16 to thesecond branch 15, while it prevents the reverse flow, and enables flow only if the piloting fluid pressure rises above a determined value corresponding to the thrust exerted by the elastic means. At least a part of the piloting fluid can be rapidly discharge through the limiter valve 4, such as to enable the obturator of thebalance valve 16 to displace rapidly towards the closed position thereof, at least for a considerable part of the run towards the closed position. Although the above description relates to the use of the device in combination with a balance valve, the device of the invention can be used for controlling the piloting pressure towards any hydraulically-piloted organ, with the aim of having a very rapid start-up of the piloted organ in response to an external command supplied via the piloting pressure supply. The device obviates delays in start-up of the hydraulically-piloted organ while at the same time preventing instability phenomena in the functioning of the piloted organ after start-up.
Claims (11)
- A device for controlling a piloting pressure, comprising: a choke (8), predisposed to be interposed between a piloting fluid source and an organ (16) actuatable by the piloting fluid; a valve (2), arranged in parallel to the choke (8), which valve (2) is normally open and is predisposed to close when the piloting fluid pressure reaches a determined value said valve (2) being a pressure reducer valve provided with an obturator (21);
the obturator (21) being mobile between an open position, in which a piloting fluid flow is enabled through the reducer valve (2), and a closed position, in which the piloting fluid flow is not enabled through the reducer valve (2), the obturator being pushed towards the open position thereof by effect of a thrust exerted by an elastic element (25), the obturator being pushed towards the closed position thereof by effect of the thrust exerted by the piloting fluid pressure on a thrust surface (210) of the obturator (21); characterised in that the obturator (21) is conformed and arranged such that the thrust surface (210) is not exposed to the direct flow of the piloting liquid in inlet to the reducer valve (2), the thrust surface (210) being exposed directly only to the piloting fluid pressure downstream of the reducer valve (2). - The device of one of the preceding claims, wherein the obturator (21) is sealedly slidable along a seating (22) which exhibits at least an inlet opening (23) predisposed to receive the piloting fluid, and at least an outlet opening (24), through which the piloting fluid can be sent to the organ (16).
- The device of claim 2, wherein the obturator (21) is mobile between at least an open position, in which the inlet opening (23) and the outlet opening (24) are in mutual communication and the piloting fluid can flow from the inlet opening to the outlet opening, and at least a closed position, in which the communication between the inlet opening and the outlet opening is prevented.
- The device of claim 3, wherein: the obturator (21) exhibits a communicating conduit (211) provided with a first opening (212) and a second opening (213); the second opening (213) is set in communication with the outlet opening (24) of the reducer valve (2); the first opening (212), in the open position of the obturator (21), is in communication with the inlet opening (23), such that the inlet opening (23) is in communication with the outlet opening (24) via the first opening (212), the communicating conduit (211) and the second opening (213); in the closed position of the obturator (21), the first opening (212) is not in communication with the inlet opening (23).
- The device of claim 4, wherein: the inlet opening (23) and the first opening (212) substantially face in a same direction; the outlet opening (24) and the second opening (213) are aligned to one another; the orientation direction of the inlet opening (23) and the first opening (212) are perpendicular to the alignment direction of the outlet opening (24) and the second opening (213).
- The device of claim 5, wherein: the first opening (212) is arranged at an annular channel (214), afforded on the lateral surface of the obturator (21), which delimits, in cooperation with the internal wall of the seating (22), an annular chamber in which the first opening (212) opens; in the open position of the obturator (21), the annular chamber at least partly faces the inlet opening (23); in the closure position of the obturator (21) the annular chamber is not in communication with the inlet opening (23).
- The device of one of the preceding claims, wherein the elastic element or spring (25) is housed in a low-pressure chamber (27).
- The device of claim 7, wherein the chamber (27) of the elastic element (25) is open to air.
- The device of one of the preceding claims, comprising a single-acting valve (3) arranged downstream of the reducer valve (2), which is predisposed to enable flow of the piloting fluid from the reducer valve (2) towards the organ to be piloted (16) and to prevent a reverse flow.
- The device of one of the preceding claims, comprising a pressure limiter valve (4), arranged in parallel to the choke (8) and to the reducer valve (2), which is predisposed to enable the piloting fluid flow in discharge from the organ (16) and to prevent a reverse flow.
- An activating circuit for a hydraulic actuator (9), comprising: a hydraulic cylinder; a first branch (14) predisposed to connect the distributor (13) with a first chamber (10) of the hydraulic actuator (9); a second branch (15) predisposed to connect the distributor (13) with a second chamber (11) of the hydraulic actuator (9); wherein the organ is a balance valve, said balance valve (16) is arranged along the first branch (14) in order to regulate the operating fluid flow in outlet from the first chamber (10) during a lowering stage of the load (12); a choke (8) interposed between the second branch (15) and the balance valve (16); characterised in that it comprises a device for controlling the piloting pressure as in one of the preceding claims, arranged in parallel to the choke (8) between the second branch (15) and the balance valve (16).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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EP20100425101 EP2372167B1 (en) | 2010-03-30 | 2010-03-30 | A device for controlling a piloting pressure, in particular of a balance valve. |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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EP20100425101 EP2372167B1 (en) | 2010-03-30 | 2010-03-30 | A device for controlling a piloting pressure, in particular of a balance valve. |
Publications (2)
Publication Number | Publication Date |
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EP2372167A1 EP2372167A1 (en) | 2011-10-05 |
EP2372167B1 true EP2372167B1 (en) | 2012-11-14 |
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Application Number | Title | Priority Date | Filing Date |
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EP20100425101 Not-in-force EP2372167B1 (en) | 2010-03-30 | 2010-03-30 | A device for controlling a piloting pressure, in particular of a balance valve. |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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CN106050784A (en) * | 2016-08-14 | 2016-10-26 | 宁波市博尔法液压有限公司 | Balance valve |
CN110360174A (en) * | 2019-06-14 | 2019-10-22 | 常德中联重科液压有限公司 | Valve body, valve rod assembly, balanced valve and the flexible control loop of hydraulic cylinder of balanced valve |
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EP2786958B1 (en) * | 2013-04-05 | 2017-06-14 | Bosch Rexroth Oil Control S.p.A. | Control device for the descent of a load |
CN103486105B (en) * | 2013-10-14 | 2016-02-24 | 徐州重型机械有限公司 | A kind of control gear of pilot slide valve |
CN103982482A (en) * | 2014-05-30 | 2014-08-13 | 徐州重型机械有限公司 | Crane, telescopic arm control system of crane and balance valve |
CN108661971B (en) * | 2018-08-22 | 2020-04-17 | 玉环信得利阀业股份有限公司 | Load sensing type flow control balance valve |
CN108953713B (en) * | 2018-08-22 | 2021-09-28 | 宁波威森搏乐机械制造有限公司 | Flow type balance valve |
CN109099023B (en) * | 2018-09-29 | 2020-08-21 | 艾肯(江苏)工业技术有限公司 | Balance valve |
Family Cites Families (6)
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US4523430A (en) * | 1981-03-19 | 1985-06-18 | Daikin Kogyo Co., Ltd. | Fluid flow control system |
JPS5916022A (en) * | 1982-07-16 | 1984-01-27 | Uchida Yuatsu Kiki Kogyo Kk | Backlash removing circuit device |
DE9412530U1 (en) * | 1994-08-03 | 1994-11-10 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Hydraulic damping device |
DE9412531U1 (en) * | 1994-08-03 | 1994-09-29 | Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München | Hydraulic control device |
ATE294332T1 (en) | 2000-08-04 | 2005-05-15 | Oil Control Spa | HYDRAULIC DEVICE FOR CONTROLLING PRIMARY PRESSURE |
US7712482B2 (en) * | 2007-06-07 | 2010-05-11 | Kabushiki Kaisha Kawasaki Precision Machinery | Pressure-reducing valve |
-
2010
- 2010-03-30 EP EP20100425101 patent/EP2372167B1/en not_active Not-in-force
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106050784A (en) * | 2016-08-14 | 2016-10-26 | 宁波市博尔法液压有限公司 | Balance valve |
CN110360174A (en) * | 2019-06-14 | 2019-10-22 | 常德中联重科液压有限公司 | Valve body, valve rod assembly, balanced valve and the flexible control loop of hydraulic cylinder of balanced valve |
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