EP4095393A1 - Hydraulic distributor with compensator device for directional valves and hydraulic circuit comprising the same - Google Patents

Hydraulic distributor with compensator device for directional valves and hydraulic circuit comprising the same Download PDF

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Publication number
EP4095393A1
EP4095393A1 EP22175917.8A EP22175917A EP4095393A1 EP 4095393 A1 EP4095393 A1 EP 4095393A1 EP 22175917 A EP22175917 A EP 22175917A EP 4095393 A1 EP4095393 A1 EP 4095393A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
energy recovery
compensator
segment
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.)
Pending
Application number
EP22175917.8A
Other languages
German (de)
English (en)
French (fr)
Inventor
Ulderico Busani
Davide MESTURINI
Gianluca Ganassi
Mattia Scolari
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.)
Walvoil SpA
Original Assignee
Walvoil SpA
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Filing date
Publication date
Application filed by Walvoil SpA filed Critical Walvoil SpA
Publication of EP4095393A1 publication Critical patent/EP4095393A1/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • 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
    • 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
    • F15B2013/0409—Position sensing or feedback of the valve member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41554—Flow control characterised by the connections of the flow control means in the circuit being connected to a return line and a directional control valve
    • 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
    • F15B2211/605—Load sensing circuits
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a valve
    • 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
    • F15B2211/88—Control measures for saving energy

Definitions

  • the present invention finds application in hydraulic systems, in particular but not exclusively in the sector of hydraulic distributors intended for operating hydraulic actuators using pressure compensation devices.
  • the invention refers to a hydraulic distributor of the type comprising at least one spool for operating a hydraulic user, e.g. a hydraulic actuator, and a pressure compensator.
  • Pressure compensation is in fact typically used in order to maintain a constant pressure drop at the ends of the regulating ports, thus enabling a precise flow rate control, independent of the load of the actuator and the simultaneous operation of several sections to be obtained. This allows the flow rate to be regulated so that it is only a function of the stroke of the main spool.
  • the known solutions allow only a passive management of this functionality, leaving that the priority flow intended for energy recovery is only connected to the operating conditions of the system.
  • the operation of the energy recovery unit in the known solutions does not provide any possibility of regulation, since it is also connected only to the priority flow redirected by the distributor.
  • the technical problem at the basis of the present invention is to make available a hydraulic circuit that is structurally and functionally conceived to overcome one or more of the limitations disclosed above with reference to the mentioned prior art.
  • one object of the present invention is to make available to the art a hydraulic distributor that is set up for a simple use in applications provided with energy recovery logics.
  • a further object is to make available a hydraulic circuit provided with a (at least) three-way compensator, capable of combining the usual flow regulation functions typical of the compensators with the ability to manage a priority flow aimed at energy-saving logics.
  • Still another object of the invention is to make available a hydraulic distributor in which the energy recovery functions can be regulated not only according to the boundary conditions of the hydraulic circuit in which the distributor operates, but also in a user-adjustable or otherwise modifiable manner according to specific operational requirements.
  • the invention refers to a hydraulic distributor comprising at least one main spool for operating a hydraulic user, for example a hydraulic actuator, a supply segment for operating the hydraulic user, preferably configured to provide a delivery segment with a flow rate of operating fluid at a working pressure, and a pressure compensator.
  • the pressure compensator is configured in such a way that acting on a first side thereof is a local pressure, preferably taken at the delivery segment.
  • acting on a second side of the pressure compensator is a maximum Load Sensing pressure either characteristic of the working pressure of said hydraulic user, in case it is operated individually, or, in case a plurality of hydraulic units being operated, each defining a respective characteristic pressure, characteristic of the maximum pressure among said characteristic pressures of the hydraulic users.
  • said hydraulic distributor comprises a position sensor associated with said pressure compensator.
  • Said position sensor is preferably configured to detect the position of said pressure compensator and preferably transmit it to a control unit operatively connected with said energy recovery device.
  • the second side is opposite said first side.
  • said spool is configured to define a delivery segment and a discharge segment.
  • said pressure compensator comprises at least three ways.
  • a first way is connected to said discharge segment of the spool in such a way as to intercept the discharge segment itself.
  • a second way is connected to discharge.
  • a third way is configured in such a way as to connect said discharge segment with an energy recovery stretch connectable to an energy recovery device.
  • the hydraulic distributor of the present invention provides for the presence of a pressure compensator arranged in such a way as to intercept at least the discharge segment; a position sensor is associated with said compensator.
  • the pressure compensator is configured in such a way that acting on a first side thereof is a local pressure (Ploc) taken at a stretch of the main delivery segment and acting on a second side thereof is a pressure corresponding to the maximum Load Sensing pressure (PLSmax) among the characteristic pressures of the hydraulic users operated by the distributor.
  • PLSmax maximum Load Sensing pressure
  • the compensator is preferably of the at least three-way type and one of these ways connects the discharge segment exiting the main spool with an energy recovery stretch connected to an energy recovery device.
  • the distributor further comprises a position sensor operatively associated with the pressure compensator so as to be able to detect the position of the pressure compensator itself and transmit it to a control unit operatively connected with the energy recovery device.
  • the presence of the position sensor makes it possible to transmit information about the position of the compensator to the control unit, using this information to regulate or set the operating modes in which the energy recovery device operates.
  • this regulation of the energy recovery device results in a consequent variation in the back pressure value of the energy recovery stretch, i.e. of the pressure upstream of the device.
  • This pressure variation has an impact on the overall operating conditions of the circuit.
  • the position of the pressure compensator will in turn be changed, bringing the system to a different equilibrium position, which will be read again via the position sensor to be transmitted to the control unit.
  • the control unit can therefore be configured in such a way as to intervene on the energy recovery device and, more generally, on the pressure value of the energy recovery stretch, in such a way that the compensator is brought to a position corresponding to the most advantageous condition from the point of view of energy recovery.
  • this position is the one in which the pressure compensator has its way connected to the discharge segment completely closed and its way connected to the energy recovery stretch minimally "choked".
  • the control unit can be configured to set the desired behaviour of the pressure compensator towards a specific position.
  • the system can be set to be under a certain condition for a first time interval and under a second condition in a subsequent time interval. This different setting may also be associated with the charge level of an energy accumulator or other boundary conditions.
  • the invention also refers to the hydraulic circuit in which the aforesaid distributor connected to an energy recovery device and to a relative control unit is present.
  • the energy recovery device may comprise regulating means configured to vary a back pressure value on the recovery stretch. In this way it is possible to condition the position of the compensator by varying the conditions within which the distributor operates as illustrated above.
  • the energy recovery device may comprise a hydraulic motor activated by a fluid flow rate supplied via said energy recovery stretch in such a way as to supply energy to an energy storage device.
  • the regulating means are configured to vary the pressure upstream of the hydraulic motor.
  • the control unit can operate in such a way as to have the circuit work under the condition of maximum energy recovery as long as there is energy available to be supplied to the accumulator and as long as it can receive energy.
  • the energy storage device comprises a rechargeable battery and the regulating means comprise an electric generator.
  • the control unit is configured in such a way as to regulate resistant torque and/or speed values of the electric generator. In this way it is possible to vary the pressure conditions upstream of the hydraulic motor, that is, of the stretch connected to the pressure compensator, by means of a solution of simple implementation that allows to make available electrical energy that can be advantageously used in the operating context of the means on which the distributor and the circuit of the present invention are installed.
  • the energy storage device may also be of different types, for example of hydraulic type.
  • the distributor and the circuit of the present invention may further provide for numerous other preferred features, as indicated below and in the dependent claims of the present invention. It will be appreciated that these features apply to all aspects of the invention unless otherwise indicated.
  • the pressure compensator comprises a first way connected to the discharge segment of the spool, a second way connected to discharge, or to a tank of the hydraulic circuit, and a third way configured in such a way as to connect the discharge segment with the energy recovery stretch.
  • the fluid flow rate provided through the supply segment can be directed to discharge or, if the working conditions allow it, partially or entirely to a recovery device by partialising or closing the discharge segment.
  • the pressure compensator may further be arranged in such a way as to intercept both the delivery segment and the discharge segment.
  • said pressure compensator is arranged in such a way as to respectively intercept said delivery segment and said discharge segment.
  • the term "intercept” will be understood to mean that the pressure compensator is placed in an intermediate position of a respective segment, i.e. the delivery segment and/or the discharge segment. The segment is then interrupted to flow into the compensator, and then continue out of the compensator itself. Both the delivery segment and the discharge segment can be intercepted by the compensator.
  • the pressure compensator can act taking into account both the working conditions of the different sections activated by the distributor and taking into account the delivery conditions.
  • the compensator can therefore act by fully opening the delivery and discharge passage ports or by choking them, depending on the working conditions of the distributor. For example, in the event that the maximum Load Sensing Pressure (PLSmax) has a high value, for example due to the occurrence of a particular working condition, for example resulting from a high load being simultaneously activated on another user, the compensator will tend to choke the passage ports, by acting on both the delivery and on the discharge such to bring the hydraulic system back to an equilibrium situation without significant variations in the flow rate deriving therefrom.
  • PLSmax maximum Load Sensing Pressure
  • the pressure compensator comprises a continuous-positioning spool, precisely allowing a continuous and precise regulation of the flow rate according to the actual working conditions.
  • the pressure compensator comprises five ways, thereby enabling a particularly simple constructive solution to be realized.
  • the five ways comprise two inlet ways, one for the delivery and one for the discharge respectively, and two outlet ways, one for the delivery and one for the discharge respectively, and a fifth way that defines an energy recovery stretch connectable to an energy recovery device.
  • the compensator in order to keep the compensator normally open, it may comprise an elastic element, for example a spring, acting on the first side.
  • the local pressure is taken at a primary stretch of the delivery segment immediately downstream of the spool.
  • the primary stretch connects the spool with the pressure compensator.
  • the delivery segment can also comprise a secondary stretch that again places the compensator in communication with the spool. This allows to optimise the overall dimensions of the distributor, simplifying the design thereof.
  • the compensator is arranged downstream, and preferably immediately downstream, of the main spool along the discharge segment.
  • the compensator is arranged downstream, and preferably immediately downstream, of the main spool along the delivery stretch.
  • a hydraulic circuit comprising an oleodynamic distributor 100 according to the present invention is illustrated as a whole with number 10.
  • the hydraulic circuit 10 is intended to operate one or more hydraulic users U1, U2,..., Un and comprises a supply group 20 intended to provide an operating fluid flow rate for the operation of such hydraulic users.
  • the supply group 20 can be of the variable flow rate or pressure type. However, solutions may be provided in which other solutions for regulating the supply group 20 may be used.
  • the supply group 20 may comprise a variable displacement pump that regulates the flow rate based on the pressure characteristic of the user at a higher pressure among those supplied by the supply group.
  • the example in Figure 1 illustrates the hydraulic system 10 in the case where the supply group 20 is intended to supply two hydraulic users U1, U2. It should be noted that there can still be an even larger number of users, as indicated above.
  • the two users U1, U2 are for example formed by double-acting hydraulic actuators.
  • the hydraulic user U1 can however be represented by the actuation of any other hydraulic equipment. It will in fact be appreciated that the same inventive concepts set forth in connection with the present invention are also applicable to other solutions, like a hydraulic motor. For this reason, hereafter the term "hydraulic user" will be used to refer to any hydraulic equipment intended to be actuated by means of a hydraulic circuit with one or more working sections.
  • the supply group 20 is intended to provide the fluid required to operate these actuators, which is provided to them by means of the distributor 100.
  • a segment directed to tank is also defined, generically indicated by T, in which the operating fluid being discharged from the users flows.
  • the distributor 100 comprises a supply segment 1 connected to the supply group 20 and through which the fluid flow rate is directed to the individual sections of the distributor 100.
  • the distributor 100 may have a plurality of working sections 101, each one intended to operate a respective hydraulic user U1,..., Un.
  • the distributor 100 comprises two working sections 101, 102, connected to a respective actuator or more generally to a respective hydraulic user U1, U2.
  • each section 101, 102 comprises a spool 2 for operating the hydraulic actuator U1, U2 and a pressure compensator 3, the operating characteristics of which will be better illustrated below.
  • the spool 2 defines a delivery segment 11, connected to the supply segment 1, and a discharge segment 12, for the management of the discharge flows.
  • the spool 2 is configured in such a way as to operate the respective hydraulic user in one or the opposite direction depending on the position of the spool itself.
  • a first connection stretch 21 and a second connection stretch 22 can be provided in the section 101, 102 to which the spool 2 sends the flow rate provided by the delivery segment 11, depending on the positioning of the spool 2.
  • the discharge segment 12 defined by the spool 2 is advantageously intercepted at the outlet of the spool 2, by the compensator 3.
  • the compensator 3 can therefore comprise at least three ways.
  • a first way 3a is connected to the discharge segment and intercepts the discharge segment 12 itself, a second way 3b is connected to discharge, that is to say to the segment connecting to the tank T and a third way 3c connects the discharge segment 12 with an energy recovery stretch 13 connected in turn to the energy recovery device 5.
  • the compensator 3 makes it possible to compensate for the pressures present in the system as a function of the position of its continuously positioned spool.
  • the pressure compensator 3 is advantageously configured such that acting on the first side 31 thereof is a local pressure Ploc taken at the delivery segment 11 and acting on the second side 32, opposite the first side 31 is a maximum Load Sensing pressure PLSmax.
  • the local pressure PLoc is taken at a primary stretch 11b of the delivery segment 11 located downstream of said spool 2 and upstream of said pressure compensator 3, in the embodiment of Figure 2 , and upstream of the users more generally.
  • the pressure is taken immediately upstream of the compensator 3, i.e. there are no hydraulic components interposed between the point where the pressure PLoc is taken and the compensator 3.
  • a spring, or other equivalent elastic element 33 further acts on the side 31 in addition to the local pressure PLoc.
  • the pressure PLSmax in the present case, in which only one hydraulic user is present, this pressure corresponds to the pressure characteristic of the working pressure of the hydraulic user U1.
  • the pressure PLSmax corresponds to the maximum Load Sensing pressure among all those characteristic of the hydraulic users present. This pressure is taken at a Load Sensing segment 14 which provides the supply group 20 with the Load Sensing signal.
  • Load Sensing pressure denotes the pressure value characteristic of each user that is sent to the supply group 20 to achieve flow rate regulation in the system, for example by regulating the displacement of the pump.
  • the compensator 3 can therefore make a continuous regulation based on the actual operating conditions of the system, moving the spool, and therefore compensating for the flow rates, so as to keep the system under a condition of dynamic equilibrium.
  • the position of the spool, and more generally of the pressure compensator 3, is also advantageously detected by a position sensor 4.
  • This position sensor for example made by means of a position transducer, makes it possible to read the operating position of the pressure compensator 3, thus determining which ways are open and which are partially choked or closed.
  • This position sensor can be of the LVDT, Hall effect, potentiometric type, and in general any type suitable to be read and processed by the control unit.
  • the compensator 3 diverts the flow simultaneously towards discharge and towards the energy recovery stretch.
  • the flow is directed only to the energy recovery device.
  • the way to the energy recovery device is also progressively choked or possibly closed.
  • This information can then be sent to a control unit 6 interfaced with the energy recovery device 5.
  • the compensator is positioned between the first and the second position, that is, with the way 3b connected directly to discharge T completely closed and the way 3c, connected to the recovery stretch 13, minimally choked.
  • Figure 1 illustrates an example embodiment of the energy recovery device 5, in which the use of a hydraulic motor 50 that drives an electric generator 53 is provided.
  • the hydraulic motor 50 is advantageously driven by a fluid flow rate provided through the energy recovery stretch 13 in such a way as to provide energy to a rechargeable battery, or other energy storage device 51, by means of the electric generator 53.
  • the circuit may further comprise regulating means 52 configured to vary the pressure upstream of the hydraulic motor 50.
  • Such regulation can, for example, take place by using an inverter 60 associated with the generator 53 to regulate resistant torque and/or speed values thereof.
  • the presence of the position sensor 4 on the compensator 3 is a functional part for reading the status of the system and the correct feedback on the energy recovery device 5.
  • the control unit 6 can process in real time the position of the compensator 3 detected through the sensor 4 and through a control algorithm, defined by the user depending on the application, it can vary the resistant torque and/or the speed of the generator and consequently bring the compensator 3 to its optimal working position.
  • the compensator 3 intercepts both the discharge segment 12 and the delivery segment 11 defined by the spool 2.
  • the spool 2 preferably intercepts the delivery segment 11 defining a connection stretch 11a that brings the fluid to the spool 2 and a primary stretch 11b that connects the spool 2 to the pressure compensator 3.
  • the compensator 3 is of the type having at least five-ways.
  • a fourth way 3d and a fifth way 3e intercept the delivery segment 11.
  • the fourth way 3d is in particular connected to the primary stretch 11b, while the fifth way 3e is connected to a secondary stretch 11c of the delivery segment 11, which brings the flow rate of operating fluid back to the main spool 2 after passing through the compensator 3.
  • This flow rate of operating fluid can then be sent to the hydraulic user Un, operating it in one or the opposite direction depending on the position of the main spool 2 in the same way as illustrated above via the connection stretches 21 and 22.
  • the compensator 3 allows to choke the passage of the fluid both along the delivery stretch and along the discharge stretch.
  • passageways 3a, 3b, 3c, 3d and 3e are configured such as to define a passage port of the delivery segment and a passage port on the discharge segment.
  • passage ports can be chocked according to the position of the spool of the compensator 3 which position is read by means of the position sensor 4 in order to be sent to the control unit 6 with an operating principle similar to the previously described embodiment.
  • the passageways 3a, 3b, 3c, 3d and 3e are configured such that the passage port on the discharge segment 12 has a smaller surface area than said passage port defined on the delivery segment 11.
  • the compensation will mainly occur on the discharge segment, but the share part of compensation on the delivery segment can help reduce the undesirable effects of increased pressures and system instability.
  • Different sizings of the ports advantageously allow to obtain different behaviours in the compensator and in general in the system.
  • control unit can operate according to specific algorithms that will allow to optimise the energy recovery functions according to the specific operating needs or to the specific application.
  • circuit of the present invention allows the compensation and energy recovery functions to be realised effectively, with a high degree of versatility and efficiency in handling the different operating conditions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forklifts And Lifting Vehicles (AREA)
EP22175917.8A 2021-05-28 2022-05-27 Hydraulic distributor with compensator device for directional valves and hydraulic circuit comprising the same Pending EP4095393A1 (en)

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IT102021000014123A IT202100014123A1 (it) 2021-05-28 2021-05-28 Distributore idraulico con dispositivo di compensazione per valvole direzionali

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3930553A1 (de) 1989-09-13 1991-03-14 Bosch Gmbh Robert Hydraulische steuereinrichtung fuer einen hubantrieb
EP2028376A2 (de) * 2007-08-22 2009-02-25 Robert Bosch GmbH Hydraulische Steueranordnung
WO2014012608A1 (de) * 2012-07-19 2014-01-23 Hydac System Gmbh Ventil, insbesondere stetigventil
IT201700042145A1 (it) * 2017-04-14 2018-10-14 Walvoil Spa Circuito idraulico con funzione combinata di compensazione e recupero energetico
EP3822492A1 (en) * 2019-11-13 2021-05-19 Walvoil S.p.A. Hydraulic circuit having a combined compensation and energy recovery function

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3930553A1 (de) 1989-09-13 1991-03-14 Bosch Gmbh Robert Hydraulische steuereinrichtung fuer einen hubantrieb
EP2028376A2 (de) * 2007-08-22 2009-02-25 Robert Bosch GmbH Hydraulische Steueranordnung
WO2014012608A1 (de) * 2012-07-19 2014-01-23 Hydac System Gmbh Ventil, insbesondere stetigventil
IT201700042145A1 (it) * 2017-04-14 2018-10-14 Walvoil Spa Circuito idraulico con funzione combinata di compensazione e recupero energetico
EP3822492A1 (en) * 2019-11-13 2021-05-19 Walvoil S.p.A. Hydraulic circuit having a combined compensation and energy recovery function

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