EP2428686B1 - Vorrichtung zur kontrolle eines hydraulischen betätigungswerkzeuges und steuerun des steigens und des senkens einer last - Google Patents

Vorrichtung zur kontrolle eines hydraulischen betätigungswerkzeuges und steuerun des steigens und des senkens einer last Download PDF

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Publication number
EP2428686B1
EP2428686B1 EP11179650.4A EP11179650A EP2428686B1 EP 2428686 B1 EP2428686 B1 EP 2428686B1 EP 11179650 A EP11179650 A EP 11179650A EP 2428686 B1 EP2428686 B1 EP 2428686B1
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Prior art keywords
descent
control valve
chamber
load
working
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EP11179650.4A
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English (en)
French (fr)
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EP2428686A1 (de
Inventor
Danilo Manfredi
Graziano Levoni
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NEM SRL
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NEM SRL
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • 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
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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

Definitions

  • the present invention relates to a system for controlling a hydraulic actuator for the rise and descent of a load.
  • a hydraulic circuit is generally used for controlling a cylinder provided with a stem connected to the load to be moved, with a first chamber which if supplied causes the rise of the load and with a second chamber which if supplied causes the descent of the load, see for example FR 2 328 868 A1 .
  • This circuit includes a directional valve, with 4 ways and 3 positions, which is connected to the descent and rise chambers through a first and a second working duct.
  • the second working duct in particular, is flow controlled by an over-center valve, which is normally closed and driven to open in order to allow the discharge of the rise chamber, which prevents the accidental lowering of the load.
  • the systems for driving the known type of over-center valve to open generally use pressure taken from the first working duct, or they use pressure from external sources of supply.
  • pressurization of the circuit is required in order to actuate the opening of the over-center valve with consequent energy consumption even to execute manoeuvres to lower the load, which if suitably controlled could occur spontaneously as a result of the force of gravity.
  • hydraulic or electro-hydraulic drives are required that use an external pressure source in order to actuate the opening of the over-center valve, which in this type of application is generally referred to as the descent control valve.
  • the lack of an independent driving line has limited the application of this system on lifting apparatuses as well.
  • systems that use electro-hydraulic drives exhibit the problem linked to the fact that, in the event of an outage of the electrical system, they do not allow manoeuvres to be executed to lower the load in an emergency in order to return the apparatus to a rest condition.
  • the aim of the present invention is to eliminate the above-mentioned drawbacks in the background art by providing a system for controlling a hydraulic actuator for the rise and descent of a load that makes it possible to reduce the energy consumption of the apparatus on which it is installed for the execution of manoeuvres to lower the load, and also to ensure that these manoeuvres can be executed correctly and in total safety even in the event of an outage of the system, thus making it possible to return the apparatus to a rest condition.
  • Another object of the present invention is that of not requiring changes in the general architecture of hydraulic circuits, and therefore being capable of being installed both on newly-built machines and on existing machines.
  • Another object of the present invention is to provide a simple structure, that is relatively easy and practical to implement, safe to use and effective in operation, and relatively low-cost.
  • the present system for controlling a hydraulic actuator for the rise and descent of a load comprising a directional valve for distributing a pressurized working fluid, from which the following branch out: a first working duct associated with a first chamber of said actuator adapted to actuate the descent of the load if supplied and a second working duct associated with a second chamber of said actuator which is adapted to actuate the rise of the load if supplied and a descent control valve for controlling the descent of the load which is arranged along said second working duct, is normally closed in the discharge direction and can be opened in the direction for supplying said second chamber and is driven hydraulically to open in the direction for discharge of said second chamber during descent of the load, characterized in that it comprises a line for driving said descent control valve which is in fluid connection with said second chamber and is flow controlled by a downstream pressure control valve, which is normally closed hermetically and is switched to open by actuation means, operable by an operator to obtain a preset pressure reduction, and has at least one inlet
  • the reference numeral 1 generally designates a system for controlling a hydraulic actuator 2 for the rise and descent of a load, not shown, of the type that is conventionally used on fixed and self-propelled lifting apparatuses.
  • the actuator 2 is generally of the linear type and is constituted by a conventional cylinder whose stem 3 is associated with the load and which is provided with a first chamber 4 that, if supplied with a pressurized working fluid of the type of hydraulic oil, actuates the descent of the load and with a second chamber 5 that, if supplied, actuates the rise of the load.
  • the actuator 2 could be of the rotating type, such as a hydraulic engine.
  • the system 1 comprises a conventional directional valve 6, of the type with 4 ways and 3 positions, not described in detail, whose corresponding ports are connected to a device for supplying oil under pressure (not shown), a discharge device (also not shown) and to the chambers 4 and 5 of the actuator 2.
  • the system 1 comprises a first working duct 7 and a second working duct 8 for the connection of corresponding ports of the directional valve 6, respectively, to the first chamber 4 and to the second chamber 5.
  • the system 1 comprises, moreover, a descent control valve 9 for controlling the descent of the load which is arranged along the second working duct 8.
  • the descent control valve 9 is normally closed in the discharge direction and can be opened in the direction for supplying the second chamber 5 and is hydraulically driven to open in the direction for discharge of the second chamber during descent of the load.
  • the system 1 comprises a line 10 for driving the descent control valve 9, which is in fluid connection with the second chamber 5 and is flow controlled by a downstream pressure control valve 11, which is normally closed hermetically and is switched to open by actuation means 12, operable by an operator to obtain a preset pressure reduction, for example in the order of magnitude of 25-30 bar independently of the pressure acting in the second chamber 5.
  • the pressure control valve 11 is provided with at least one inlet 13 associated with the second chamber 5 and at least one outlet 14 associated with the descent control valve 9 for driving the opening of the valve 9.
  • the driving line 10 branches out from the second working duct 8.
  • the descent control valve 9 is provided with a movable piston 16 in a corresponding seat and with at least one working chamber 15 for driving opening of the piston 16. Moreover, means are provided for the discharge of the working chamber 15 so as to allow the restoration of the closed condition of the descent control valve 9 once the step of lowering the load is concluded.
  • the pressure control valve 11 is preferably of the proportional type. Alternatively, it can be of the fixed-setting or adjustable type.
  • the actuation means 12 can be, for example, of the electrical, mechanical, hydraulic or pneumatic type, depending on the nature of the actuation of the pressure control valve 11.
  • the actuation means 12 are provided with a conventional joystick 17 or other element operable by an operator.
  • actuation means 12 can also be controlled by the actuation of the directional valve 6, or they can be dedicated to the pressure control valve 11.
  • Figures 1 and 3-7 exemplify embodiments of the system 1 with actuation means 12 of the electrical type, in which the joystick 17 is associated with an electronic controller 18 that manages the supply of electric current for the actuation to open the pressure control valve 11, which is of the spool type, and the directional valve 6.
  • Figure 2 shows an embodiment of the system 1 with actuation means 12 of the hydraulic type, in which the joystick 17 manages the supply of pressurized working fluid for the actuation of the pressure control valve 11 and of the directional valve 6.
  • the system 1 comprises means for supplying the working chamber 15 in an emergency which comprise a connection branch 19 interposed between the chamber and the first working duct 7.
  • the descent control valve 9 is provided with a single working chamber 15 and the connection branch 19 merges along the driving line 10 downstream of the outlet 14 in the direction for passing through during descent of the load.
  • the discharge means coincide with the emergency supplying means and the connection branch 19 is flow controlled by at least one choke 20.
  • the choke 20 offers resistance to the passage of the oil along the connection branch 19, thus enabling the working chamber 15 to be pressurized.
  • connection branch 19 serves to enable the discharge of the working chamber 15 when the descent step of the load has been concluded, and to restore the closed configuration of the descent control valve 9.
  • connection branch 19 it is possible to achieve the opening of the descent control valve 9, and thus the lowering of the load, by pressurizing the working chamber 15 by means of oil under pressure derived from the first working duct 7, which is also supplied with oil under pressure, through the connection branch 19 and the corresponding choke 20.
  • the descent control valve 9 is provided with a first working chamber 15a, which operates on a first driving area of the piston 16, which is supplied by means of the driving line 10, and a second working chamber 15b, which operates on a second driving area of the piston 16, which has a smaller extension than the first one and is supplied through the connection branch 19.
  • the discharge means coincide with the connection branch 19 to discharge the second working chamber 15b and comprise a connecting portion 35, which is interposed between the driving line 10 and the connection branch and is flow controlled by at least one choke 20 for discharging the first working chamber 15a.
  • the choke 20 offers resistance to the passage of the oil along the connecting portion 35 in the step of supplying the driving line 10, thus enabling the first working chamber 15a to be pressurized.
  • the connecting portion 35 branches off the driving line 10 downstream of the outlet 14 in the direction for passing through of the working fluid during descent of the load.
  • the driving to open the descent control valve 9 occurs by means of the pressurization of the second working chamber 15b through the connection branch 19 with the oil under pressure derived from the first working duct 7, which is also under pressure, in the event of an outage of the pressure control valve 11 or of the actuation means 12 or if the load acting on the actuator 2 changes direction.
  • the system 1 can be provided with a pressure reduction valve 34 arranged along the driving line 10 upstream of the inlet 13 in the direction for passing through during descent of the load.
  • This reduction valve 34 makes it possible to reduce phenomena of hysteresis thanks to a lower pressurization of the dynamic gaskets associated with the supply pressure.
  • the system 1 can be provided with a conventional flow control valve, which is normally closed and can be opened during descent of the load, and is arranged along the driving line 10 upstream of the inlet 13 in the direction for passing through during descent of the load.
  • This flow control valve can be provided in addition to or as a substitution of the reduction valve 34 and it ensures the maintaining of the load applied to the stem 3.
  • the flow control valve could be constituted by a two-way solenoid valve actuated, again, by the actuation means 12.
  • Figure 2 shows a possible constructive embodiment of an assembly 21 that incorporates the electrically-actuated pressure control valve 11 and the descent control valve 9 with a single working chamber 15 according to the circuit diagram in Figure 1 .
  • the assembly 21 comprises a monolithic body 22 in which the following are formed: sections of the first and of the second working duct, respectively, 7 and 8, the driving line 10, the connection branch 19 with the corresponding choke 20 and the accommodation seats of the descent control valve 9 and of the pressure control valve 11.
  • the piston 16 is provided in a single body and has a first end 16a directed toward the working chamber 15 and a second end 16b, opposite to the first, on which a first compression spring 24 operates for maintaining the closed configuration in the direction for discharge of the second chamber 5.
  • the first end 16a forms the driving area upon which the pressure supplied in the working chamber 15 acts.
  • the piston 16 is provided with a contoured median portion 16c, which abuts hermetically against a sleeve 25 which is kept pressed against the median portion and against a fixed abutment element 26 by a second compression spring 27 accommodated within the seat of the descent control valve 9.
  • the median portion 16c, the sleeve 25 and the second spring 27 provide the one-way valve incorporated in the descent control valve 9.
  • the pressure in the second working duct 8 at the gate A causes the movement to the right, with reference to the figure, of the sleeve 25 in contrast to the resistance offered by the second spring 27 and, therefore, the passage of oil, the piston 16 remaining stationary within its seat.
  • the pressure acting in the working chamber 15 on the first end 16a causes the movement to the left, with reference to the figure, of the piston 16 with consequent opening of the gap formed between the median portion 16c and the sleeve 25 which is prevented from moving to the left by the fixed abutment element 26.
  • the pressure control valve 11 is of the electrically actuated type and is provided with a spool 28 coupled to an electromagnetic core 29 which, through a stem 30, operates on a conical plug 31.
  • the pressure control valve 11 is, therefore, normally kept hermetically closed.
  • the difference between the electromagnetic force that opens the pressure control valve 11 and the reaction of the third spring 33 determines the extent of the pressurization of the driving chamber 15.
  • FIG 6 shows a possible embodiment of the assembly 21 in Figure 2 , of which the same reference numerals are used and to the description of which the reader is referred, in which the descent control valve 9 is provided with two working chambers 15a and 15b and the piston 16 with corresponding driving areas, according to the circuit diagram in Figure 5 .
  • the piston 16 is provided at its first end 16a with a slave cylinder 36 the free end 36a of which forms the first driving area exposed to the pressure supplied in the first working chamber 15a through the pressure control valve 11.
  • the first end 16a directed toward the slave cylinder 36, forms the second driving area exposed to the pressure supplied in the second working chamber 15b through the connection branch 19.
  • system according to the invention does not involve burdensome changes in the architecture and in the components of traditional circuits.

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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)

Claims (12)

  1. Ein System (1) zur Kontrolle eines hydraulischen Betätigungswerkzeugs (2) für die Anhebung und Senkung einer Last, das ein Steuerventil (6) zum Verteilen eines unter Überdruck gesetzten Treibmittels umfasst, wovon Folgendes abzweigt: eine erste Arbeitsleitung (7), verbunden mit einer ersten Kammer (4) des Betätigungswerkzeugs (2), ausgebildet, um die Senkung der Last, wenn versorgt, zu aktivieren, und eine zweite Arbeitsleitung (8), verbunden mit einer zweiten Kammer (5) des Betätigungswerkzeugs, die ausgebildet ist, um die Anhebung der Last, wenn versorgt, zu aktivieren, und ein Senkungs-Regelventil (9) zur Steuerung der Senkung der Last, das entlang der zweiten Arbeitsleitung (8) angeordnet und normalerweise in der Auslassrichtung geschlossen ist und in der Richtung zur Versorgung der zweiten Kammer (5) geöffnet werden kann und hydraulisch betätigt wird, um sich in die Richtung zur Leerung der zweiten Kammer während der Senkung der Last zu öffnen, weiter eine Leitung (10) zum Antreiben des Senkungs-Regelventils (9) aufweist, das in Fluidverbindung mit der zweiten Kammer (5) steht und von einem stromabwärts gelegenen Druckregelventil (11) durchflussgeregelt wird, dadurch gekennzeichnet, dass das Regelventil (11) normalerweise hermetisch geschlossen ist und zum Öffnen geschaltet wird von Betätigungsmitteln (12), die von einem Bediener betätigt werden können, um eine vordefinierte Druckminderung zu erzielen, und dadurch, dass es mindestens einen Einlass (13) hat, verbunden mit der zweiten Kammer (5), und mindestens einen Auslass (14), verbunden mit dem Senkungs-Regelventil (9), um die Öffnung des Ventils (9) zu aktivieren.
  2. Das System (1) gemäß Anspruch 1, dadurch gekennzeichnet, dass das Senkungs-Regelventil (9) mit einem beweglichen Kolben (16) und mit mindestens einer Arbeitskammer (15; 15a, 15b) zur Aktivierung der Öffnung des Ventils (9) ausgestattet ist, wobei weiter Mittel bereitgestellt sind, um die mindestens eine Arbeitskammer (15; 15a, 15b) zu entleeren, um den geschlossenen Zustand des Senkungs-Regelventils (9) wiederherzustellen.
  3. Das System (1) gemäß Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Betätigungsmittel vom elektrischen, mechanischen, hydraulischen oder pneumatischen Typ sind, je nach Art der Betätigung des Druckregelventils (11).
  4. Das System (1) gemäß einem oder mehreren der obigen Ansprüche, dadurch gekennzeichnet, dass die Betätigungsmittel (12) auch durch die Betätigung des Steuerventils (6) gesteuert werden.
  5. Das System (1) gemäß einem oder mehreren der obigen Ansprüche, dadurch gekennzeichnet, dass das Druckregelventil (11) vom Proportionaltyp ist.
  6. Das System (1) gemäß einem oder mehreren der obigen Ansprüche, dadurch gekennzeichnet, dass es Mittel für die Notversorgung der mindestens einen Arbeitskammer (15; 15b) aufweist, welche einen Verbindungszweig (19) aufweisen, der zwischen der Kammer und der ersten Arbeitsleitung (7) angeordnet ist.
  7. Das System (1) gemäß Anspruch 6, dadurch gekennzeichnet, dass das Senkungs-Regelventil (9) mit einer einzigen Arbeitskammer (15) ausgestattet ist und der Verbindungszweig (19) entlang der Antriebsleitung (10) stromabwärts vom Auslass (14) des Druckregelventils (11) in der Richtung zum Durchdringen der Leitung zur Senkung der Last übergeht.
  8. Das System (1) gemäß Anspruch 6, dadurch gekennzeichnet, dass das Senkungs-Regelventil (9) mit einer ersten Arbeitskammer (15a) ausgestattet ist, die auf einen ersten Antriebsbereich (16a) des Kolbens (16) einwirkt, welcher durch die Antriebsleitung (10) versorgt wird, und einer zweiten Arbeitskammer (15b), die auf einen zweiten Antriebsbereich (16b) des Kolbens einwirkt, der eine geringere Ausdehnung hat als der erste und durch den Verbindungszweig (19) versorgt wird.
  9. Das System (1) gemäß Anspruch 2 und 7, dadurch gekennzeichnet, dass die Ablassmittel mit den Notversorgungsmitteln zusammenfallen, wobei weiter mindestens eine Drossel (20) entlang dem Verbindungszweig (19) bereitgestellt ist.
  10. Das System (1) gemäß Anspruch 2 und 8, dadurch gekennzeichnet, dass die Ablassmittel mit dem Verbindungszweig (19) zusammenfallen, um die zweite Arbeitskammer (15b) zu entleeren, und einen Verbindungsabschnitt (35) aufweisen, der zwischen der Antriebsleitung (10) und dem Verbindungszweig angeordnet und von mindestens einer Drossel (20) zum Entleeren der ersten Arbeitskammer (15a) durchflussgesteuert wird.
  11. Das System (1) gemäß einem oder mehreren der obigen Ansprüche, dadurch gekennzeichnet, dass es ein zusätzliches Druckminderventil (34) aufweist, angeordnet entlang der Antriebsleitung (10) stromaufwärts von der Einlassöffnung (13) des Druckregelventils (11), angetrieben in der Richtung zum Durchdringen der Leitung für die Senkung der Last.
  12. Das System (1) gemäß einem oder mehreren der obigen Ansprüche, dadurch gekennzeichnet, dass es ein Druckregelventil aufweist, angeordnet entlang der Antriebsleitung (10), die normalerweise geschlossen ist und während der Senkung der Last geöffnet werden kann.
EP11179650.4A 2010-09-08 2011-08-31 Vorrichtung zur kontrolle eines hydraulischen betätigungswerkzeuges und steuerun des steigens und des senkens einer last Active EP2428686B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITMO2010A000253A IT1402421B1 (it) 2010-09-08 2010-09-08 Sistema di controllo di un attuatore oleoidraulico per la salita e la discesa di un carico

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EP2428686B1 true EP2428686B1 (de) 2013-11-20

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IT1402421B1 (it) 2010-09-08 2013-09-04 Nem S P A Sistema di controllo di un attuatore oleoidraulico per la salita e la discesa di un carico

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Publication number Priority date Publication date Assignee Title
SE393843B (sv) * 1975-10-21 1977-05-23 Monsun Tison Ab Anordning vid en lastmanovrerande medelst en riktningsventil styrd hydraulmotor for forhindrande av okontrollerbar lastrorelse i hendelse av leckage
FR2459894A1 (fr) * 1979-06-26 1981-01-16 Poclain Sa Dispositif de commande d'un recepteur a fluide sous pression.
IT1402421B1 (it) 2010-09-08 2013-09-04 Nem S P A Sistema di controllo di un attuatore oleoidraulico per la salita e la discesa di un carico

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