EP4030067A1 - Commande hydraulique pour machines hydrauliques - Google Patents

Commande hydraulique pour machines hydrauliques Download PDF

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Publication number
EP4030067A1
EP4030067A1 EP21151799.0A EP21151799A EP4030067A1 EP 4030067 A1 EP4030067 A1 EP 4030067A1 EP 21151799 A EP21151799 A EP 21151799A EP 4030067 A1 EP4030067 A1 EP 4030067A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic control
valve
port
connection
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
EP21151799.0A
Other languages
German (de)
English (en)
Inventor
Aniello Valiante
Christoph Siebert
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.)
XCMG European Research Center GmbH
Original Assignee
XCMG European Research Center GmbH
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 XCMG European Research Center GmbH filed Critical XCMG European Research Center GmbH
Priority to EP21151799.0A priority Critical patent/EP4030067A1/fr
Publication of EP4030067A1 publication Critical patent/EP4030067A1/fr
Pending legal-status Critical Current

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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
    • F15B11/04—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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31552—Directional control characterised by the connections of the valve or valves in the circuit being connected to an output member and a return line
    • F15B2211/31558—Directional control characterised by the connections of the valve or valves in the circuit being connected to an output member and a return line having a single output 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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

Definitions

  • the invention relates to a hydraulic control for hydraulic machines with elements that can be raised and lowered, such as shovel excavators, hydraulic winches, hydraulic cranes and the like, the hydraulic control having a first connection X designed as a control connection, a second connection B designed as a connection for the high-pressure side, and a third port A designed as a port for the low-pressure side and an outlet L to the tank and a hydraulically controllable, proportionally adjustable load-holding valve with a 2/2-way valve, which is actuated by means of a hydraulic control connected to the first port X against the restoring force of a spring the closed position can be brought in the direction of the open position, the load-holding valve being connected to the second port B on the one hand and being provided on the other with a control line which bew an additional closing force on the 2/2-way valve ect.
  • Hydraulic controls of this type are known in a wide variety of designs from practice.
  • the load-holding or lowering brake valve is often used as a safety device that is connected between the control valve and the hydraulic cylinder and is used to perform safety functions that prevent unwanted lowering under the dead weight of the load-carrying organ or the load effect of the carried load prevented.
  • dangerous sagging of the load or the load-carrying element of the machine should be prevented in order to avoid accidents in the event of a fault in the hydraulic system, since the control valve, with which the "lift”, “lower” and “stop” states can be switched, cannot perform these safety functions, especially in the event of a pipe burst.
  • Such known load-holding or lowering brake valves usually combine several functions, namely leak-free holding of the maximum load that occurs and pressure limitation of the pressure value that occurs on the load side, as well as control for intentional lowering of the load and a check valve function when lifting the load.
  • a proportional valve is tuned in such a way that the pressure on the control surface is always proportional to the resulting spool travel, i. H. the valve opens proportionally depending on the control pressure. With the same control pressures, the valve would always open to the same extent.
  • the object of the invention is to avoid the aforementioned disadvantages and to enable compensation that can be adjusted without parts of the valve having to be mechanically modified for this purpose, since this is not easily possible during operation.
  • a pressure relief valve, a device for generating a counterforce to the hydraulic control and a pressure divider consisting of two orifices are additionally provided, the pressure relief valve being connected on the input side to the second port B and from the second Port B is actuated via a control line to open at a preset pressure against the restoring force of a spring, and the pressure relief valve on the outlet side via the first orifice plate of the pressure divider, on the one hand with the device for generating a counterforce to the hydraulic control, and on the other hand via the second orifice plate of the pressure divider is connected to the drain L to the tank.
  • the effect on the hydraulic control of the 2/2-way valve that takes place in this respect changes the compensation without parts of the 2/2-way valve having to be changed mechanically for this purpose.
  • the device for generating a counterforce to the hydraulic control can be designed in the form of a piston or a surface that can be pressurized, so that a counterforce to the movement of the 2/2-way valve can be brought about in a simple manner.
  • the hydraulic control can be connected to the first port X via a check valve, with the check valve opening in the direction of the first port X.
  • the non-return valve is used to quickly relieve the pressure from port X via the orifice to the load-holding valve and the pressure relief valve as soon as the operator stops operating.
  • a faster closing can preferably take place when the operator ends the actuation, since otherwise the load-holding valve and the pressure-limiting valve would only close with a delay.
  • a further orifice can be provided between the first connection X and the check valve, so that the oil flow entering through connection X is limited to a safe level, so that the system reacts within a period of time that the operator can control.
  • the pressure-limiting valve can be provided with a hydraulic control, which is connected via the further orifice and a further orifice to the first port X in such a way that the check valve is connected between the two orifices, with the hydraulic control being activated in the opening direction against the restoring force of a further spring is designed to act, so that oil can flow over here.
  • the pressure-limiting valve can be provided with a control line on the output side, which causes an additional closing force on the pressure-limiting valve.
  • a further orifice can be provided between the second port B and the pressure-limiting valve.
  • a filter can preferably be provided downstream of the first connection X in the direction of flow, so that any particles present in the oil entering through connection X are filtered out and cannot impair the function of components through which flow occurs.
  • a filter can also be provided downstream of port B in the direction of flow, so that any particles present in the oil entering through port B are filtered out and cannot impair the function of components through which flow occurs.
  • the ratio of the areas on the pressure relief valve can be selected such that the pressure relief valve can only open against the springs when the pressure present at the first port X is greater than the pressure on the hydraulic control of the pressure relief valve on the one hand and that on the second Connection B applied Pressure is greater than the "set pressure" of the pressure relief valve on the other hand.
  • the 2/2-way valve can have an integrated non-return function, which allows a volume flow in the direction from port A to port B.
  • the 2/2-way valve can be a leak-free valve.
  • FIG. 1 An exemplary embodiment of the invention shown in the drawing is explained below.
  • the single figure shows a hydraulic control system for hydraulic machines with organs that can be raised and lowered, such as power shovels, hydraulic winches, hydraulic cranes and the like.
  • the hydraulic control has a load-holding valve 1 and a first connection X designed as a control connection, via which the load-holding valve 1 is actuated, i. H. can be opened.
  • the hydraulic control comprises a second connection B designed as a connection for the high-pressure side, to which the drive is connected, the load of which is to be held, ie z. B. a hydraulic cylinder not shown in the drawing.
  • the hydraulic control is provided with a third connection A designed as a connection for the low-pressure side, to which the line that essentially leads to the pump or to the main control valve block is connected.
  • a third connection A designed as a connection for the low-pressure side, to which the line that essentially leads to the pump or to the main control valve block is connected.
  • an outflow to the tank L is provided, which usually has no or only a very small dynamic pressure.
  • the hydraulic control also includes a hydraulically controllable, proportionally adjustable load-holding valve 1 with a 2/2-way valve 1.1, which can be brought from the closed position in the direction of the open position against the restoring force of a spring 1.2 by means of a hydraulic control 1.4 connected to the first port X is.
  • the load-holding valve 1 is connected to the second port B on the one hand and to the other provided with a control line 1.5, which causes an additional closing force on the 2/2-way valve 1.1.
  • a pressure-limiting valve 3 a device 1.3 designed in the form of a piston for generating a counterforce to the hydraulic control 1.4 and a pressure divider 2 consisting of two orifices 2.1, 2.2 are provided.
  • the pressure relief valve 3 is connected on the input side to the second port B and is acted upon accordingly by the second port B via a control line 3.2 to open at a preset pressure against the restoring force of a spring 3.1.
  • the pressure-limiting valve 3 is connected on the outlet side via the first orifice plate 2.1 of the pressure divider 2 to the device 1.3 for generating a counterforce to the hydraulic control 1.4 and on the other hand via the second orifice plate 2.2 of the pressure divider 2 to the outflow to the tank L.
  • the hydraulic control 1.4 is connected to the first port X via a check valve 4, with the check valve 4 opening in the direction of the first port X.
  • a further orifice plate 5 is in turn provided between the first connection X and the check valve 4 .
  • the pressure-limiting valve 3 is provided with a hydraulic control 3.4, which is connected via the additional orifice 5 and an additional orifice 6 to the first connection X in such a way that the check valve 4 is connected between the two orifices 5, 6.
  • the hydraulic control 3.4 is designed to act in the opening direction against the restoring force of a further spring 3.5, so that oil can flow off here.
  • the pressure relief valve 3 is also provided with a control line 3.3 on the outlet side, which causes an additional closing force on the pressure relief valve 3.
  • a further orifice plate 7 is provided between the second connection B and the pressure-limiting valve 3 in order to set the pressure acting on the hydraulic control 3.4.
  • the ratio of the areas on the pressure relief valve 3 is selected so that the pressure relief valve 3 can only open against the springs 3.1, 3.5 when the pressure present at the first port X is greater than the pressure on the hydraulic control 3.4 of the pressure relief valve 3 on the one hand and the pressure present at the second port B is greater than the "set pressure" of the pressure relief valve 3 on the other hand.
  • the pressure of the control signal coming from port X, acting on the control surface 1.4, can then cause the 2/2-way valve 1.1 to open.
  • the force generated by this pressure must be greater than the sum of the forces from the spring 1.2 and the pressure 1.5. and the pressure by the piston 1.3.
  • the operating pressure from which the additional compensation begins can now be adjusted by selecting the opening pressure of the pressure-limiting valve 3.
  • a force that also acts in the opening direction is generated on the pressure-limiting valve via a control line 3.2, so that the pressure-limiting valve 3 can only open if it has been released for this purpose by the operator, in that a pressure is present at port X that is greater than that for the release required pressure.

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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)
EP21151799.0A 2021-01-15 2021-01-15 Commande hydraulique pour machines hydrauliques Pending EP4030067A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21151799.0A EP4030067A1 (fr) 2021-01-15 2021-01-15 Commande hydraulique pour machines hydrauliques

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21151799.0A EP4030067A1 (fr) 2021-01-15 2021-01-15 Commande hydraulique pour machines hydrauliques

Publications (1)

Publication Number Publication Date
EP4030067A1 true EP4030067A1 (fr) 2022-07-20

Family

ID=74186474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21151799.0A Pending EP4030067A1 (fr) 2021-01-15 2021-01-15 Commande hydraulique pour machines hydrauliques

Country Status (1)

Country Link
EP (1) EP4030067A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1143151A1 (fr) * 1999-10-20 2001-10-10 Hitachi Construction Machinery Co., Ltd. Appareil de vanne de commande a rupture de conduit
WO2007019712A1 (fr) * 2005-08-19 2007-02-22 Bucher Hydraulics Ag Montage pour commander un cylindre d'entrainement hydraulique a double effet
WO2014041710A1 (fr) * 2012-09-14 2014-03-20 株式会社小松製作所 Dispositif de vanne antidérive et circuit hydraulique
EP3205888A1 (fr) * 2014-10-06 2017-08-16 KYB-YS Co., Ltd. Dispositif de régulation de pression de fluide

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1143151A1 (fr) * 1999-10-20 2001-10-10 Hitachi Construction Machinery Co., Ltd. Appareil de vanne de commande a rupture de conduit
WO2007019712A1 (fr) * 2005-08-19 2007-02-22 Bucher Hydraulics Ag Montage pour commander un cylindre d'entrainement hydraulique a double effet
WO2014041710A1 (fr) * 2012-09-14 2014-03-20 株式会社小松製作所 Dispositif de vanne antidérive et circuit hydraulique
EP3205888A1 (fr) * 2014-10-06 2017-08-16 KYB-YS Co., Ltd. Dispositif de régulation de pression de fluide

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