EP2620657B1 - Agencement de soupapes pour une machine de travail mobile - Google Patents

Agencement de soupapes pour une machine de travail mobile Download PDF

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Publication number
EP2620657B1
EP2620657B1 EP13150234.6A EP13150234A EP2620657B1 EP 2620657 B1 EP2620657 B1 EP 2620657B1 EP 13150234 A EP13150234 A EP 13150234A EP 2620657 B1 EP2620657 B1 EP 2620657B1
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EP
European Patent Office
Prior art keywords
valve
regeneration
arrangement according
control
valve arrangement
Prior art date
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Active
Application number
EP13150234.6A
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German (de)
English (en)
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EP2620657A3 (fr
EP2620657A2 (fr
Inventor
Wolfgang Kauss
Guillaume Fremiot
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2620657A2 publication Critical patent/EP2620657A2/fr
Publication of EP2620657A3 publication Critical patent/EP2620657A3/fr
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Publication of EP2620657B1 publication Critical patent/EP2620657B1/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B13/027—Check 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
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F15B2211/7054—Having equal piston areas
    • 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 invention relates to a valve arrangement for a consumer of a mobile work machine with a regeneration position according to the preamble of patent claim 1.
  • a differential cylinder of a stick of an excavator is supplied via such a valve arrangement.
  • a valve arrangement By applying pressure to a piston crown side of the differential cylinder in a working position of the valve arrangement, a lowering movement of the handle with a shovel and thus a digging movement takes place.
  • pressure is applied to one side of the annular surface of the differential cylinder, and thus the stem is lifted.
  • the pamphlets DE 10 2009 021 831 A1 and JP 2002-061605 A show a valve arrangement in which a separate regeneration slide is provided for regeneration. This automatically switches between working and regeneration positions, depending on the pressure on the piston surface side.
  • the regeneration slide adjusts a continuously variable throttle point so that there is a smooth transition between the work and regeneration positions.
  • the DE 10 2006 002 920 A1 discloses a valve arrangement in which the working position and the regeneration position are separate switching positions of a single control slide which must be actively switched from the outside.
  • the KR 2010 0044941 A discloses a valve assembly having a regeneration valve.
  • the aim of the present invention is to create a valve arrangement in which the switchover between regeneration and working position takes place automatically and smoothly. Vibrations of the regeneration slide, especially in the working position, should be avoided.
  • the present invention is intended to create a valve arrangement which offers advantages with regard to the retrofitting of the regeneration valve and with regard to the optimization of the available installation space.
  • the valve arrangement according to the invention has a metering or control valve via which a regenerable connection and a further connection of a consumer - for example a working cylinder or motor - of a mobile working machine can be supplied.
  • a separate regeneration valve with only two switching positions (fully open; fully closed) is provided, via which pressure medium can be diverted from the regenerable connection into a tank. Above a predetermined pressure difference between the connections, the regeneration valve is open and otherwise closed.
  • a main slide or control slide of the control valve has a common regeneration and working position. The control slide therefore does not have an operating position that is spaced apart from the regeneration position along a displacement path of the control slide.
  • the switchover takes place between the regeneration and working positions soft and automatic. Vibrations of the control slide are avoided by its common regeneration and working position.
  • valve arrangement according to the invention has advantages with regard to the retrofitting of the regeneration valve and with regard to the optimization of the available installation space.
  • the mobile work machine the consumer of which is connected to the valve arrangement according to the invention, can be a backhoe loader or a compact excavator or a mini excavator or a telescopic loader. Regeneration of the limited energy reserves is particularly advantageous in these machines.
  • control slide in the control valve is continuously adjustable, preferably hydraulically. An operator of the mobile machine can thus control the consumer continuously. This results in an area on a displacement path of the control slide along its longitudinal axis with a plurality of working positions and thus common regeneration positions.
  • the regeneration valve is a releasable non-return valve which is controlled directly with a control pressure acting in the opening direction, tapped from the further connection. This ensures that the check valve remains closed in the regeneration mode and that no pressure medium flowing back from the regenerable connection can flow to the tank via the check valve. Thus, all of the pressure medium flowing back from the regenerative connection flows to the control valve for regeneration. As soon as the force pulling on the consumer changes into a counterforce, i.e. the direction of the external force on the consumer changes, the working mode is recognized and the check valve opens. In this way, the pressure medium flowing back from the regenerative connection can flow off to the tank via the check valve with minimal resistance.
  • its closing spring has a low level of spring stiffness, so that practically no intermediate position can be established.
  • the consumer that can be supplied by the valve arrangement according to the invention is a differential cylinder.
  • the annulus of the differential cylinder must be connected to the regenerable connection.
  • the regeneration valve has an opening area and a closing area, the closing area being smaller than the opening area.
  • the ratio of closing area / opening area preferably corresponds approximately to the ratio of ring area / bottom area of a piston of the differential cylinder.
  • the bottom space of the differential cylinder can be connected to the regenerable connection.
  • the regeneration valve has an opening area and a closing area, the closing area being larger than the opening area.
  • the ratio of opening area / closing area preferably corresponds approximately to the ratio of ring area / base area of a piston of the differential cylinder.
  • the consumer that can be supplied by the valve arrangement according to the invention is a synchronous cylinder.
  • the regeneration valve has an opening area and closing area that are approximately the same size.
  • the opening area and the closing area can be arranged on two different valve bodies (e.g. closing body and opening piston) of the regeneration valve, which can be brought into contact with one another.
  • a regeneration line is opened in the common regeneration and working position (s), in which a non-return valve opening from the regenerable to the further connection is arranged.
  • An adjustable throttle can be arranged in or on the regeneration line.
  • the throttle can preferably be adjusted via the displacement path or the position of the control slide in the control valve.
  • the regenerable connection is connected to the tank via a throttled outlet via the common regeneration and working position (s) of the control slide.
  • This A throttled drain is important for a regeneration according to the second application example (e.g. boom cylinder) in order to dissipate the excess volume.
  • the throttled flow can discharge pressure medium that is not to be regenerated.
  • the throttled outlet or its throttle is formed on the control slide of the control valve.
  • FIG. 1 shows the embodiment of the valve assembly according to the invention.
  • This consists essentially of a control valve 1 and a separate regeneration valve designed as a releasable shut-off or check valve 2.
  • the valve arrangement 1, 2 is connected to a variable displacement pump 4 via a pump connection P and to a tank 6 via a tank connection T.
  • the valve arrangement 1, 2 serves (according to the in Figure 1 shown first application example) for supply of a differential cylinder 8 and is connected to an annular space 10 via a regenerable connection C2 and to a floor space 12 of the differential cylinder 8 via a further connection C1.
  • the differential cylinder 8 (in the case of which in Figure 1 Application example shown) for operating a (not shown) stick of an excavator.
  • Pressurization of the floor space 12 leads to a lowering of the handle and a shovel (also not shown). This function is particularly used for digging. Pressurization or supply of the annular space 10 leads to a lifting of the handle and the shovel.
  • the control valve 1 which is designed as a continuously adjustable 4/3-way valve, is used for the corresponding control and metering of a pressure medium flow from the variable displacement pump 4 to the respective connection C1 or C2.
  • the connections A, B are blocked in the spring-loaded basic position 0 of a control slide 14 shown).
  • a working position a which is also a regeneration position
  • the pump connection P is connected to the working connection B and thus the further connection C1 and thus the floor space 12 are acted upon with pressure medium.
  • a further working position b the pump connection P is connected to the working connection A and thus the connection C2 and thus the annular space 10 are acted upon with pressure medium.
  • a pressure medium connection from port A to port B is provided, via which the regeneration takes place.
  • a check valve 16 which opens from port A to port B, and a throttle 18, the opening cross section of which can be adjusted via the position or position of the control slide 14, are provided.
  • the releasable check valve 2 has a valve body 20 and a tank connection T, a connection from connection C2 to tank connection T being open in normal or working operation of the valve arrangement 1, 2 according to the invention, while in regeneration mode the connection from connection C2 to tank connection T is open the valve body 20 is shut off.
  • the check valve 2 has a control line 22 which is connected to a working line section 24 connecting the further connection C1 to a connection V1 of the check valve 2.
  • FIG Figure 2 shows the structural design of the regeneration valve, designed as a releasable check valve 2, of the valve arrangement according to FIG Figure 1 . It has an inlet, which is connected to the regenerable connection C2, and an outlet or tank connection T. Furthermore, the check valve 2 connects the further connection C1 and the connection V1, between which the working line section 24 is formed. Depending on the setting of control valve 1 (cf. Figure 1 ) Pressure medium from this to the bottom space 12 of the differential cylinder 8 (cf. Figure 1 ) or the other way around.
  • the check valve 2 has a bushing 26 which is screwed into a housing 28 and in which the valve body 20 is prestressed in a closing direction by a closing spring 30.
  • a connection from the regenerable connection C2 to the tank connection T is blocked, so that the pressure medium displaced from the annular space 10 can be regenerated via the main valve 1.
  • the pressure prevailing at the regenerable connection C2 also acts in the closing direction of the valve body 20.
  • the pressure prevailing at the further connection C1 acts against this in an opening direction of the valve body 20.
  • a control pressure chamber 31 acting in the opening direction is connected via the control line 22 and via the working line section 24 to the further connection C1.
  • the control pressure chamber 31 is limited by an opening surface 33 of an opening piston 32, which can be brought into contact with the valve body 20 and then acts on the valve body 20 with an opening force depending on the working pressure at the further connection C1.
  • the bridge channel 40 connects the metering pressure chamber 44 via a load-holding valve 54 with the two bridge pressure chambers 42, 48.
  • the check valve 16 is located inside the control slide 14 (cf. Figure 1 ) arranged. This has at least a first radial bore 58 and at least a second radial bore 62.
  • the check valve 16 opens when there is a flow from the first radial bore 58 to the second radial bore 62, while conversely it closes when the pressure is predominantly applied via the second radial bore 62.
  • a valve body or switching piston 60 of the check valve 16 is movably arranged in a longitudinal bore of the control slide 14 and is secured by a closing spring 64 in the (in Figure 3 shown) closed position biased.
  • the switching piston 60 has a radially stepped back section, as a result of which an annular space 66 is formed with the longitudinal bore, which is always connected to the first radial bore 58.
  • a sealing section 68 is also attached to the radially recessed area of the switching piston 60, which in the (in Figure 3 shown) the closed position of the switching piston 60 blocks a connection from the second radial bore 62 to the radial bore 58.
  • the switching piston 60 of the check valve 16 can be acted upon by the pressure at the working port B via a longitudinal bore 63 and via a radial pressure reporting bore 65. This application takes place when the pressure reporting bore 65 is brought into connection with the pressure chamber 50. This is done by adjusting the control slide 14 (in Figure 3 ) to the left into the common regeneration and working position a. In this position a, which is in the Figures 4 and 5 is shown, the check valve 16 closes when the pressures at the working ports A and B are approximately equal.
  • the adjustable throttle 18 (cf. Figure 1 ) is formed by the second radial bore 62 and a control edge 70 arranged on the first bridge pressure chamber 42.
  • control slide 14 In order to connect the working port A to the pump port P and the working port B to the tank port T, the control slide 14 is in Figure 3 to the right into working position b (cf. Figure 1 ) postponed. This establishes a connection from the pump connection P via the pump pressure chamber 46, via a metering orifice 56b, the metering pressure chamber 44, the load holding valve 54, a section of the bridge channel 40, the first bridge pressure chamber 42, and the pressure chamber 38 to the working connection A.
  • Figure 4 shows the control valve 1 of the valve assembly 1, 2 according to the invention Figure 3 in regeneration mode. This is done with the (in Figure 4 shown) common regeneration and working position a of the control slide 14 is reached.
  • Figure 4 the first application example with the differential cylinder 8 and a second application example with a differential cylinder 108 are shown.
  • pressure medium for regeneration is displaced from the annular space 10 of the differential cylinder 8 via the regenerable connection C2 to the working connection A
  • pressure medium is displaced from a floor space 112 of the differential cylinder 108 via the regenerable connection C2 to the working connection A.
  • the pressure medium flows through the first radial bore 58, into the annular space 66 arranged inside the control slide 14.
  • the pressure medium flows further over the open check valve 16, over the adjustable throttle 18 and over the bridge channel 40 to port B.
  • First application example with the differential cylinder 8 the entire pressure medium displaced from its annular space 4 can be regenerated.
  • a throttled drain ST to tank T is provided between the pressure chamber 38 and the first tank pressure chamber 36. This has a groove formed on the control slide 14.
  • the throttled outlet ST serves to divert at least the excess pressure medium displaced from the floor space 112.
  • FIG. 5 shows the control valve 1 of the valve assembly 1, 2 according to the invention Figure 3 in normal or working mode. This is also supported by the in Figure 4 Regeneration and working position shown a of the control slide 14 is reached.
  • the pressure medium flows from the pump pressure chamber 46, via the metering pressure chamber 44, via the (in Figure 5 ) right section of the bridge channel 40 and via the pressure chamber 50 to the working connection B.
  • the from the variable displacement pump 4 (cf. Figure 1 ) conveyed pressure medium continues to be applied via the (in Figure 5 ) the left section of the bridge channel 40 and, via the throttle 18, the check valve 16 formed in the interior of the control slide 14, whereby the latter is closed.
  • the directional control valve or control valve 1 is equipped with a regeneration control slide 14.
  • the cross section of the throttled outlet ST serves to relieve pressure at the moment of the load reversal.
  • the hydraulically controlled shut-off or check valve 2 is arranged with the regenerable annular space 10 between the rod side or the annular space 10 and the bottom side or the bottom space 12 of the differential cylinder 8.
  • the check valve 2 remains closed.
  • the check valve 2 opens the rod side to the tank T and the compressive force of the cylinder bottom is available as a work force.
  • a changeover switch is integrated in the control slide 14 of the control valve 1.
  • the switching piston 60 accommodated therein is not connected to the pump connection P and the working connections A, B, er therefore has no influence on the internal leakage, since it is connected downstream of the closed control edges.
  • the first application example shows a digging position in which the ground resistance increases and the pressure difference between the working connections A, B decreases.
  • the smaller pressure difference leads to a reduction in the volume flow from working port A to working port B; the movement becomes slower the greater the digging resistance.
  • the pressure difference reaches the value specified by the closing spring 64, it moves the switching piston 60.
  • the regeneration connection from working port A to working port B is interrupted and the rod side is connected to tank T, that is, there is none on the rod side Back pressure generated more and the differential cylinder 8 can extend with maximum power against the ground resistance.
  • the boom of the compact excavator, the mast of the loader and the boom of the telehandler are driven by pressure cylinders according to the in Figure 4 second application example shown.
  • the differential cylinder 108 When the differential cylinder 108 is lowered or retracted, more oil is displaced on the bottom side than the rod side can absorb.
  • the regeneration circuit according to the invention can be used in order to reduce the hydraulic pump output with almost no hydraulic power.
  • the excess volume flow, which corresponds to the rod volume, is controlled via control notches of the throttled drain ST from the pressure chamber 38 via the first tank pressure chamber 36 to the tank 6.
  • the throttled outlet ST to the tank 6 provided in the control slide 14 can be omitted.
  • a shut-off of the return from the connection A to the tank connection T of the control valve 1 can be provided.
  • the load-holding valve 54 shown can be provided in the bridge channel 40 with a pressure compensator based on the principle of load-independent flow distribution (LUDV).
  • LUDV load-independent flow distribution
  • a valve arrangement for a mobile work machine with a metering or control valve via which a regenerable connection and a further connection of a consumer - for example a working cylinder or motor - of the mobile work machine can be supplied.
  • a separate regeneration valve with only two switching positions (fully open; fully closed) is provided, via which pressure medium can be diverted from the regenerable connection into a tank. Above a predetermined pressure difference between the connections, the regeneration valve is open and otherwise closed.
  • a main slide or control slide of the control valve has a common regeneration and Working position. The control slide therefore does not have a working position that is spaced apart from the regeneration position along a displacement path of the control slide, so that no active switching between working mode and regeneration mode is necessary.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Claims (16)

  1. Agencement de soupapes (1, 2) pour une machine de travail mobile, comprenant une soupape de commande (1) et une soupape de régénération (2) ;
    un raccord pouvant être régénéré (C2) et un raccord supplémentaire (C1) d'un consommateur (8 ; 108) pouvant être alimentés par le biais de la soupape de commande (1), la soupape de régénération (2) étant prévue avec seulement deux positions de commutation, et du fluide sous pression pouvant être conduit par celle-ci depuis le raccord pouvant être régénéré (C2) dans un réservoir (6), et la soupape de régénération (2), au-dessus d'une différence de pression prédéfinie entre les raccords (C1, C2), étant ouverte et sinon étant fermée, et un coulisseau de commande (14) de la soupape de commande (1) présentant une position de régénération et de travail commune (a), caractérisé en ce que la soupape de régénération (2) est réalisée sous forme de soupape séparée de la soupape de commande (1), avec un boîtier séparé (28), le boîtier (28) de la soupape de régénération (2) étant connecté à un boîtier de la soupape de commande (1) par le biais de conduites de fluide sous pression.
  2. Agencement de soupapes selon la revendication 1, dans lequel le coulisseau de commande (14) peut être déplacé en continu dans la soupape de commande (1), et dans lequel une région au niveau d'une course de déplacement du coulisseau de commande (14) est formée avec des positions de régénération et de travail communes (a).
  3. Agencement de soupapes selon la revendication 1 ou 2, dans lequel la soupape de régénération est une soupape antiretour libérable (2).
  4. Agencement de soupapes selon la revendication 3, dans lequel la soupape antiretour (2) est pilotée directement avec une pression de commande agissant dans la direction d'ouverture, prélevée au niveau du raccord supplémentaire (C1).
  5. Agencement de soupapes selon la revendication 3 ou 4, dans lequel la soupape antiretour (2) présente un ressort de fermeture (30) avec une faible rigidité de ressort.
  6. Agencement de soupapes selon l'une quelconque des revendications précédentes, dans lequel le consommateur est un cylindre différentiel (8) dont l'espace annulaire (10) est connecté au raccord pouvant être régénéré (C2).
  7. Agencement de soupapes selon la revendication 6, dans lequel la soupape de régénération (2) présente une surface d'ouverture (33) et une surface de fermeture et dans lequel la surface de fermeture est plus petite que la surface d'ouverture.
  8. Agencement de soupapes selon les revendications 1 à 5, dans lequel le consommateur est un cylindre différentiel (108) dont l'espace de fond (112) est connecté au raccord pouvant être régénéré (C2).
  9. Agencement de soupape selon la revendication 8, dans lequel la soupape de régénération (2) présente une surface d'ouverture et une surface de fermeture et dans lequel la surface de fermeture est plus grande que la surface d'ouverture.
  10. Agencement de soupapes selon les revendications 1 à 5, dans lequel le consommateur est un cylindre synchrone.
  11. Agencement de soupapes selon la revendication 10, dans lequel la soupape de régénération (2) présente une surface d'ouverture et une surface de fermeture qui sont approximativement aussi grandes l'une que l'autre.
  12. Agencement de soupapes selon l'une quelconque des revendications précédentes, dans lequel, dans la position de régénération et de travail commune (a), une conduite de régénération est commandée à l'ouverture, dans laquelle est disposée une soupape antiretour (16) s'ouvrant depuis le raccord pouvant être régénéré (C2) vers le raccord supplémentaire (C1).
  13. Agencement de soupapes selon la revendication 12, dans lequel un clapet d'étranglement ajustable (18) est disposé dans ou sur la conduite de régénération.
  14. Agencement de soupapes selon la revendication 13, dans lequel la conduite de régénération est réalisée avec la soupape antiretour (16) dans le coulisseau de commande (14), et dans lequel le clapet d'étranglement ajustable (18) est formé entre le coulisseau de commande (14) et le boîtier de la soupape de commande (1).
  15. Agencement de soupapes selon l'une quelconque des revendications précédentes, dans lequel, dans la position de régénération et de travail commune (a), le raccord pouvant être régénéré (C2) est connecté au réservoir (6) par le biais d'un écoulement étranglé (ST).
  16. Agencement de soupapes selon la revendication 15, dans lequel l'écoulement étranglé (ST) est réalisé au niveau du coulisseau de commande (14) de la soupape de commande (1).
EP13150234.6A 2012-01-27 2013-01-04 Agencement de soupapes pour une machine de travail mobile Active EP2620657B1 (fr)

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DE102012001562A DE102012001562A1 (de) 2012-01-27 2012-01-27 Ventilanordnung für eine mobile Arbeitsmaschine

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DE102015216833A1 (de) * 2015-09-03 2017-03-09 Robert Bosch Gmbh Entsperrbares Rückschlagventil für ein Schieberventil, Verfahren zum Ansteuern des entsperrbaren Rückschlagventils und Schieberventil mit dem entsperrbaren Rückschlagventil
JP6647826B2 (ja) * 2015-09-29 2020-02-14 ナブテスコ株式会社 方向切換弁及び油圧システム
DE102016111874A1 (de) * 2016-06-29 2018-01-04 Gustav Klauke Gmbh Verfahren zum Betreiben eines hydraulisch betriebenen Handgerätes sowie hydraulisch betriebenes Handgerät
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WO2018056037A1 (fr) * 2016-09-21 2018-03-29 Smc Corporation Vérin à pression de fluide
JP6673550B2 (ja) 2016-09-21 2020-03-25 Smc株式会社 流体圧シリンダの駆動方法及び駆動装置
JP6467733B1 (ja) * 2018-05-21 2019-02-13 Smc株式会社 流体圧シリンダの駆動方法及び駆動装置
JP7382792B2 (ja) * 2019-10-31 2023-11-17 川崎重工業株式会社 再生装置、それを備える液圧駆動システム、及びその制御装置

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CN103225632A (zh) 2013-07-31
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EP2620657A2 (fr) 2013-07-31
DE102012001562A1 (de) 2013-08-01

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