EP2834544B1 - Load holding valve - Google Patents
Load holding valve Download PDFInfo
- Publication number
- EP2834544B1 EP2834544B1 EP13723239.3A EP13723239A EP2834544B1 EP 2834544 B1 EP2834544 B1 EP 2834544B1 EP 13723239 A EP13723239 A EP 13723239A EP 2834544 B1 EP2834544 B1 EP 2834544B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- piston
- seat
- opening
- zone
- 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.)
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Links
- 239000012530 fluid Substances 0.000 claims description 64
- 239000008186 active pharmaceutical agent Substances 0.000 description 5
- 238000007789 sealing Methods 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- 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
Definitions
- the invention relates to a load-holding valve traversed by a pressurized fluid.
- the load-holding valves are piloted valves that are typically employed in the field of the earthmoving machines. These valves are arranged for holding suspended loads being also very heavy, such as, for example, an excavator articulated arm, as well as for keeping the above-mentioned loads suspended in a desired position for a preset time interval.
- valves are fed and traversed by a pressurized fluid, which is sent to an actuator, generally a double-action hydraulic piston, which in turn is connected to the arm to be supported.
- actuator generally a double-action hydraulic piston
- the known valves comprise a main channel, extending longitudinally along a valve body, inside which various known components - among which a piston and a seat are received, both being longitudinally movable - arranged to permit or prevent the passage of the pressurized fluid as a function of their mutual arrangement.
- a plurality of openings is obtained in the valve body, each of which is in communication with the main channel through a respective duct, and it is arranged to permit said pressurized fluid entering in or exiting from the valve. Therefore, the known valves comprise a first opening and a second opening through which, in a lifting step of the load, the pressurized fluid respectively enters the valve body and exits from the latter to reach the actuator. On the contrary, in a lowering step of the load, the pressurized fluid enters the valve through the second opening and exits the valve through the first opening.
- the flow of the pressurized fluid - when the latter has its typical operative pressures - from the second opening towards the first opening would not, however, be permitted due to the mutual arrangement of the above-mentioned known components.
- the suspended load When the suspended load has to be lowered, it is then provided to pilot the valve, so as to permit the fluid reaching the valve from the actuator exiting through the first opening.
- piloting step further pressurized fluid is delivered into the valve body through a piloting opening, which further pressurized fluid acts on the piston and pushes it in such a position as to permit the above-mentioned fluid flow from the second opening to the first opening.
- a thrust force further acts, which is exerted by the pressurized fluid flow entering the valve through the second opening.
- the piloting force exerted on the piston by the further pressurized fluid is concordant with the above-mentioned thrust force, so that both the above-mentioned forces are able to overcome an elastic force that is opposite them and that is exerted by a spring on the piston.
- valves comprising a seat and a piston interacting together in order to allow or prevent the passage of fluid therebetween are known, for example, from US 2011/101772 or US 2009/065727 .
- a drawback of the known valves is that they lack safety devices to block the movement of the suspended load in the case of breakages or structural failures of a valve component, particularly, the spring.
- the latter In use, the latter is very stressed and therefore, it may occur that one or more spring coils are damaged, for example, at surface cracks that cause the successive spring breakage.
- the elastic force exerted by the spring on the piston suddenly ceases, and the piloting and thrust forces are not opposed anymore.
- the piston is consequently kept far away from the seat, and the passage for the pressurized fluid flow from the second opening to the first opening remains open therebetween. Consequently, the suspended load suddenly and quickly lowers, until the hydraulic piston reaches the end stroke position.
- An object of the invention is to improve known piloted valves.
- Another object is to provide a load-holding valve that allows blocking the movement of the suspended load, if the spring acting on the piston in opposition to the piloting force and the thrust force of the pressurized fluid flow breaks.
- a further object is to provide a load-holding valve in which it is possible to compensate for pressure increases of the fluid entering the valve to avoid corresponding speed increases during the lowering of the suspended load.
- a load-holding valve as defined in claim 1 is provided.
- the valve 1 comprises a body 2 provided with a plurality of openings through which the pressurized fluid can enter, or exit from, the valve 1. Therefore, these openings enable the valve 1 to be connected to a oleodynamic circuit of a machine (not shown), for example, an earthmoving machine.
- a first opening 3, a piloting opening 4, and a second opening 5 are visible, the function of which will be explained in detail herein below.
- a cavity 8 is made in the body 2, extending in a substantially parallel manner to a first longitudinal axis A of the valve 1.
- the cavity 8 comprises a plurality of portions having, for example, a substantially cylindrical transversal section. The portions have diameters different from one another and are made in sequence along the axis A.
- the valve 1 lacks the safety valve 10.
- the second channel 5a is not a through channel, or it is closed by a closing member, such as, for example, a threaded plug.
- this version of the valve lacks the connection channel 26.
- the valve 1 comprises a containing element 16, partially received inside the cavity 8 and partially projecting outside the valve body 2.
- the containing element 16 is fixed to the body 2 through a threaded connection 17.
- a thread is made on an external side wall portion of the containing element 16, which thread is arranged to couple with a respective thread formed on an internal side wall of the cavity 8.
- the containing element 16 is internally hollow, so as to define a chamber 61 inside it.
- the piston 30 comprises a head portion 32, which is enclosed inside the containing element 16, an intermediate portion 33, and an end portion 34.
- the intermediate portion 33 has a transversal dimension that is less than the head portion 32 and the end portion 34.
- a connecting portion 52 is interposed, arranged near the end 21, and comprising a first zone 52a and a second zone 52b, having an approximately frusto-conical shape ( Fig. 3 ).
- first zone 52a and the second zone 52b can be shaped in a different manner, while maintaining a transverse dimension greater than the adjacent head portion 32 and intermediate portion 33.
- a spring 41 is housed, acting on a centering member 42 pressing on the piston 30, particularly on a bottom wall of the head portion 32.
- the centering member 42 is substantially conical-shaped, i.e., it is shapingly coupled with the above-mentioned bottom wall, and it ensures that the elastic force F EL exerted by the spring 41 on the piston 30 is balanced, i.e., substantially directed along the axis A.
- the spring 41 is pre-loaded, and it is kept compressed by a thrust member 43, which is fixed to the internal side wall of the containing element 16 by a threaded coupling 67. On the thrust member 43, a plug 44 is screwed, by acting on which an operator can adjust the spring 41 preload.
- a movable seat 22 is further received in the cavity 8, which is shaped as a bush, and thus it is internally hollow, arranged near the end 21 of the containing element 16 and the connecting portion 52.
- the seat 22 comprises an internal wall 22a, defining an internal maximum transverse dimension D S of the seat 22 and facing the piston, and an external wall 22b, contacting the walls of the cavity 8. ( Fig. 3 )
- An annular seat 23 is made in the external wall 22b, in which a second sealing member 24 ( Fig. 3 ) is housed, which enables the passage of the pressurized fluid to be prevented outside the seat 22.
- the seat 22 surrounds the piston 30, particularly near the second zone 52b and the part of intermediate portion 33 contiguous thereto. Therefore, according to the position of the piston 30, the latter can completely occlude, or not, a passage zone A s for the pressurized fluid, which is interposed between the seat 22 and the piston 30. More precisely, the passage zone A s is overall defined by the seat 22 and the piston 30 when the second zone 52b does not contact, i.e., it is spaced apart from, the internal wall 22a of the seat 22, thus enabling the passage of the pressurized fluid from the second channel 5a towards the first channel 3a. On the contrary, when the second zone 52b contacts the internal walls of the seat 22, the passage zone A s is absent, and the passage of the pressurized fluid from the second channel 5a towards the first channel 3a is prevented.
- the spring 25 can be arranged outside the movable seat 22.
- the end portion 34 of the piston 30 is received in a portion of the cavity 8 having substantially the same radial dimension.
- the end portion 34 has a maximum transverse dimension D P and comprises a piloting face 37 ( Fig. 2 ).
- the further pressurized fluid entering the valve 1 from the piloting opening 4 during the piloting step acts on the piloting face 37.
- the end portion 34 further comprises an annular face 47, which is frustoconical-shaped. The annular face 47 is opposite the piloting face 37 and it faces the intermediate portion 33.
- the end portion 34 abuts on a shoulder 60 (shown in Fig. 2 ) of the cavity 8 and the connecting portion 52 contacts the seat 22.
- a groove is made, which acts as a seat for a third sealing member 35, for example, an O-ring.
- the piloting face 37 has the maximum transverse dimension Dp that is greater than the internal maximum transverse dimension D S of the internal wall 22a of the movable seat 22. Since the movable seat 22 is interposed between the connecting portion 52 and the end portion 34 of the piston 30, the latter comprises a first part 30a and a second part 30b joined together, for example through a threaded connection ( Figures 1 and 2 ). In this manner, since the internal maximum transverse dimension D S is less than both the radial extension of the connecting portion 52, and the maximum transverse dimension D P of the piloting face 37, it is possible to correctly assembly the valve 1 by arranging the seat 22 and the piston 30 in the manner shown in the Figs. 1-3 .
- the first part 30a is first positioned by inserting the head portion 32 inside the containing element 16, then the movable seat 22 and the spring 25 are positioned, finally the second part 30b is positioned, which is screwed to the first part 30a.
- the safety valve 10 of a known type, is a maximum pressure valve detecting the fluid pressure in the second channel 5a (i.e., of the fluid arriving near to the intermediate zone 33) and it opens if the above-mentioned pressure exceeds a predetermined threshold value.
- a predetermined threshold value is a value set by the user acting on adjustment means with which the safety valve 10 is provided, and it can be equal to 350 bars.
- the safety valve 10 opens, and a portion of the above-mentioned fluid enters the connection channel 26 to subsequently reach the piloting channel 4a. In the latter, the above-mentioned portion of the fluid traverses the dowel 6, with consequent pressure drop in the fluid.
- the piloting step is not controlled by the operator, but it is automatically started by the valve 1 owing to the presence of the safety valve 10.
- valve 1 The operation of the valve 1 is described herein below, with particular reference to the case in which the latter is comprised in an earthmoving machine.
- the pressurized fluid for example an oil provided with suitable chemical-physical characteristics, enters the valve 1 through the first opening 3 communicating with the cavity 8 through the first channel 3a.
- the pressurized fluid traverses the passage zone As and it can flow, inside the movable seat 22, towards the second channel 5a.
- the fluid exits the body 2 and moves towards actuating means (not illustrated), which is comprised in the machine and which, in this manner, is actuated to lift the load.
- valve 1 When the load has to be lowered, the valve 1 is initially in the first operative configuration K and the pressurized fluid exiting from the actuating means enters the valve 1 through the second opening 5. The flow of this fluid causes the movable seat 22 to move in the direction X until abutting on the end 21 of the containing element 16 ( Fig. 2 ).
- a volume of further pressurized fluid enters the body 2 and flows in the piloting channel 4a.
- This fluid exerts a thrust action - i.e., a piloting force F P represented by an arrow in Fig. 3 - on the piston 30, particularly on the end portion 34 of the latter.
- the piston 30 begins to move in the direction X so that the second frusto-conical zone 52b moves away from the internal wall 22a.
- the piston 30 moves inwards the containing element 16, so that the connecting portion 52 does not abut anymore on the end 21 of the containing element 16.
- the passage zone A S is defined, and the half-circular passages made in the end 21 are not closed by the connecting portion 52 anymore.
- the pressurized fluid entering from the second opening 5 can thus traverse the passage zone As and the above-mentioned half-circular passages - after flowing in the second channel 5a and a portion of the first cavity 8 (inside the seat 22) - to exit subsequently the body 2 of the valve 1 through the first opening 3.
- the piston 30 is moved in the direction Y by the thrust action of the spring 41, the elastic force F EL of which is not opposed anymore by the piloting force F P due to the pressurized fluid in the piloting channel 4a.
- the connecting portion 52 of the piston 30 abuts again on the end 21 of the containing element 16 and the fi-usto-conical second zone 52b is in contact with the movable seat 22, thus interrupting the connection between the first opening 3 and the second opening 5.
- the elastic force F EL , the thrust force F S , and the piloting force F P are shown, all of which being substantially parallel to the longitudinal axis A.
- the elastic force F EL and the thrust force F S are concordant and push the piston 30 in the direction Y, while the piloting force F P , opposite the other two, pushes the piston 30 in the direction X.
- the pressurized fluid entering the second channel 5a is distributed in the valve 1 so that it acts on both the annular face 47 of the end portion 34, and on a portion 46 of the frusto-conical second zone 52b positioned inside the seat 22 when the valve 1 is in the operative configuration K ( Fig. 3 ), i.e., when the connecting portion 52 contacts the seat 22.
- the area of the annular face 47 is greater than the area of the portion 46, and therefore the resulting thrust force F S is directed so as to oppose the piloting force F P .
- the valve 1 is able to adjust the flow rate of the pressurized fluid entering the valve 1 through the second opening 5a and exiting the valve 1 through the first opening 3a, i.e., during the lowering step of the suspended load.
- the valve 1 can be associated to any machine or apparatus, even different from an earthmoving machine.
- a load-holding valve 1 which allows blocking the movement of the suspended load (for example the arm of an earthmoving machine) in the case of a breakage of the spring 41.
- a load-holding valve 1 is provided in which it is possible to compensate for pressure increases of the fluid entering the valve from the actuating means (through the second channel 5a) to avoid corresponding speed increases during the lowering of the suspended load. This is achieved owing to the orientation of the force F S that tends to push the piston 30 in the direction Y, so as to avoid that the passage zone As becomes excessively large, so as to adjust the flow rate of pressurized fluid entering the valve through the second opening 5a and exiting the valve through the first opening 3a.
- This adjustment of the fluid flow rate is automatically performed by the valve 1, as described above, and it is therefore an accurate and reliable adjustment of the fluid flow rate.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Temperature-Responsive Valves (AREA)
Description
- The invention relates to a load-holding valve traversed by a pressurized fluid.
- The load-holding valves are piloted valves that are typically employed in the field of the earthmoving machines. These valves are arranged for holding suspended loads being also very heavy, such as, for example, an excavator articulated arm, as well as for keeping the above-mentioned loads suspended in a desired position for a preset time interval.
- These valves are fed and traversed by a pressurized fluid, which is sent to an actuator, generally a double-action hydraulic piston, which in turn is connected to the arm to be supported.
- The known valves comprise a main channel, extending longitudinally along a valve body, inside which various known components - among which a piston and a seat are received, both being longitudinally movable - arranged to permit or prevent the passage of the pressurized fluid as a function of their mutual arrangement.
- A plurality of openings is obtained in the valve body, each of which is in communication with the main channel through a respective duct, and it is arranged to permit said pressurized fluid entering in or exiting from the valve. Therefore, the known valves comprise a first opening and a second opening through which, in a lifting step of the load, the pressurized fluid respectively enters the valve body and exits from the latter to reach the actuator. On the contrary, in a lowering step of the load, the pressurized fluid enters the valve through the second opening and exits the valve through the first opening. In use, the flow of the pressurized fluid - when the latter has its typical operative pressures - from the second opening towards the first opening would not, however, be permitted due to the mutual arrangement of the above-mentioned known components. When the suspended load has to be lowered, it is then provided to pilot the valve, so as to permit the fluid reaching the valve from the actuator exiting through the first opening.
- In the piloting step, further pressurized fluid is delivered into the valve body through a piloting opening, which further pressurized fluid acts on the piston and pushes it in such a position as to permit the above-mentioned fluid flow from the second opening to the first opening. On the piston, particularly on the piston zone cooperating with the seat in which the passage for the pressurized fluid is defined, a thrust force further acts, which is exerted by the pressurized fluid flow entering the valve through the second opening.
- In the piloting step, the piloting force exerted on the piston by the further pressurized fluid is concordant with the above-mentioned thrust force, so that both the above-mentioned forces are able to overcome an elastic force that is opposite them and that is exerted by a spring on the piston.
- Known valves comprising a seat and a piston interacting together in order to allow or prevent the passage of fluid therebetween are known, for example, from
US 2011/101772 orUS 2009/065727 . - A drawback of the known valves is that they lack safety devices to block the movement of the suspended load in the case of breakages or structural failures of a valve component, particularly, the spring. In use, the latter is very stressed and therefore, it may occur that one or more spring coils are damaged, for example, at surface cracks that cause the successive spring breakage. When this occurs, the elastic force exerted by the spring on the piston suddenly ceases, and the piloting and thrust forces are not opposed anymore. The piston is consequently kept far away from the seat, and the passage for the pressurized fluid flow from the second opening to the first opening remains open therebetween. Consequently, the suspended load suddenly and quickly lowers, until the hydraulic piston reaches the end stroke position.
- The sudden and quick lowering of the suspended load can be dangerous for anything being present in the surrounding environment, which can be hit or impacted by the load. Therefore, it is apparent that this is certainly to be avoided, for both preserving people's safety, and for not damaging, even severely, objects such as, for example, machineries, buildings, etc.
- Another drawback of the known valves is that they are not able to control and adjust in a safe and effective manner the lowering step of the suspended load, particularly when the latter is running the final length of its stroke. As the suspended load is inclined, the pressure of the fluid entering the valve from the second opening increases, being able to reach values that are even significantly high. This causes a consequent increase of the thrust force on the piston by the above-mentioned fluid, which causes the lowering speed of the suspended load to considerably increase. This effect is particularly unwanted by the operators, since it makes the lowering operation of the suspended load more complex to be controlled.
- An object of the invention is to improve known piloted valves.
- Another object is to provide a load-holding valve that allows blocking the movement of the suspended load, if the spring acting on the piston in opposition to the piloting force and the thrust force of the pressurized fluid flow breaks.
- A further object is to provide a load-holding valve in which it is possible to compensate for pressure increases of the fluid entering the valve to avoid corresponding speed increases during the lowering of the suspended load.
- According to the invention, a load-holding valve as defined in
claim 1 is provided. - The invention will be able to be better understood and implemented with reference to the appended drawings, which show an exemplary, non-limiting embodiment thereof, in which:
-
Fig. 1 is a longitudinal section of a valve according to the invention, illustrated in a first operative configuration; -
Fig. 2 is a section as the one ofFig. 1 , in which the valve is illustrated in a second operative configuration; -
Fig. 3 is an enlarged schematic view of a piston and a seat comprised in the valve ofFig. 1 , in which the forces acting on the piston are highlighted. -
Figs. 1-3 show apiloted valve 1 in a first operative configuration K (Figs. 1 and3 ) and in a second operative configuration J (Fig. 2 ). - The
valve 1 comprises a body 2 provided with a plurality of openings through which the pressurized fluid can enter, or exit from, thevalve 1. Therefore, these openings enable thevalve 1 to be connected to a oleodynamic circuit of a machine (not shown), for example, an earthmoving machine. In particular, afirst opening 3, a pilotingopening 4, and asecond opening 5 are visible, the function of which will be explained in detail herein below. - A
cavity 8 is made in the body 2, extending in a substantially parallel manner to a first longitudinal axis A of thevalve 1. Thecavity 8 comprises a plurality of portions having, for example, a substantially cylindrical transversal section. The portions have diameters different from one another and are made in sequence along the axis A. - The
first opening 3 is connected to thecavity 8 by means of afirst channel 3a, the pilotingopening 4 is connected to thecavity 8 by means of a pilotingchannel 4a, and thesecond opening 5 is connected to thecavity 8 by means of asecond channel 5a. The latter is a through channel connecting two opposite walls of the body 2, and it is closed - on an opposite side to the second opening 5 - by asafety valve 10, the function of which will be explained in more detail herein below. The pilotingchannel 4a comprises afirst portion 4b, which is orthogonal to the axis A, and asecond portion 4c, communicating with thefirst portion 4b and leading into thecavity 8. Thefirst portion 4b may comprise adowel 6 arranged for being traversed by the pressurized fluid. Thevalve 1 further comprises aconnection channel 26 allowing connecting the pilotingchannel 4a with thesecond channel 5a when the safety valve 10 (interposed therebetween) is in the open position. - In a non-illustrated version, the
valve 1 lacks thesafety valve 10. In this case, thesecond channel 5a is not a through channel, or it is closed by a closing member, such as, for example, a threaded plug. Furthermore, this version of the valve lacks theconnection channel 26. - The
valve 1 comprises a containingelement 16, partially received inside thecavity 8 and partially projecting outside the valve body 2. The containingelement 16 is fixed to the body 2 through a threaded connection 17. A thread is made on an external side wall portion of the containingelement 16, which thread is arranged to couple with a respective thread formed on an internal side wall of thecavity 8. The containingelement 16 is internally hollow, so as to define achamber 61 inside it. - Externally to the containing
element 16, asecond sealing member 20 is arranged, for example, an "O-ring" in polymeric material, which enables thecavity 8 to be sealingly closed. The containingelement 16 is provided with aninternal end 21, on which a plurality of passages is made. The passages are shaped as half-circular recesses, and they are obtained in sequence on an end edge of theend 21, which is shaped as a hollow cylinder. Thevalve 1 further comprises apiston 30, extending in a substantially parallel manner to the first longitudinal axis A and being received inside thecavity 8. The approximatelycylindrical piston 30 is bidirectionally movable according to the directions indicated by the arrows X and Y, parallel to the axis A. Thepiston 30 comprises ahead portion 32, which is enclosed inside the containingelement 16, anintermediate portion 33, and anend portion 34. Theintermediate portion 33 has a transversal dimension that is less than thehead portion 32 and theend portion 34. Between thehead portion 32 and theintermediate portion 33, a connectingportion 52 is interposed, arranged near theend 21, and comprising afirst zone 52a and asecond zone 52b, having an approximately frusto-conical shape (Fig. 3 ). - In other embodiments, not illustrated, the
first zone 52a and thesecond zone 52b can be shaped in a different manner, while maintaining a transverse dimension greater than theadjacent head portion 32 andintermediate portion 33. - In the
chamber 61 of the containing element 16 aspring 41 is housed, acting on a centeringmember 42 pressing on thepiston 30, particularly on a bottom wall of thehead portion 32. The centeringmember 42 is substantially conical-shaped, i.e., it is shapingly coupled with the above-mentioned bottom wall, and it ensures that the elastic force FEL exerted by thespring 41 on thepiston 30 is balanced, i.e., substantially directed along the axis A. Thespring 41 is pre-loaded, and it is kept compressed by athrust member 43, which is fixed to the internal side wall of the containingelement 16 by a threadedcoupling 67. On thethrust member 43, aplug 44 is screwed, by acting on which an operator can adjust thespring 41 preload. - A
movable seat 22 is further received in thecavity 8, which is shaped as a bush, and thus it is internally hollow, arranged near theend 21 of the containingelement 16 and the connectingportion 52. Theseat 22 comprises aninternal wall 22a, defining an internal maximum transverse dimension DS of theseat 22 and facing the piston, and anexternal wall 22b, contacting the walls of thecavity 8. (Fig. 3 ) - An
annular seat 23 is made in theexternal wall 22b, in which a second sealing member 24 (Fig. 3 ) is housed, which enables the passage of the pressurized fluid to be prevented outside theseat 22. - The
seat 22 surrounds thepiston 30, particularly near thesecond zone 52b and the part ofintermediate portion 33 contiguous thereto. Therefore, according to the position of thepiston 30, the latter can completely occlude, or not, a passage zone As for the pressurized fluid, which is interposed between theseat 22 and thepiston 30. More precisely, the passage zone As is overall defined by theseat 22 and thepiston 30 when thesecond zone 52b does not contact, i.e., it is spaced apart from, theinternal wall 22a of theseat 22, thus enabling the passage of the pressurized fluid from thesecond channel 5a towards thefirst channel 3a. On the contrary, when thesecond zone 52b contacts the internal walls of theseat 22, the passage zone As is absent, and the passage of the pressurized fluid from thesecond channel 5a towards thefirst channel 3a is prevented. - The
movable seat 22 is bidirectionally movable according to the directions X and Y, parallel to the axis A. In particular, as it will be explained in more detail herein below, themovable seat 22 is moved along the direction Y by the pressurized fluid and it moves along the direction X owing to the presence of aspring 25, arranged inside themovable seat 22 and acting on the latter. - In a non-illustrated embodiment, the
spring 25 can be arranged outside themovable seat 22. - The
end portion 34 of thepiston 30 is received in a portion of thecavity 8 having substantially the same radial dimension. Theend portion 34 has a maximum transverse dimension DP and comprises a piloting face 37 (Fig. 2 ). In use, the further pressurized fluid entering thevalve 1 from the pilotingopening 4 during the piloting step acts on the pilotingface 37. Theend portion 34 further comprises anannular face 47, which is frustoconical-shaped. Theannular face 47 is opposite the pilotingface 37 and it faces theintermediate portion 33. - In the operative configuration K of the
valve 1, theend portion 34 abuts on a shoulder 60 (shown inFig. 2 ) of thecavity 8 and the connectingportion 52 contacts theseat 22. On the outer side wall of theend portion 34, a groove is made, which acts as a seat for athird sealing member 35, for example, an O-ring. - As it is apparent from
Fig. 3 , the pilotingface 37 has the maximum transverse dimension Dp that is greater than the internal maximum transverse dimension DS of theinternal wall 22a of themovable seat 22. Since themovable seat 22 is interposed between the connectingportion 52 and theend portion 34 of thepiston 30, the latter comprises afirst part 30a and asecond part 30b joined together, for example through a threaded connection (Figures 1 and2 ). In this manner, since the internal maximum transverse dimension DS is less than both the radial extension of the connectingportion 52, and the maximum transverse dimension DP of the pilotingface 37, it is possible to correctly assembly thevalve 1 by arranging theseat 22 and thepiston 30 in the manner shown in theFigs. 1-3 . By way of example, during the assembling, thefirst part 30a is first positioned by inserting thehead portion 32 inside the containingelement 16, then themovable seat 22 and thespring 25 are positioned, finally thesecond part 30b is positioned, which is screwed to thefirst part 30a. - The fact that the maximum transverse dimension DP is greater than the internal maximum transverse dimension DS causes the pressurized fluid entering the
valve 1 through thesecond channel 5a to exert on thepiston 30 a thrust force FS (illustrated by an arrow inFig. 3 ), which is oriented so as to push thepiston 30 in the direction Y. - The
safety valve 10, of a known type, is a maximum pressure valve detecting the fluid pressure in thesecond channel 5a (i.e., of the fluid arriving near to the intermediate zone 33) and it opens if the above-mentioned pressure exceeds a predetermined threshold value. The latter is a value set by the user acting on adjustment means with which thesafety valve 10 is provided, and it can be equal to 350 bars. When the pressurized fluid in thesecond channel 5a exceeds this threshold value, thesafety valve 10 opens, and a portion of the above-mentioned fluid enters theconnection channel 26 to subsequently reach the pilotingchannel 4a. In the latter, the above-mentioned portion of the fluid traverses thedowel 6, with consequent pressure drop in the fluid. The pressure difference between the fluid upstream of thedowel 6 and the fluid downstream of thedowel 6 causes the piloting step to start. Consequently, thepiston 30 moves in the direction of the arrow X and the pressurized fluid can leave thesecond channel 5a - so that the fluid pressure lowers below the threshold value - to reach thefirst channel 3a. In this case, the piloting step is not controlled by the operator, but it is automatically started by thevalve 1 owing to the presence of thesafety valve 10. - The operation of the
valve 1 is described herein below, with particular reference to the case in which the latter is comprised in an earthmoving machine. - When a load has to be lifted, the pressurized fluid, for example an oil provided with suitable chemical-physical characteristics, enters the
valve 1 through thefirst opening 3 communicating with thecavity 8 through thefirst channel 3a. - The pressurized fluid reaches the
movable seat 22 and moves the latter in the direction Y, thus moving theseat 22 away from theend 21 of the containingelement 16. This is due to the fluid high pressures, which are able to overcome the elastic force exerted of thespring 25 on themovable seat 22. Instead, when the fluid is absent, thespring 25 acts on themovable seat 22 maintaining the latter abutting on the second frusto-conical zone 52b of the connectingportion 52 of thepiston 30. - Then the pressurized fluid traverses the passage zone As and it can flow, inside the
movable seat 22, towards thesecond channel 5a. Through thesecond opening 5, the fluid exits the body 2 and moves towards actuating means (not illustrated), which is comprised in the machine and which, in this manner, is actuated to lift the load. - When the load has to be lowered, the
valve 1 is initially in the first operative configuration K and the pressurized fluid exiting from the actuating means enters thevalve 1 through thesecond opening 5. The flow of this fluid causes themovable seat 22 to move in the direction X until abutting on theend 21 of the containing element 16 (Fig. 2 ). - At the same time, through the piloting
opening 4, a volume of further pressurized fluid enters the body 2 and flows in the pilotingchannel 4a. This fluid exerts a thrust action - i.e., a piloting force FP represented by an arrow inFig. 3 - on thepiston 30, particularly on theend portion 34 of the latter. Thepiston 30 begins to move in the direction X so that the second frusto-conical zone 52b moves away from theinternal wall 22a. - Then the
piston 30 moves inwards the containingelement 16, so that the connectingportion 52 does not abut anymore on theend 21 of the containingelement 16. In this manner, between themovable seat 22 and thepiston 30, the passage zone AS is defined, and the half-circular passages made in theend 21 are not closed by the connectingportion 52 anymore. The pressurized fluid entering from thesecond opening 5 can thus traverse the passage zone As and the above-mentioned half-circular passages - after flowing in thesecond channel 5a and a portion of the first cavity 8 (inside the seat 22) - to exit subsequently the body 2 of thevalve 1 through thefirst opening 3. - When the lowering of the load has to be stopped, the further pressurized fluid is no more supplied to the piloting
opening 4. - The
piston 30 is moved in the direction Y by the thrust action of thespring 41, the elastic force FEL of which is not opposed anymore by the piloting force FP due to the pressurized fluid in the pilotingchannel 4a. In this manner, the connectingportion 52 of thepiston 30 abuts again on theend 21 of the containingelement 16 and the fi-usto-conicalsecond zone 52b is in contact with themovable seat 22, thus interrupting the connection between thefirst opening 3 and thesecond opening 5. - In
Fig. 3 , the elastic force FEL, the thrust force FS, and the piloting force FP, are shown, all of which being substantially parallel to the longitudinal axis A. The elastic force FEL and the thrust force FS are concordant and push thepiston 30 in the direction Y, while the piloting force FP, opposite the other two, pushes thepiston 30 in the direction X. - On the contrary, in the known valves, the thrust force FS and the piloting force FP are concordant and push the
piston 30 in the direction X, while the elastic force FEL, opposite the other two, pushes thepiston 30 in the direction Y. - Therefore, on the contrary of the known valves, in the
valve 1 according to the invention the thrust force FS opposes the piloting force FP. - In fact, the pressurized fluid entering the
second channel 5a is distributed in thevalve 1 so that it acts on both theannular face 47 of theend portion 34, and on aportion 46 of the frusto-conicalsecond zone 52b positioned inside theseat 22 when thevalve 1 is in the operative configuration K (Fig. 3 ), i.e., when the connectingportion 52 contacts theseat 22. - Since the maximum transverse dimension DP is greater than the internal maximum transverse dimension DS, the area of the
annular face 47 is greater than the area of theportion 46, and therefore the resulting thrust force FS is directed so as to oppose the piloting force FP. - In the case when the
spring 41 does not act anymore on thepiston 30, for example due to an accidental breaking of one or more coils of the spring, and the force FEL thus becomes null, thevalve 1 closure is ensured by the thrust force FS that continues to oppose the piloting force FP (an effect that cannot be obtained in the known valves). Owing to this, thepiston 30 can move in the direction Y so as to contact themovable seat 22 and to stop the lowering of the suspended load. Moreover, this orientation of the thrust force FS avoids that, when there are very high pressures of the fluid entering the valve from the actuating means (which typically occurs when the suspended load is very inclined), the load moves very quickly. In fact, even if the fluid pressures are very high, the thrust force FS tends in any case to push thepiston 30 in the direction Y, thus preventing the passage zone As from being excessively large. Therefore, owing to the thrust force FS orientation, thevalve 1 is able to adjust the flow rate of the pressurized fluid entering thevalve 1 through thesecond opening 5a and exiting thevalve 1 through thefirst opening 3a, i.e., during the lowering step of the suspended load. - The
valve 1 can be associated to any machine or apparatus, even different from an earthmoving machine. - Owing to the invention, a load-holding
valve 1 is provided which allows blocking the movement of the suspended load (for example the arm of an earthmoving machine) in the case of a breakage of thespring 41. - Furthermore, owing to the invention, a load-holding
valve 1 is provided in which it is possible to compensate for pressure increases of the fluid entering the valve from the actuating means (through thesecond channel 5a) to avoid corresponding speed increases during the lowering of the suspended load. This is achieved owing to the orientation of the force FS that tends to push thepiston 30 in the direction Y, so as to avoid that the passage zone As becomes excessively large, so as to adjust the flow rate of pressurized fluid entering the valve through thesecond opening 5a and exiting the valve through thefirst opening 3a. This adjustment of the fluid flow rate is automatically performed by thevalve 1, as described above, and it is therefore an accurate and reliable adjustment of the fluid flow rate. - Furthermore, variations and/or additions to what has been disclosed above and/or to what has been shown in the attached drawings are possible.
Claims (11)
- Load-holding valve (1), comprising:- a body (2) provided with a cavity (8),- a piston (30) that is bidirectionally movable inside said cavity (8),- a movable seat (22) positioned inside said cavity (8) and arranged for interacting with said piston (30) such as alternatively to permit a pressurized fluid, or prevent said pressurized fluid from, traversing a passage zone (As) interposed between said seat (22) and said piston (30), said seat (22) being hollow and surrounding said piston (30),- a plurality of openings (3, 4, 5) obtained in said body (2), through said openings (3, 4, 5) the pressurized fluid being able to enter in, or exit from, said valve (1) and at least one of said openings (3, 4, 5) being suitable for connecting an intermediate portion (33) of said piston (30) with actuating means that is associable with said valve (1), said intermediate portion (33) being interposed between an end portion (34) of said piston (30) and said seat (22),characterised in that said end portion (34) has a maximum transverse dimension (DP) that is greater than an internal maximum transverse dimension (DS) of said seat (22).
- Valve (1) according to claim 1, wherein said piston (30) comprises a first part (30a) and a second part (30b), said first part (30a) and said second part (30b) being joined together.
- Valve (1) according to claim 1, or 2, wherein said plurality of openings (3, 4, 5) comprises a first opening (3), a piloting opening (4) and a second opening (5), said second opening (5) being suitable for connecting said intermediate portion (33) to said actuating means and being interposed between said first opening (3) and said piloting opening (4).
- Valve (1) according to claim 2, or 3, wherein said second part (30b) comprises said intermediate portion (33) and said end portion (34).
- Valve (1) according to any preceding claim, wherein said seat (22) comprises an internal wall (22a) defining said internal maximum transverse dimension (DS).
- Valve (1) according to any preceding claim, wherein said piston (30) further comprises a head portion (32) and a connecting portion (52), which is arranged near said seat (22), said connecting portion (52) comprising a first zone (52a) and a second zone (52b).
- Valve (1) according to claim 6, as appended to claim 5, wherein said passage zone (As) is overall defined, in use, by said seat (22) and by said piston (30) when said second zone (52b) is spaced apart from said internal wall (22a).
- Valve (1) according to claim 6, or 7, wherein said second zone (52b) comprises a portion (46), said portion (46) being positioned inside said seat (22) when, in use, said connecting portion (52) contacts said seat (22).
- Valve (1) according to any preceding claim, wherein said end portion (34) comprises an annular face (47), said annular face (47) facing said intermediate portion (33).
- Valve (1) according to claim 9, as appended to claim 8, wherein the area of said annular face (47) is greater than the area of said portion (46).
- Valve (1) according to any preceding claim, comprising a safety valve (10) arranged for detecting a pressure of said fluid near said intermediate portion (33) and for opening if said pressure overcomes a predetermined threshold value.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT000087A ITMO20120087A1 (en) | 2012-04-02 | 2012-04-02 | LOAD DISPLACEMENT VALVE |
PCT/IB2013/052542 WO2013150431A1 (en) | 2012-04-02 | 2013-03-29 | Load holding valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2834544A1 EP2834544A1 (en) | 2015-02-11 |
EP2834544B1 true EP2834544B1 (en) | 2016-05-25 |
Family
ID=46022542
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13723239.3A Active EP2834544B1 (en) | 2012-04-02 | 2013-03-29 | Load holding valve |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2834544B1 (en) |
IT (1) | ITMO20120087A1 (en) |
WO (1) | WO2013150431A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016070450A (en) * | 2014-10-01 | 2016-05-09 | ナブテスコ株式会社 | Hydraulic valve |
CN110748518B (en) * | 2019-11-05 | 2021-04-06 | 山东金利液压科技有限公司 | Excavator load keeps valve |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006250239A (en) * | 2005-03-10 | 2006-09-21 | Kawasaki Precision Machinery Ltd | Seat block and valve device |
DE102008002539A1 (en) * | 2008-06-19 | 2009-12-24 | Robert Bosch Gmbh | Control valve for a vehicle brake system and corresponding vehicle brake system |
-
2012
- 2012-04-02 IT IT000087A patent/ITMO20120087A1/en unknown
-
2013
- 2013-03-29 WO PCT/IB2013/052542 patent/WO2013150431A1/en active Application Filing
- 2013-03-29 EP EP13723239.3A patent/EP2834544B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
EP2834544A1 (en) | 2015-02-11 |
WO2013150431A1 (en) | 2013-10-10 |
ITMO20120087A1 (en) | 2013-10-03 |
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