EP3786461A1 - Directional valve for a work vehicle and related hydraulic arrangement - Google Patents
Directional valve for a work vehicle and related hydraulic arrangement Download PDFInfo
- Publication number
- EP3786461A1 EP3786461A1 EP20193827.1A EP20193827A EP3786461A1 EP 3786461 A1 EP3786461 A1 EP 3786461A1 EP 20193827 A EP20193827 A EP 20193827A EP 3786461 A1 EP3786461 A1 EP 3786461A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- port
- directional valve
- valve
- fluidly
- piston
- 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.)
- Withdrawn
Links
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
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
- F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
-
- 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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
- F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/76—Control of force or torque of the output member
- F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
-
- 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation
Definitions
- the present invention concerns a directional valve, in particular a directional valve for a hydraulic cylinder of a work vehicle.
- Work vehicles are usually provided with implements actuated by hydraulic cylinders; an example may be found in a front loader that carries a bucket lifted by a boom that is actuated by a hydraulic cylinder.
- Figure 1 discloses a known hydraulic arrangement 1' for managing the lifting or lowering of a double acting cylinder 2' .
- such known hydraulic arrangement 1' comprises a load sensing pump 3' and a directional valve 4', fluidly interposed between the load sensing pump 3', the hydraulic cylinder 2' and a discharge 5'.
- directional valve 4' is configured to assume different position to allow a lowering, a lifting or a neutral stationary condition of the hydraulic cylinder 2'. Such positions may be assumed in function of a mechanical or electronic input given by the user of the work vehicle which needs to use the implement actuated by cylinder 2'.
- pump 3' In lifting condition, pump 3' is configured to pump pressurized fluid towards piston chamber of cylinder 2' thereby lifting a load carried by the housing of the cylinder 2'and, at the same time, generating a load sensing signal x' which is proportional to the fluid sent to cylinder 2'.
- load sensing signal x' is fluidly connected to pump 3', thereby controlling its operation.
- valve 4' make communicate fluidly discharge 5' with piston chamber from which, thanks to the action on the load on cylinder 2', fluid flow out.
- pump 3' can supply with pressurized fluid rod chamber of cylinder 2', however load sensing signal x" is very low and accordingly pump 3' is not controlled to supply fluid; therefore the movement of cylinder 2' is passive and actuated only by gravity acting on load M.
- cavitation may arise in rod chamber of cylinder 2' thereby decreasing quality of cylinder 2' and, during use, filling rod chamber with air. Furthermore, such passive movement is low and cannot be actively hydraulically controlled.
- An aim of the present invention is to satisfy the above mentioned needs in an economic and optimized way.
- Figure 2 shows a hydraulic arrangement 1 for controlling the operation of an active cylinder 2 suitable for handling of a load M.
- cylinder 2 is a standard double acting differential hydraulic cylinder comprising a body 3 defining a volume suitable for housing a piston 4 configured to slide in tight manner inside such volume and connected to a rod 5 configured to pass through body 3 in tight manner.
- an extremity of rod 5 with respect to piston 4 is fixed to a portion of a work vehicle (not shown) while piston 4 subdivides the volume defined by body 3 in a piston chamber 6a and a rod chamber 6b.
- Piston chamber 6a if fluidly connectable via a conduit 7a and a related hose 8 to a piston conduit 9a of hydraulic arrangement 1 and, similarly, rod chamber 6b is fluidly connectable to this latter via a conduit 7b and a related hose 8 to a rod conduit 9b.
- Hydraulic arrangement 1 further comprises a pump 10 preferably a load sensing pump configured to suck fluid, e.g. oil, from a reservoir 11, increase its pressure and provide a pressurized fluid as output.
- a pump 10 preferably a load sensing pump configured to suck fluid, e.g. oil, from a reservoir 11, increase its pressure and provide a pressurized fluid as output.
- Such pump 10 is connectable to both piston and rod conduits 9a, 9b mentioned above as defined in the following.
- Hydraulic arrangement 1 further comprises a directional valve 12 according to the present invention fluidly interposed between cylinder 2 and pump 10.
- hydraulic cylinder 2 comprises a send conduit 13 fluidly connecting an output of pump 10 with a first port 12a of directional valve 12 and a return conduit 14 fluidly connecting directional a second port 12b of valve 12 with reservoir 11.
- a directional third port 12c of valve 12 is fluidly connect to pump 10 via a conduit 15 carrying a load sensing signal configured to control pump 10.
- a fourth and fifth ports 12d, 12e of directional valve 12 is fluidly connected to piston and rod conduits 9a, 9b mentioned above.
- Directional valve 12 is configured to allow a lifting, a lowering, a neutral and a closed operational configuration by connecting in different manners piston and rod conduits 9a, 9b with send and return conduits 13, 14.
- actuators means 16 configured to move directional valve 12.
- such actuator means 16 are mechanical means and preferably acts against elastic means 17 configured to maintain directional valve in the neutral operational configuration.
- directional valve is a five ways - four positions valve.
- Hydraulic arrangement may further comprise a non return valve 18 fluidly interposed on send conduit 13 upstream with respect to directional valve 11, so as to allow passage only from pump 10 towards cylinder 2 and not vice versa.
- hydraulic arrangement 1 may comprise a pressure compensator module 20, provided with a narrowing 21 and proportional ON-OFF valve 22 fluidly interposed in series upstream with the non-return valve 18.
- pressure compensation module is per se known and therefore is not described for sake of brevity.
- valve 12 of figure 3 may assume a first position I, i.e. rest neutral position wherein load signal conduit 15 is connected to return conduit 14, i.e. to reservoir 11. Accordingly, pump 10 does not provide any pressurized flow to cylinder 2 and piston and rod chambers 6a, 6b and pump 2 output are isolated. Accordingly, load M is maintained at a pre-set position since body 3 cannot be moved with respect to work vehicle. Indeed, pressure in piston and rod chambers 6a, 6b defines a stiffness of support given by cylinder 2 to mass M.
- send conduit 13 is fluidly connected to piston conduit 9a and a portion X' of such fluid is spilled to load sensing conduit 15, while rod conduit 9b is fluidly connected to return conduit 14.
- pump 10 can provide pressurized fluid to piston chamber 6a thereby moving body 3 and decreasing volume of rod chamber 6b. Fluid from such chamber may flow out via conduits 9b, 14.
- the load sensing signal given by portion X' is collected by conduit 15 and sent to pump 10 which is controlled consequently.
- send conduit 13 is fluidly connected to rod conduit 9b, while return conduit 14 is fluidly connected to piston conduit 9a; according to the invention, respective fluid portions X", X''' are spilled from both the fluid connection between conduits 9b and 13 and the fluid connection between conduits 9a, 14.
- Such fluid portions are fluidly directed to a selection module 25, for example comprising a shuttle valve, configured to allow the passage of fluid to load sensing signal conduit 15 only to the portion X", X''' having the greater pressure.
- send conduit 13 is open while both piston and rod conduits 9a, 9b and load sensing conduit 15 are fluidly connected to return conduit 14. Accordingly, pump 10 cannot provide pressurized fluid to cylinder 2, which is totally vent out to reservoir 11.
- valve 10 In a lifting condition, i.e. second position II, fluid will flow from send conduit 13 towards piston conduit 9a to piston chamber 6a, thereby lifting body 3 and mass M accordingly. Operation of valve 10 is controlled by load sensing signal x' spilled to conduit 15 from the fluid flowing between conduits 9a and 13.
- fluid will flow from piston conduit 9a, i.e. flowing out from piston chamber 9a under load acted by mass M, towards return conduit 14 and, in parallel, pump 10 may send pressurized fluid to rod chamber 6b via fluid connection between send conduit 13 and rod conduit 9b.
- Fluid is spilled from both fluid connection between rod conduits 9b and send conduit 13 (X") and connection between piston conduit 9a and return conduit 14 (X''').
- Such spilled fluid portions X", X''' then pass to selection module 25, e.g. to a shuttle valve, in which the one with greatest pressure will pass to pump 10 as loading sensing signal. In this way, a sufficient load sensing signal is always sent to pump 10 which can provide pressurized flow to rod chamber 6b, thereby avoiding cavitation and assuring a fast lowering of load M.
- the proposed directional valve 12 allows to provide always a sufficient load sensing signal to control pump 10 thereby pressurizing road chamber 6b and avoiding cavitation.
- pressure compensation module 20 may be optional, such as the non-return valve 18.
- the pump 10 may be substituted by a hydraulic supply system of any known typology.
- neutral position is optional and, accordingly, the present invention may apply to 5/3 way valves as known in the art.
- fixation of cylinder 2 elements to work vehicle may be realized in specular or different way.
- selection module 25 may comprise elements having the same function of the described shuttle valve.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
Abstract
Description
- The present invention concerns a directional valve, in particular a directional valve for a hydraulic cylinder of a work vehicle.
- Work vehicles are usually provided with implements actuated by hydraulic cylinders; an example may be found in a front loader that carries a bucket lifted by a boom that is actuated by a hydraulic cylinder.
-
Figure 1 discloses a known hydraulic arrangement 1' for managing the lifting or lowering of a double acting cylinder 2' . - Briefly, such known hydraulic arrangement 1' comprises a load sensing pump 3' and a directional valve 4', fluidly interposed between the load sensing pump 3', the hydraulic cylinder 2' and a discharge 5'.
- In synthesis, directional valve 4' is configured to assume different position to allow a lowering, a lifting or a neutral stationary condition of the hydraulic cylinder 2'. Such positions may be assumed in function of a mechanical or electronic input given by the user of the work vehicle which needs to use the implement actuated by cylinder 2'.
- In lifting condition, pump 3' is configured to pump pressurized fluid towards piston chamber of cylinder 2' thereby lifting a load carried by the housing of the cylinder 2'and, at the same time, generating a load sensing signal x' which is proportional to the fluid sent to cylinder 2'. Such load sensing signal x' is fluidly connected to pump 3', thereby controlling its operation.
- In neutral condition, pump 3', discharge 5' and cylinder 2' are isolated one with respect to the other. Accordingly, the position of cylinder 2' is fixed as also the pressure of the fluid in both rod and piston chambers of this latter, thereby guarantee a correct support and stiffness of the cylinder 2'.
- In lowering condition, valve 4' make communicate fluidly discharge 5' with piston chamber from which, thanks to the action on the load on cylinder 2', fluid flow out. Also in this case pump 3' can supply with pressurized fluid rod chamber of cylinder 2', however load sensing signal x" is very low and accordingly pump 3' is not controlled to supply fluid; therefore the movement of cylinder 2' is passive and actuated only by gravity acting on load M.
- In view of the above, cavitation may arise in rod chamber of cylinder 2' thereby decreasing quality of cylinder 2' and, during use, filling rod chamber with air. Furthermore, such passive movement is low and cannot be actively hydraulically controlled.
- Therefore, the need is felt to provide a directional valve and a related hydraulic arrangement comprising such directional valve for controlling a hydraulic cylinder of a work vehicle that solve the above problems.
- An aim of the present invention is to satisfy the above mentioned needs in an economic and optimized way.
- The aforementioned aim is reached by a directional valve and a related hydraulic circuit as claimed in the appended set of claims.
- For a better understanding of the present invention, a preferred embodiment is described in the following, by way of a non-limiting example, with reference to the attached drawings wherein:
-
Figure 1 is a schematic representation of a hydraulic circuit as known in the prior art; -
Figure 2 is a schematic representation of a hydraulic circuit comprising a directional valve according to the invention; and -
Figure 3 is an enlarged schematic representation of the directional valve according to the invention. -
Figure 2 shows a hydraulic arrangement 1 for controlling the operation of anactive cylinder 2 suitable for handling of a load M. - In particular,
cylinder 2 is a standard double acting differential hydraulic cylinder comprising abody 3 defining a volume suitable for housing apiston 4 configured to slide in tight manner inside such volume and connected to arod 5 configured to pass throughbody 3 in tight manner. - According to the exemplarily disclosed embodiment, an extremity of
rod 5 with respect topiston 4 is fixed to a portion of a work vehicle (not shown) whilepiston 4 subdivides the volume defined bybody 3 in apiston chamber 6a and arod chamber 6b. Pistonchamber 6a if fluidly connectable via aconduit 7a and arelated hose 8 to apiston conduit 9a of hydraulic arrangement 1 and, similarly,rod chamber 6b is fluidly connectable to this latter via aconduit 7b and arelated hose 8 to arod conduit 9b. - According to the above-defined arrangement, when a fluid enters into
piston chamber 6a,body 3 is pushed against mass M in order to lift said mass while when a fluid enters intorod chamber 6b,body 3 is pushed concordantly with gravity of mass M, lowering this latter. - Hydraulic arrangement 1 further comprises a
pump 10 preferably a load sensing pump configured to suck fluid, e.g. oil, from areservoir 11, increase its pressure and provide a pressurized fluid as output.Such pump 10 is connectable to both piston androd conduits - Hydraulic arrangement 1 further comprises a
directional valve 12 according to the present invention fluidly interposed betweencylinder 2 andpump 10. In particular,hydraulic cylinder 2 comprises asend conduit 13 fluidly connecting an output ofpump 10 with afirst port 12a ofdirectional valve 12 and areturn conduit 14 fluidly connecting directional asecond port 12b ofvalve 12 withreservoir 11. Moreover, a directionalthird port 12c ofvalve 12 is fluidly connect topump 10 via aconduit 15 carrying a load sensing signal configured to controlpump 10. Furthermore, a fourth andfifth ports directional valve 12 is fluidly connected to piston androd conduits -
Directional valve 12 is configured to allow a lifting, a lowering, a neutral and a closed operational configuration by connecting in different manners piston androd conduits return conduits directional valve 12. In the described embodiment, such actuator means 16 are mechanical means and preferably acts againstelastic means 17 configured to maintain directional valve in the neutral operational configuration. Accordingly, directional valve is a five ways - four positions valve. - Hydraulic arrangement may further comprise a
non return valve 18 fluidly interposed on sendconduit 13 upstream with respect todirectional valve 11, so as to allow passage only frompump 10 towardscylinder 2 and not vice versa. - Always preferably and optionally, hydraulic arrangement 1 may comprise a
pressure compensator module 20, provided with a narrowing 21 and proportional ON-OFF valve 22 fluidly interposed in series upstream with thenon-return valve 18. Such pressure compensation module is per se known and therefore is not described for sake of brevity. - Making reference to enlarged view of
directional valve 12 offigure 3 , said valve may assume a first position I, i.e. rest neutral position whereinload signal conduit 15 is connected toreturn conduit 14, i.e. toreservoir 11. Accordingly,pump 10 does not provide any pressurized flow tocylinder 2 and piston androd chambers pump 2 output are isolated. Accordingly, load M is maintained at a pre-set position sincebody 3 cannot be moved with respect to work vehicle. Indeed, pressure in piston androd chambers cylinder 2 to mass M. - In a second position II, send
conduit 13 is fluidly connected topiston conduit 9a and a portion X' of such fluid is spilled to loadsensing conduit 15, whilerod conduit 9b is fluidly connected toreturn conduit 14. Accordingly,pump 10 can provide pressurized fluid topiston chamber 6a thereby movingbody 3 and decreasing volume ofrod chamber 6b. Fluid from such chamber may flow out viaconduits conduit 15 and sent topump 10 which is controlled consequently. - In a third position III, which is according to the present invention, send
conduit 13 is fluidly connected torod conduit 9b, whilereturn conduit 14 is fluidly connected topiston conduit 9a; according to the invention, respective fluid portions X", X''' are spilled from both the fluid connection betweenconduits conduits selection module 25, for example comprising a shuttle valve, configured to allow the passage of fluid to loadsensing signal conduit 15 only to the portion X", X''' having the greater pressure. - In a fourth position IV, send
conduit 13 is open while both piston androd conduits load sensing conduit 15 are fluidly connected toreturn conduit 14. Accordingly,pump 10 cannot provide pressurized fluid tocylinder 2, which is totally vent out toreservoir 11. - The operation of the above described
directional valve 12 and related hydraulic arrangement 1 is the following. - As said, in first position IV of
directional valve 12 sendconduit 13 is open and allother conduits return conduit 14 to reservoir andcylinder 2 is empty. - In neutral condition, i.e. first position I, all
conduits load sensing signal 15 is sent viaconduit 14 toreservoir 11 and accordingly level ofcylinder 2 is maintained with the stiffness defined by the pressure ratio between piston androad chambers - In a lifting condition, i.e. second position II, fluid will flow from send
conduit 13 towardspiston conduit 9a topiston chamber 6a, thereby liftingbody 3 and mass M accordingly. Operation ofvalve 10 is controlled by load sensing signal x' spilled to conduit 15 from the fluid flowing betweenconduits - In a lowering condition, i.e. third position III, fluid will flow from
piston conduit 9a, i.e. flowing out frompiston chamber 9a under load acted by mass M, towardsreturn conduit 14 and, in parallel,pump 10 may send pressurized fluid torod chamber 6b via fluid connection between sendconduit 13 androd conduit 9b. Fluid is spilled from both fluid connection betweenrod conduits 9b and send conduit 13 (X") and connection betweenpiston conduit 9a and return conduit 14 (X'''). Such spilled fluid portions X", X''' then pass toselection module 25, e.g. to a shuttle valve, in which the one with greatest pressure will pass to pump 10 as loading sensing signal. In this way, a sufficient load sensing signal is always sent to pump 10 which can provide pressurized flow torod chamber 6b, thereby avoiding cavitation and assuring a fast lowering of load M. - In view of the foregoing, the advantages of a
directional valve 12 and a related hydraulic arrangement 1 according to the invention are apparent. - The proposed
directional valve 12 allows to provide always a sufficient load sensing signal to controlpump 10 thereby pressurizingroad chamber 6b and avoiding cavitation. - Accordingly, the work quality of
cylinder 2 is improved and the formation of air inside the volume of this latter is decreased. - Moreover, the proposed solution of a selection module as shuttle valve is economic and compact thereby allowing the use of the
directional valve 12 according to the present invention in already existing hydraulic arrangements. - It is clear that modifications can be made to the described a
directional valve 12 and a related hydraulic arrangement 1 which do not extend beyond the scope of protection defined by the claims. - For example,
pressure compensation module 20 may be optional, such as thenon-return valve 18. Furthermore, thepump 10 may be substituted by a hydraulic supply system of any known typology. - Moreover, neutral position is optional and, accordingly, the present invention may apply to 5/3 way valves as known in the art.
- In addition, fixation of
cylinder 2 elements to work vehicle may be realized in specular or different way. - Again,
selection module 25 may comprise elements having the same function of the described shuttle valve.
Claims (12)
- Directional valve (12) for a hydraulic arrangement (1) of a work vehicle for controlling the operation of a double acting cylinder (2) comprising a piston chamber (6a) and a rod chamber (6b), such directional valve (12) comprising a first port (12a) fluidly connectable to an output of a load sensing hydraulic supply system (10), a second port (12b) fluidly connectable to a reservoir (11), a third port (12c) fluidly connectable to said hydraulic supply system (10) to carry a load sensing signal configured to control the operation of said supply system (10), a fourth and fifth ports (12d, 12e) fluidly connectable to respectively said piston and rod chambers (6a, 6b), said valve being configured to assume at least:- a first operational position (II) in which said first port (12a) is fluidly connected to said fourth port (12d) and said fifth (12e) port is fluidly connected to said second port (12b), in parallel, a portion (X') of fluid passing through said first and fourth ports (12a, 12d) is spilled to generate a load sensing signal sent through said third port (12c) to said hydraulic supply system (10); and- a second operational position (III) in which said first port (12a) is fluidly connected to said fifth port (12e) and said fourth port (12d) is fluidly connected to said second port (12b), in parallel, a portion (X") of fluid passing through said first and fifth ports (12a, 12e) is spilled and a portion (X''') of fluid passing through said second and fourth ports (12b, 12d) is spilled, such fluid spilled portions (X", X''') being fluidly connected to a selection module (25) configured to allow the passage towards said third port (12c) to the greatest between such spilled portions (X", X"') as load sensing signal for said hydraulic supply system (10) .
- Directional valve according to claim 1, wherein said selection module (25) comprising a shuttle valve.
- Directional valve according to claim 1 or 2, further comprising a third operational position (I) in which said first, fourth and fifth ports (12a, 12d, 12e) are not connected to any other among said ports of said valve (12) and in which said second and third ports (12b, 12c) are fluidly connected to each other.
- Directional valve according to any of the preceding claims, further comprising a fourth operational position (IV) in which said second, third, fourth and fifth ports (12b, 12c, 12d, 12e) are fluidly connected to each other and in which said first port (12a) is not connected to any other among said ports.
- Directional valve according to any of the preceding claims, comprising actuator means (16) configured to move said valve (12) to select one between said operational positions (I, II, III, IV).
- Directional valve according to claim 5, wherein said actuator means (16) comprise mechanical actuator means.
- Directional valve according to claim 5 or 6, further comprising elastic means (17) configured to impart a force to said valve (12) opposed to the action of said actuator means (16) and configured to maintain said valve (12) in a pre-set operational position.
- Hydraulic arrangement (1) for controlling the operation of a double acting cylinder (2) comprising a piston chamber (6a) and a rod chamber (6b), said arrangement (1) further comprising a reservoir (11) and a load sensing hydraulic supply system (10) configured to suck fluid from said reservoir (11), pressurize and send this latter towards said cylinder (2), said hydraulic arrangement (1) further comprising a directional valve (12) according to any of the preceding claims fluidly interposed between said hydraulic supply system (10), said reservoir (11) and said piston and rod chambers (6a, 6b).
- Hydraulic arrangement according to claim 8, further comprising a non-return valve (18) fluidly interposed between the output of said hydraulic supply system (10) and said directional valve (12).
- Hydraulic arrangement according to claim 9, further comprising a pressure compensator module (20) fluidly interposed between the output of said hydraulic supply system (10) and said directional valve (12), upstream with respect to said non-return valve (18).
- Hydraulic arrangement according to claim 10, wherein said pressure compensator module (20) comprises a narrowing (21) and a proportional valve (22) fluidly in series one with respect to the other.
- Hydraulic arrangement according to any of claims 8 to 11, wherein said cylinder (2) comprises a body (3) defining a volume housing a piston (4) carried by a rod (5) passing through said body (3), said piston (4) subdividing such volume into said piston and rod chambers (6a, 6b), said rod (5) being fixed to a portion of a work vehicle.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102019000015363A IT201900015363A1 (en) | 2019-09-02 | 2019-09-02 | DIRECTIONAL VALVE FOR A WORK VEHICLE AND RELATIVE HYDRAULIC ARRANGEMENT |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3786461A1 true EP3786461A1 (en) | 2021-03-03 |
Family
ID=68988223
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20193827.1A Withdrawn EP3786461A1 (en) | 2019-09-02 | 2020-09-01 | Directional valve for a work vehicle and related hydraulic arrangement |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP3786461A1 (en) |
IT (1) | IT201900015363A1 (en) |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3505623A1 (en) * | 1985-02-19 | 1986-08-21 | Robert Bosch Gmbh, 7000 Stuttgart | HYDRAULIC DIRECTION VALVE FOR A LOAD PRESSURE COMPENSATED CONTROL |
US5211196A (en) * | 1990-08-31 | 1993-05-18 | Hydrolux S.A.R.L. | Proportional seat-type 4-way valve |
EP1143152A2 (en) * | 2000-04-03 | 2001-10-10 | Husco International, Inc. | Auto-calibration of a solenoid operated valve |
JP2002005107A (en) * | 1996-01-08 | 2002-01-09 | Nachi Fujikoshi Corp | Hydraulic driving device |
EP2365226A1 (en) * | 2010-03-12 | 2011-09-14 | CNH Italia S.p.A. | Hydraulic system |
CN103062144B (en) * | 2012-12-30 | 2015-08-12 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | A kind of load sensing multi-way valve with anti-saturation function |
CN105351278A (en) * | 2015-12-10 | 2016-02-24 | 上海新跃仪表厂 | Novel compound electro-hydraulic servo control system |
EP3001042A1 (en) * | 2014-09-25 | 2016-03-30 | CNH Industrial Italia S.p.A. | Hydraulic system |
WO2016163926A1 (en) * | 2015-04-10 | 2016-10-13 | Volvo Construction Equipment Ab | A load sensing hydraulic system for a working machine, and a method for controlling a load sensing hydraulic system |
-
2019
- 2019-09-02 IT IT102019000015363A patent/IT201900015363A1/en unknown
-
2020
- 2020-09-01 EP EP20193827.1A patent/EP3786461A1/en not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3505623A1 (en) * | 1985-02-19 | 1986-08-21 | Robert Bosch Gmbh, 7000 Stuttgart | HYDRAULIC DIRECTION VALVE FOR A LOAD PRESSURE COMPENSATED CONTROL |
US5211196A (en) * | 1990-08-31 | 1993-05-18 | Hydrolux S.A.R.L. | Proportional seat-type 4-way valve |
JP2002005107A (en) * | 1996-01-08 | 2002-01-09 | Nachi Fujikoshi Corp | Hydraulic driving device |
EP1143152A2 (en) * | 2000-04-03 | 2001-10-10 | Husco International, Inc. | Auto-calibration of a solenoid operated valve |
EP2365226A1 (en) * | 2010-03-12 | 2011-09-14 | CNH Italia S.p.A. | Hydraulic system |
CN103062144B (en) * | 2012-12-30 | 2015-08-12 | 徐工集团工程机械股份有限公司江苏徐州工程机械研究院 | A kind of load sensing multi-way valve with anti-saturation function |
EP3001042A1 (en) * | 2014-09-25 | 2016-03-30 | CNH Industrial Italia S.p.A. | Hydraulic system |
WO2016163926A1 (en) * | 2015-04-10 | 2016-10-13 | Volvo Construction Equipment Ab | A load sensing hydraulic system for a working machine, and a method for controlling a load sensing hydraulic system |
CN105351278A (en) * | 2015-12-10 | 2016-02-24 | 上海新跃仪表厂 | Novel compound electro-hydraulic servo control system |
Also Published As
Publication number | Publication date |
---|---|
IT201900015363A1 (en) | 2021-03-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7614336B2 (en) | Hydraulic system having augmented pressure compensation | |
EP2679735B1 (en) | Construction machine with working attachment | |
US9206821B2 (en) | Hydraulic switching mechanism for mobile hydraulics, mobile hydraulic machine and valve unit | |
US7204185B2 (en) | Hydraulic system having a pressure compensator | |
US5490384A (en) | Hydraulic flow priority system | |
JP6467515B2 (en) | Construction machinery | |
US5802847A (en) | Hydraulic system for a mobile work device, in particular a wheel loader | |
JP2009505013A (en) | Hydraulic circuit of double acting hydraulic cylinder | |
AU2004276616A1 (en) | Hydraulic control device of industrial machinery | |
US6370874B1 (en) | Hydraulic control device for a mobile machine, especially for a wheel loader | |
CA2945219C (en) | Device for recovering hydraulic energy in an implement and a corresponding implement | |
JP2008039184A (en) | Hydraulic actuator control circuit with pressure operated counterbalancing valves | |
US20080295681A1 (en) | Hydraulic system having an external pressure compensator | |
JP2017115992A (en) | Hydraulic system of work machine | |
KR102535297B1 (en) | fluid circuit | |
EP3786461A1 (en) | Directional valve for a work vehicle and related hydraulic arrangement | |
US7383682B2 (en) | Hydraulic control arrangement for a mobile equipment | |
US8763388B2 (en) | Hydraulic system having a backpressure control valve | |
JP2017015130A (en) | Fluid circuit | |
JP2008185098A (en) | Control system in working machine | |
EP4112946A1 (en) | Hydraulic arrangement for a work vehicle | |
CN111677704B (en) | Hydraulic system and engineering machinery | |
EP4098808A1 (en) | Construction machinery | |
CN112360833B (en) | Flow control system, flow control method and crane | |
EP2118385B1 (en) | Fluid system and method of operating thereof |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20210903 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20221114 |
|
RAP3 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: CNH INDUSTRIAL ITALIA S.P.A. |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20230325 |