EP2473745B1 - Distribution valve - Google Patents

Distribution valve Download PDF

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Publication number
EP2473745B1
EP2473745B1 EP10754709.3A EP10754709A EP2473745B1 EP 2473745 B1 EP2473745 B1 EP 2473745B1 EP 10754709 A EP10754709 A EP 10754709A EP 2473745 B1 EP2473745 B1 EP 2473745B1
Authority
EP
European Patent Office
Prior art keywords
conduit
valve
way
distributor
port
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
Application number
EP10754709.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2473745A1 (en
Inventor
Maurizio Bartoli
Valeriomarco Montanari
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brevini Fluid Power SpA
Original Assignee
Brevini Fluid Power SpA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Brevini Fluid Power SpA filed Critical Brevini Fluid Power SpA
Publication of EP2473745A1 publication Critical patent/EP2473745A1/en
Application granted granted Critical
Publication of EP2473745B1 publication Critical patent/EP2473745B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0832—Modular valves
    • F15B13/0839—Stacked plate type 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
    • 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
    • F15B13/026—Pressure compensating valves

Definitions

  • the invention relates to a distribution valve.
  • the invention can be used in the context of an operating machine for making a modular system with a series of modules or valve sections to connect a pump to a plurality of hydraulic actuators.
  • US 2008/000535 discloses a distribution valve as in the preamble of claim 1.
  • One object of the invention is to improve prior-art distribution valves with pressure compensators.
  • One advantage of the invention is to make a valve with relatively reduced dimensions.
  • Another advantage is to provide a constructionally simple and cheap valve.
  • a further advantage is to enable several actuators to be driven simultaneously.
  • Still another advantage is to permit substantially constant speed of the actuator, or of the actuators, also as the load varies, in particular by keeping constant the pressure difference through the valve, for example by means of a regulating choke.
  • Another advantage is to provide a distribution valve that integrates a pressure compensator and combines relatively high performance and relatively compact dimensions.
  • Another advantage is to make available a valve that can be used in the context of control systems of hydraulic actuators and which for this purpose can be associated with already existing components, with a consequent reduction of costs. Another advantage is the reduced consumption of energy required to regulate the valve.
  • a distribution valve is indicated overall having a valve body 2.
  • the valve body 2 has externally a first face 3 and a second face 4 opposite the first face 3.
  • the first face 3 and the second face 4 can be substantially flat, or at least partially flat, and parallel to one another.
  • the valve 1 can be used, as in this specific case, to make a module of a modular control system of a plurality of hydraulic actuators.
  • the modular system schematically illustrated in figure 18 , comprises a plurality of valves 1 placed serially alongside one another (with a parallel hydraulic connection), with the first face 3 of a valve coupled with the second face 4 of the adjacent valve such that one or more conduits obtained inside the valve body of a valve are in fluid communication with one or more conduits obtained inside the valve body of the adjacent valve.
  • At least one corresponding hydraulic actuator (which is of known type and not illustrated) can be operationally associated with every valve 1.
  • the modular system of hydraulic control is used, in particular, on an operating machine of know type provided with various hydraulic actuators.
  • the valve body 2 can be optionally made by fusion of material, for example made of cast iron or of another (metal) material through casting.
  • the valve body 2 has hollow portions inside that are configured for the passage of an operating fluid and/or for housing operating elements of the valve 1. For greater clarity, these hollow portions are shown for greater clarity as full portions (a solid body) in figures 7 to 12 . These hollow portions are now disclosed in greater detail.
  • the valve body 2 has an inlet conduit 5 that, in the assembled configuration of the modular system, is optionally connected to a delivery of operating fluid (in the case in point it is collected to the delivery of a hydraulic pump).
  • the inlet conduit 5 optionally crosses the valve body 2 from one side to the other.
  • the inlet conduit 5 has opposite ends that end on two opposite faces (first face 3 and second face 4) of the valve body 2.
  • the inlet conduit 5 can be substantially rectilinear, and, for example, perpendicular to the opposite faces.
  • the valve body 2 has an outlet conduit 6, that, in the assembled configuration of the modular system, is optionally connected to a discharge of operating fluid (in the specific case the discharge is connected to the inlet of the hydraulic pump).
  • the outlet conduit 6 optionally crosses the valve body 2 from one side to the other.
  • the outlet conduit 6 has opposite ends that end on two opposite faces (first face 3 and second face 4) of the valve body 2.
  • the outlet conduit 6 can be substantially rectilinear and, for example, perpendicular to the opposite faces.
  • the outlet conduit 6 is optionally parallel to the inlet conduit 5.
  • the longitudinal axis of the outlet conduit 6 and the longitudinal axis of the inlet conduit 5 are optionally coplanar and can define a plane that passes through these longitudinal axes and is transverse to the opposite faces 3 and 4.
  • This transverse plane is optionally a substantially median plane of the valve body 2.
  • valve body 2 has a distributor seat 7 that hosts a distributor that is configured for controlling the direction (distribution) of the operating fluid in relation to the actuator.
  • the distributor seat 7 comprises a cavity extending in length along a longitudinal axis that may be transverse (optionally perpendicular) to the plane passing through the longitudinal axes of the conduits 5 and 6. This cavity of the distributor seat 7 has some recesses that define the operating ways of the distributor.
  • These recesses optionally comprise a first central recess 71, a second intermediate recess 72 and a third intermediate recess 73 arranged on opposite sides of the first recess 71, a fourth end recess 74 and a fifth end recess 75 arranged on a side of the second recess 72 and respectively of the third recess 73 opposite with respect to the first recess 71.
  • the valve body 2 has a compensator seat 8 that houses a pressure compensator configured for maintaining substantially constant the pressure difference between two zones of the hydraulic circuit, as will be better explained below.
  • the compensator seat 8 comprises a cavity extending in length according to a longitudinal axis that may be transverse (optionally perpendicular) to the plane passing through the longitudinal axes of the conduits 5 and 6.
  • the longitudinal axis of the compensator seat 8 can be, for example, substantially parallel to the longitudinal axis of the distributor seat 7.
  • the valve body 2 has a first user conduit A1 and a second user conduit B1 that are connected respectively to the second recess 72 and to the third recess 73.
  • the user conduits A1 and B1 will be connected, in a known manner, to a hydraulic actuator, in particular to two sides (users A and B) of the actuator.
  • the valve body 2 has a third face 9 that may have, as in the specific case, two fluid ports 10A and 10B connected respectively to the first user conduit A1 and to the second user conduit B1.
  • the two fluid ports 10A and 10B are substantially coplanar.
  • the third face 9 can be, as in the specific case, transverse both to the first face 3 and to the second face 4.
  • the third face 9 can connect, as in the specific case, the first face 3 to the second face 4.
  • the fluid ports 10A and 10B are configured for connection (for example of removable type) to the actuator, in particular to the two operating sides A and B of the actuator.
  • the distance of each point (or the average distance of the various points) of the longitudinal axis of the distributor seat 7 from the third face 9 may be, as in the specific case, greater than the distance from each point (or the average distance of the various points) of the longitudinal axis of the inlet conduit 5 from the third face 9.
  • the distance of each point (or the average distance of the various points) of the longitudinal axis of the outlet conduit 6 from the third face 9 can be, as in the specific case, greater than the distance of each point (or the average distance of the various points) of the longitudinal axis of the inlet conduit 5 from the third face 9, and/or greater than the distance of each point (or the average distance of the various points) of the longitudinal axis of the distributor seat 7 from the third face 9.
  • the distance of each point (or the average distance of the various points) of the longitudinal axis of the compensator seat 8 from the third face 9 can be, as in the specific case, greater than the distance of each point (or the average distance of the various points) of the longitudinal axis of the inlet conduit 5 from the third face 9, and/or greater than the distance of each point (or the average distance of the various points) of the longitudinal axis of the distributor seat 7 from the third face 9, and/or greater than the distance of each point (or the average distance of the various points) of the longitudinal axis of the outlet conduit 6 from the third face 9.
  • the inlet conduit 5 is connected to the distributor seat 7.
  • the inlet conduit 5 can be connected to the distributor seat 7 by the compensator seat 8.
  • the compensator seat 8 can be interposed between the inlet conduit 5 and the distributor seat 7 in such a manner that the passage of the operating fluid between the inlet conduit 5 and the distributor seat 7 can occur only via the passage of the fluid through at least one part of the compensator seat 8.
  • the first conduit 11 may have an end that terminates in an inlet recess 81 of the cavity of the compensator seat 8.
  • the second conduit 12 may have an end that terminates in an outlet recess 82 of the cavity of the compensator seat 8.
  • the inlet recess 81 and the outlet recess 82 can be arranged next to one another at a mutually axial distance.
  • the second conduit 12 may have an end that terminates in the distributor seat 7, in particular, as in the illustrated example, in the first central recess 71 of the seat.
  • the outlet conduit 6 is connected to the distributor seat 7.
  • the valve body 2 can have a first outlet branch 61 and a second outlet branch 62 that connect the outlet conduit 6 respectively to the fourth recess 74 and to the fifth recess 75.
  • the distributor seat 7 can be situated at least partially in a region of the valve body 2 comprised between the inlet conduit 5 and the outlet conduit 6.
  • the outlet conduit 6 can be situated at least partially in a region of the valve body 2 comprised between the distributor seat 7 and the compensator seat 8.
  • the outlet conduit 6 can be situated at least partially in a region of the valve body 2 comprised between the first conduit 11 and the second conduit 12.
  • the outlet conduit 6 can be situated at least partially in a region of the valve body 2 comprised between the compensator seat 8 and the inlet conduit 5.
  • the distributor seat 7 can be situated at least partially in a region of the valve body 2 comprised between the inlet conduit 5 and the compensator seat 8.
  • the distributor which is optionally of the proportional type and can be, as in the specific case, of the four-way (delivery, discharge and two users) and three-position type, comprises a cursor 13 that is axially slidable in the distributor seat 7.
  • the cursor 13 is configured so as to be able to assume at least three operating configurations in which it respectively locks the actuator (preventing fluid communication between the four paths, i.e.
  • the distributor comprises driving means, of known type, for example of electric type (solenoid) for controlling the axial sliding of the cursor 13 in one direction and/or in the opposite direction.
  • the distributor may comprise two elastic elements (springs) that operate on the cursor 13 with opposite actions.
  • the cursor 13 comprises an external surface that has various seal zones that are slidingly coupled with the internal surface of the distributor seat 7 to make a fluid seal in a known manner in the zones of the seat comprised between the various recesses and in the zones most outside the recesses.
  • the seal zones optionally have a cylindrical shape (with, optionally, one or more circumferal grooves).
  • the seal zones optionally terminate in a chamfered (for example frustum-conical) surface to promote the operating linearity of the distributor.
  • the seal zones may have at the ends (for example in the chamfered surface, if it exists, as in the specific case) a niche or, as in the specific case, two niches 14 (situated diametrically opposite one another), or more than two niches, to promote the operating linearity of the distributor.
  • the niche 14 can be bounded at least partially by a tilted surface (for example with a frustum conical sector shape).
  • the maximum width of the niche 14 may be a fraction (for example comprised between 20% and 80%) of the diameter of the seal zone.
  • the diagram in figure 15 that shows the operating fluid flow as a function of the position of the cursor 13, shows the operating linearity of the distributor. This linearity may be promoted and/or obtained, in particular, owing to a specific conformation of the cursor 13 provided with niches 14 (for example as illustrated in figures 13 and 14 ).
  • the diagram refers to a situation in which the pressure difference ⁇ P between the valve inlet and outlet is 8 bar.
  • the position of the cursor is given as a percentage on the horizontal axis, where the position 0 (zero) indicates the cursor 13 in central position and the position 100 (cent) indicates the cursor 13 in any of the two possible end positions (with the operating fluid directed towards the user A or to the user B).
  • the compensator comprises a movable compensating element 15 that can slide axially within the compensator seat 8.
  • An elastic element (spring) pushes axially on a side of the compensating element 15 at a preset force.
  • the compensating element 15, for example the aforesaid side of the compensating element 15 where the elastic element operates, can be set up for being placed in selective communication with the first user conduit A1 or with the second user conduit B1, according to whether the user conduit A1 or B1 is connected to the delivery (see hydraulic diagram in figure 17 ).
  • This communication comprises a three-way valve with a movable shutter that selectively shuts a first way (connected to the first port 10A) or a second way (connected to the second port 10B), according to which way is connected to the port connected in that moment by means of the distributor to the discharge, and which leaves a third way (connected to the compensator and/or to an auxiliary conduit 16) in fluid communication with the one between the first way and the second way that is not closed but connected by the distributor to the delivery of the pump P.
  • This communication may comprise, for example, a conduit having a local pressure drop (for example an adjustable or fixed throttle).
  • the means for defining the local pressure drop is adjustable, for example for varying the pressure drop as a function of the position of the cursor of the distributor. It is possible that, particularly if the distributor is of the type with magnets and an ON/OFF cursor, the throttling and therefore the local pressure drop can be fixed in a preset manner, as in the illustrated example in which the pressure drop is determined by the drilled screw 18, in which the dimensions of the hole in the screw is chosen on the basis of conditions of use, for example as a function of the features of the system in which the valve is used.
  • the side of the compensating element 15 opposite the side facing the inlet recess 81 is subjected to a reference pressure that depends on the supply pressure of the actuator (for example it is the same as this pressure less local apart from distributed and/or local pressure losses), i.e. of the pressure at the fluid door 10A or 10B that, at that moment, supplies the operating fluid to the actuator.
  • the movable compensating element 15 of the pressure compensator is subjected, on an end side, to the supply pressure at the valve inlet, and, on the opposite end side, to the sum of the force due to the elastic element and the force due to the reference pressure (taken from the way of the distributor that at that moment is connected to the supply of the actuator), to the object of maintaining the pressure drop substantially constant between the inlet of the valve and the (inlet) supply of the actuator.
  • the operating fluid flow that first passes through the pressure compensator and then through the distributor, and then supplies the actuator, remains substantially constant as the load on the actuator changes.
  • the valve optionally comprises an auxiliary conduit 16 that is connected to the user conduits A1 and B1 so as to be selectively in fluid communication with the user conduit A1 or B1 that delivers the operating fluid to the user A or B.
  • the auxiliary conduit 16 is configured for the passage of a pressure signal coming from the user conduit A1 or B1 connected to the delivery. This pressure signal can be used to control the pump that supplies the operating fluid.
  • the auxiliary conduit 16 optionally crosses the valve body from one side to the other, for example with a longitudinal axis substantially parallel to the longitudinal axis of the distributor seat 7.
  • a modular system comprising two or more modules or sections, each comprising a valve 1 of the type disclosed above.
  • the modular system comprises a pump P that supplies the operating fluid at delivery pressure and a discharge T that receives the operating fluid leaving the actuators and which is connected to the inlet of the pump P.
  • Each valve 1 (module) of the modular system is connected to the two users A and B, which may be the opposite sides of a corresponding hydraulic actuator.
  • the various valves 1 (modules or sections) are placed alongside one another and can be fixed together by locking elements, such as, for example, tie rods, inserted into holes 17.
  • the various valves 1 are clamped in a block such that the inlet conduit 5 and the outlet conduit 6 of each valve are in fluid communication (in particular aligned) with the inlet conduit 5 and the outlet conduit 6 of the adjacent valves. It is possible to provide for the various auxiliary conduits 16 of the valves being in reciprocal communication (for example co-aligned) to transmit to the pump a signal indicating the supply pressure of the actuator that works at greatest pressure.
  • the valve can be controlled electrically; for example with reels of the on/off and of the proportional type, or manually. It is optional to set up a device for determining the maximum flow that is dispensable from the valve, for example a device comprising a drilled screw 18 operating on one or both the fluid ports 10A and 10B to limit the flow (in the specific case illustrated here of a distributor with assembly of the magnets and ON/OFF cursor type).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Glass Compositions (AREA)
EP10754709.3A 2009-09-03 2010-09-03 Distribution valve Not-in-force EP2473745B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITMO2009A000220A IT1395462B1 (it) 2009-09-03 2009-09-03 Valvola di distribuzione
PCT/EP2010/062974 WO2011026947A1 (en) 2009-09-03 2010-09-03 Distribution valve

Publications (2)

Publication Number Publication Date
EP2473745A1 EP2473745A1 (en) 2012-07-11
EP2473745B1 true EP2473745B1 (en) 2013-11-20

Family

ID=42107324

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10754709.3A Not-in-force EP2473745B1 (en) 2009-09-03 2010-09-03 Distribution valve

Country Status (3)

Country Link
EP (1) EP2473745B1 (it)
IT (1) IT1395462B1 (it)
WO (1) WO2011026947A1 (it)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201900023556A1 (it) * 2019-12-10 2021-06-10 Atlantic Fluid Tech S R L Valvola di sostentamento carico

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5579642A (en) 1995-05-26 1996-12-03 Husco International, Inc. Pressure compensating hydraulic control system
US5715865A (en) * 1996-11-13 1998-02-10 Husco International, Inc. Pressure compensating hydraulic control valve system
US5890362A (en) 1997-10-23 1999-04-06 Husco International, Inc. Hydraulic control valve system with non-shuttle pressure compensator
FR2787148B1 (fr) * 1998-12-09 2001-02-16 Mannesmann Rexroth Sa Distributeur hydraulique
WO2002029256A1 (fr) * 2000-09-29 2002-04-11 Kawasaki Jukogyo Kabushiki Kaisha Regulateur hydraulique
DE602004012846T2 (de) 2004-06-24 2009-04-09 Walvoil S.P.A. Load-sensing-Hydrauliksystem mit mehreren Sektionen
US7182097B2 (en) 2004-08-17 2007-02-27 Walvoil S.P.A. Anti-saturation directional control valve composed of two or more sections with pressure selector compensators
EP1860327B1 (en) 2006-05-26 2009-12-02 Hydrocontrol S.p.A. Pressure-compensating directional control valve
US7921878B2 (en) * 2006-06-30 2011-04-12 Parker Hannifin Corporation Control valve with load sense signal conditioning
WO2009001377A1 (en) * 2007-06-26 2008-12-31 Walvoil S.P.A. Load sensing directional control valve with an element having priority under saturation conditions
DE102008008092A1 (de) * 2007-11-28 2009-06-04 Robert Bosch Gmbh Ventilanordnung
US7818966B2 (en) 2008-01-09 2010-10-26 Husco International, Inc. Hydraulic control valve system with isolated pressure compensation

Also Published As

Publication number Publication date
WO2011026947A1 (en) 2011-03-10
ITMO20090220A1 (it) 2011-03-04
EP2473745A1 (en) 2012-07-11
IT1395462B1 (it) 2012-09-21

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