EP3527833A1 - Circuit d'alimentation à commande à pression réglable - Google Patents

Circuit d'alimentation à commande à pression réglable Download PDF

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Publication number
EP3527833A1
EP3527833A1 EP19154068.1A EP19154068A EP3527833A1 EP 3527833 A1 EP3527833 A1 EP 3527833A1 EP 19154068 A EP19154068 A EP 19154068A EP 3527833 A1 EP3527833 A1 EP 3527833A1
Authority
EP
European Patent Office
Prior art keywords
line
control
return
valve
drainage
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.)
Granted
Application number
EP19154068.1A
Other languages
German (de)
English (en)
Other versions
EP3527833B1 (fr
Inventor
Massimo Baraldi
Simone Bruni
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.)
Bosch Rexroth Oil Control SpA
Original Assignee
Bosch Rexroth Oil Control 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 Bosch Rexroth Oil Control SpA filed Critical Bosch Rexroth Oil Control SpA
Publication of EP3527833A1 publication Critical patent/EP3527833A1/fr
Application granted granted Critical
Publication of EP3527833B1 publication Critical patent/EP3527833B1/fr
Active 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
    • 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
    • F15B11/024—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
    • F15B2011/0243—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 the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/67—Methods for controlling pilot 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the subject of the present invention is a supply circuit for an oil-hydraulic actuator.
  • the circuit can be used for example for the supply of an oil-hydraulic cylinder.
  • the majority of earthmoving or heavy lifting machines are provided with one or more oil-hydraulic cylinders for operating equipment or a power tool, such as a digging bucket or a forklift, connected to a movable arm.
  • Each arm is provided with an actuator cylinder which produces movement of the arm between a raised and a lowered position.
  • a working fluid is directed into a first chamber of the actuator cylinder while a second chamber of the actuator cylinder is connected to a reservoir so that the working fluid initially present in the second chamber is discharged.
  • the first chamber is disposed on the side of the cylinder bottom and, when energized, causes the cylinder shaft to exit and lift the load.
  • the second chamber is located on the side of the cylinder shaft and, when energized, causes the shank to retract and the load to descend.
  • a first circuit branch connects a hydraulic distributor associated with a pump with the chamber of the actuator, which is associated with the lifting of the load
  • a second branch connects the manifold with the chamber associated with the lowering of the load
  • the circuit is provided with a balancing valve, which is provided for the control of the liquid flow rate along the first branch in the phase of lowering the load.
  • a control line takes from the second branch a control pressure, the Opening of the compensation valve in the phase of lowering the load acts.
  • the return line is generally provided with a check valve which allows only the flow directed from the rod side to the bottom side, and with a normally closed return valve which is controlled on opening by a control pressure taken from the supply line on the bottom side of the cylinder.
  • the recirculation valve requires controlled control to prevent it from opening too quickly.
  • a particularly critical situation of operation of the circuit which occurs when, starting from a position in which the rod is fully retracted into the cylinder, the extension of the rod is commanded.
  • the pressure trapped inside the chamber of the rod counteracts the pressure created in the chamber of the soil. This creates a pressure spike in the bottom side feed line, which also transfers to the pressure to control the recirculation valve.
  • the tip of the control pressure causes a sudden opening of the return valve, which brings a jerk of the rod forward with it.
  • a drainage line which connects the control line of the return valve to a drain.
  • This drainage line is provided with one or more drainage constrictions that control the oil flow rate.
  • the current solution has some disadvantages.
  • the object of the present invention is to provide a supply circuit for an oil hydraulic actuator, which allows to overcome the disadvantages of currently available circuits and devices.
  • An advantage of the circuit according to the invention is that it does not require continuous oil drainage, so that the necessary energy expenditure is limited.
  • the feed circuit according to the invention is used to feed a hydraulic cylinder which serves to cause the lifting and lowering of a load.
  • the lifting and lowering of the load are performed by a cylinder (C), which is shown schematically in the figures.
  • the cylinder (C) normally has two chambers (C1, C2) separated by a piston (P) to which the rod (S) associated with the load to be lifted is connected in different ways.
  • a first chamber (C1) typically the Chamber, which is located on the side of the cylinder bottom, serves to absorb the pressurized oil to cause the lifting of the load.
  • a second chamber (C2) arranged on the side of the rod of the cylinder (C) and therefore annular, is provided to receive oil and to cause the lowering of the load.
  • a manifold typically a four-port, three-port valve, is provided to direct the supply of pressurized oil to the first chamber (C1) or the second chamber (C2) and, at the same time, around the chamber which is not under pressure supplied oil in connection with a drain.
  • the distributor is not present since it is known to the person skilled in the art.
  • the manifold is provided with a slide which can assume a first position in which the first chamber (C1) is brought into communication with a source of pressurized fluid and the second chamber (C2) is connected to a drain is.
  • the slider may also assume a second position in which opposite connections are created compared to those in the first position.
  • the spool may also occupy a central position in which the first and second chambers (C1, C2) are not in communication with the source of pressurized fluid.
  • the control device comprises a first line (2) which is provided to connect the first chamber (C1) of the cylinder (C) to the distributor.
  • a second conduit (3) is provided to connect the second chamber (C2) of the cylinder (C) to the manifold.
  • a compensating valve (4) disposed on the first conduit (2) is provided to permit the free flow of liquid from the manifold to the first chamber (C1) and to allow the free flow of liquid from the first chamber (C1) to the manifold , only if it is fed by a control pressure that is above a predetermined value.
  • the balance valve (4) known to those skilled in the art has substantially the function of preventing the outflow of working fluid from the first chamber (C1) unless there is a precise command from an operator. This is necessary to prevent uncontrolled lowering of the load, even in the event of damage or fluid loss.
  • the balancing valve (4) essentially comprises a slide, which by a spring in a closed position is pushed, in which it prevents the flow of fluid from the first chamber (C1).
  • the supplied liquid for opening the spool of the balance valve (4) is taken from the second line (3) through a control line (6).
  • the equalizing valve (4) opens in a command to lower the load because the operating oil is supplied to the second chamber (C2) via the second line (3) to cause the lowering of the load.
  • the circuit according to the invention also comprises a return line (5) which connects the second line (3) with the first line (2).
  • the return line (5) is connected to a first section (21) of the first line (2), which is arranged between the equalizing valve (4) and the cylinder (C).
  • a return valve (7) is arranged on the return line (5).
  • This return valve (7) is movable on command between an open configuration in which it allows flow along the return line (5) and a closed configuration in which it prevents flow along the return line (5).
  • the return line (5) is preferably a check valve (51), in particular a check valve arranged, which allows only an oil flow from the second to the first line (3, 2) out.
  • the check valve (51) can be arranged before or after the return valve (7).
  • the return valve (7) comprises a slide which is movable between a closed position in which it completely closes the return line (5) and an open position in which it releases the oil flow return line (5).
  • the slide is pushed by a spring into the closed position, so that when there is no command, the return valve (7) remains in a closed configuration.
  • the circuit according to the invention comprises a control line (8) which connects the first line (2) and the return valve (7).
  • the control line (8) supplies pressure to the return valve (7) to drive the slider to the open position.
  • the resulting pressure is transmitted to the spool of the recirculation valve (7) via the control pipe (8), so that the spool shifts to the open position.
  • the supply circuit also includes a drainage line (9) connecting the control line (8) to a drain.
  • a drainage line (9) connecting the control line (8) to a drain.
  • the drainage line (9) is provided with a control valve (10) which is movable between an opening position of the drainage line (9) and a closing position of the drainage line (9).
  • the control valve (10) is normally in the open position and is driven by the existing pressure in the control line (8) in the closed position.
  • the check valve (10) comprises a spool movable between a closed position in which it completely closes the control line (8) and an open position in which it clears the oil flow control line (8).
  • the slider is pushed by a spring to the opening position while being pushed to the closing position by the pressure existing in the control line (8). If the pressure in the control line (8) does not produce more thrust than that exerted by the spring, the control valve (10) remains in the open position.
  • the control valve (10) shifts in the closed position.
  • control line (8) may be provided with one or more control constrictions (81, 82), which may be fixed or adjustable to control the flow rate in the control line (8).
  • control line includes a first control constriction (81) and a second constriction (82).
  • the drainage line (9) may be provided with one or more fixed or adjustable drainage constrictions (91) to control the flow rate.
  • the drainage line (9) can also be provided with a check valve (92), which is preferably designed as a check valve, which prevents the flow from the outlet to the control line (8).
  • control line (8) and the drainage line (9) at the height of a node (A) are fluidly miteinader connected.
  • the first control constriction (81) of the control line (8) lies in the section between the node (A) and the first line (2).
  • the second control restriction (82) is located in the section between the node (A) and the return valve (7).
  • the drainage constriction (91) of the drainage line (9) can be arranged indiscriminately on one or the other side of the control valve (10).
  • the check valve (10) produces the following effect.
  • the control valve (10) in the return valve (7) is integrated.
  • the return valve (7) is provided with a structured slide to cause the opening and closing of both the return line (5) and the drainage line (9).
  • the return valve (7) closes the return line (5) and opens the drainage line (9) (in FIG. 2 shown position).
  • the return valve (7) opens the return line (5) and closes the drainage line (9).
  • the return valve (7) is brought to the first position by a spring, while being brought to the second position by the pressure existing in the control line (8).
  • the operation of the circuit is essentially the same as that of the version of FIG.
  • the oil supply to the first line (2) produces the already described pressure peak.
  • the return valve (7) is located in the first Position, so that the pressure peak and a certain amount of oil to drain over the drainage line (9).
  • the pressure in the control line progressively increases until it reaches a value at which the return valve (7) moves to the second position in which the return line (5) opens and the drainage line (9) opens closes.
  • the check valve (10) is in the form of an electrovalve that can be normally opened (10a) or normally closed (10b).
  • the closing command for the control valve (10) is sent electrically from a control module.
  • the opening command is sent electrically by a control module.
  • the control module operates in a manner that is suitable for the embodiments in FIG. 1 and 2 described operation reproduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Eye Examination Apparatus (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
EP19154068.1A 2018-01-30 2019-01-29 Circuit d'alimentation à commande à pression réglable Active EP3527833B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT201800002172A IT201800002172A1 (it) 2018-01-30 2018-01-30 Circuito di alimentazione con pilotaggio a pressione regolabile.

Publications (2)

Publication Number Publication Date
EP3527833A1 true EP3527833A1 (fr) 2019-08-21
EP3527833B1 EP3527833B1 (fr) 2020-10-28

Family

ID=62044872

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Application Number Title Priority Date Filing Date
EP19154068.1A Active EP3527833B1 (fr) 2018-01-30 2019-01-29 Circuit d'alimentation à commande à pression réglable

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EP (1) EP3527833B1 (fr)
IT (1) IT201800002172A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202000002506A1 (it) * 2020-02-10 2021-08-10 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru
EP3862576A1 (fr) * 2020-02-10 2021-08-11 Robert Bosch GmbH Système de commande d'un cylindre d'actionnement d'une grue
IT202100000431A1 (it) * 2021-01-12 2022-07-12 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5220862A (en) * 1992-05-15 1993-06-22 Caterpillar Inc. Fluid regeneration circuit
JP2001107905A (ja) * 1999-10-14 2001-04-17 Tokimec Inc 破砕機用増速弁
JP2001116006A (ja) * 1999-10-19 2001-04-27 Hitachi Constr Mach Co Ltd 多段伸縮アームの油圧回路
JP2003097507A (ja) * 2001-09-27 2003-04-03 Hitachi Constr Mach Co Ltd 多段伸縮アームの油圧回路

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5220862A (en) * 1992-05-15 1993-06-22 Caterpillar Inc. Fluid regeneration circuit
JP2001107905A (ja) * 1999-10-14 2001-04-17 Tokimec Inc 破砕機用増速弁
JP2001116006A (ja) * 1999-10-19 2001-04-27 Hitachi Constr Mach Co Ltd 多段伸縮アームの油圧回路
JP2003097507A (ja) * 2001-09-27 2003-04-03 Hitachi Constr Mach Co Ltd 多段伸縮アームの油圧回路

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202000002506A1 (it) * 2020-02-10 2021-08-10 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru
EP3862576A1 (fr) * 2020-02-10 2021-08-11 Robert Bosch GmbH Système de commande d'un cylindre d'actionnement d'une grue
IT202100000431A1 (it) * 2021-01-12 2022-07-12 Bosch Gmbh Robert Sistema di controllo per un cilindro attuatore di una gru

Also Published As

Publication number Publication date
IT201800002172A1 (it) 2019-07-30
EP3527833B1 (fr) 2020-10-28

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