EP1984629B1 - Systeme de commande hydraulique a regeneration et soupape de frein d'abaissement - Google Patents

Systeme de commande hydraulique a regeneration et soupape de frein d'abaissement Download PDF

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Publication number
EP1984629B1
EP1984629B1 EP07711381A EP07711381A EP1984629B1 EP 1984629 B1 EP1984629 B1 EP 1984629B1 EP 07711381 A EP07711381 A EP 07711381A EP 07711381 A EP07711381 A EP 07711381A EP 1984629 B1 EP1984629 B1 EP 1984629B1
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EP
European Patent Office
Prior art keywords
valve
pressure
space
bore
arrangement according
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EP07711381A
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German (de)
English (en)
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EP1984629A1 (fr
Inventor
Thomas Weickert
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F15B11/024—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
    • F15B11/003—Systems with 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
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a consumer, in particular a hydraulic cylinder according to the preamble of patent claim 1.
  • Such a hydraulic control arrangement for driving a hydraulic cylinder is known for example from the data sheet "Structure and Function CLSS, Arm regeneration circuit” Komatsu.
  • This conventional control arrangement has a directional control valve, the valve spool for controlling the pressure fluid connection between a pressure medium source, a tank and two pressure chambers of the hydraulic cylinder is adjustable, and an axially parallel to the directional control valve in the control arrangement arranged Senkbremsventil for flow control of the pressure medium volume flow with pulling load, the control piston in the closing direction is acted upon by the force of a spring and in the opening direction of the pressure in the expanding pressure chamber.
  • Senkbremsventil for flow control of the pressure medium volume flow with pulling load, the control piston in the closing direction is acted upon by the force of a spring and in the opening direction of the pressure in the expanding pressure chamber.
  • For regeneration is pressure medium from the running pressure medium volume flow over a direction of increasing pressure chamber opening, outside the directional control valve radially arranged check valve branched into a regeneration
  • the US 5,832,808 B1 shows a hydraulic control arrangement for driving a hydraulic cylinder with a directional control valve, the valve slide for controlling the pressure medium connection between a pressure medium source, a tank and two pressure chambers of the hydraulic cylinder is adjustable.
  • pressure medium from the running pressure medium volume flow for regeneration via a direction of increasing pressure chamber opening, outside the directional control valve radially arranged check valve is also branched into a regeneration channel and summable to the pressure medium flow in the inlet.
  • a hydraulic control arrangement with all the features of the preamble of claim 1 is known from DE 196 50 798 A1 known.
  • This control arrangement has a directional control valve, the valve spool for controlling the pressure medium connection between a pressure medium source, a tank and two pressure chambers of the hydraulic cylinder is adjustable, and arranged at a distance and parallel to the valve spool of the directional control valve Senkbremsventil, which serves the flow control of the pressure medium volume flow at pulling load and the control piston is acted upon in the closing direction by the force of a spring and in the opening direction by the pressure in the expanding pressure chamber.
  • pressure medium from the running pressure medium volume flow can be branched off into a regeneration channel via a non-return valve which opens in the direction of the increasing pressure chamber and can be summed to form the pressure medium volume flow in the inlet.
  • the check valve is integrated in the valve spool of the directional control valve.
  • the invention has for its object to provide a control arrangement in which a compact design is possible with minimal device complexity.
  • the control arrangement according to the invention for controlling a consumer has a directional control valve, the valve slide for controlling the pressure medium connection between a pressure medium source, a tank and two pressure chambers of the consumer is adjustable, and a Senkbremsventil for flow control of the pressure medium flow from a decreasing pressure chamber, the control piston in the closing direction of the Force of a spring and is acted upon in the opening direction by the pressure in the increasing pressure chamber, wherein for regeneration pressure medium from the running pressure medium volume flow upstream of the lowering brake valve via a in the direction of increasing pressure chamber opening check valve in a regeneration line can be branched off and summed to the pressure medium volume flow in the inlet.
  • control piston of the lowering brake valve is arranged coaxially to the check valve in a common receiving bore of the valve slide.
  • the pressure acting on the lowering brake valve in the opening direction is signaled through the check valve.
  • the check valve preferably has a closing body, which is biased against a valve seat and has a through hole, so that the valve seat limited end face and a spring chamber defining the rear surface of the closing body is acted upon by the pressure in a control chamber of the valve spool, which increase the pressure in itself Pressure chamber corresponds.
  • control chamber is acted upon by at least one transverse bore in the valve spool with the pressure in the increasing pressure chamber.
  • the closing body is designed in a preferred embodiment as a stepped piston and has an arranged beyond the valve seat, acting in the opening direction annular shoulder, which is acted upon by the pressure in the decreasing pressure chamber.
  • the annular shoulder limits in sections a non-return valve inlet space which is connectable via at least one radial bore in the valve spool with a return space of a valve spool receiving the valve bore in which the pressure is applied upstream of the lowering brake valve.
  • the check valve is preferably preceded by a throttle for controlling the pressure medium volume flow in the regeneration line.
  • the throttle is formed by at least one opening in the radial bore throttle notch.
  • the closing body is preferably biased by the force of a compression spring against the valve seat, which is supported on the front side of the control piston of the lowering brake valve, which in turn is supported by the spring on a fixed in the receiving bore of the valve spool closure member.
  • control piston immersed in a blind hole of the closure part and limited with this a spring chamber of the spring.
  • control piston of the lowering brake valve is designed as a stepped piston.
  • This preferably has an axial bore, so that acting in the opening direction end face and a spring space defining in the closing direction acting back surface is acted upon by the pressure in the control chamber of the valve spool, which corresponds to the pressure in the increasing pressure chamber.
  • a throttle is preferably provided in the axial bore of the control piston.
  • the acting in the opening direction of the end face of the control piston has a relation to the rear surface larger cross section, so that the control piston is actuated by the pressure in the control chamber against the force of the spring in its open position. Due to the rear surface acting in the closing direction of the control piston, the spring can be dimensioned smaller.
  • a circumferential groove is introduced on the outer circumference of the control piston, which is acted upon via at least one jacket bore with the pressure in the decreasing pressure chamber and which can be connected in the open position of the control piston via tank holes in the valve slide with a drain chamber, so that pressure medium from the decreasing pressure chamber of the consumer can drain to the tank.
  • the receiving bore is designed as a blind hole.
  • load holding valves are arranged in an arc channel, the regeneration taking place via the receiving bore designed as an axial bore.
  • a logic valve is provided in the axial bore.
  • the spring chamber of a closing body of the logic valve is relieved in a preferred embodiment of the invention via at least one radial bore in the first working positions of the valve slide to the tank, which is closed in further working positions of the valve slide by a wall of the valve bore, so that the logic valve is locked in its closed position.
  • FIG. 1 shows a circuit diagram of a hydraulic control device 1 according to the invention for driving a consumer, for example, a double-acting hydraulic cylinder 2 of a mobile working device, not shown.
  • a pump 4 which is connected via a feed line 6 and a flow line 7 with a piston-side pressure chamber (cylinder chamber) 8 of the hydraulic cylinder 2.
  • a piston-side pressure chamber (cylinder chamber) 8 of the hydraulic cylinder 2.
  • a piston rod-side annular space 12 of the hydraulic cylinder 2 can be connected via a return line 14 with a tank 16.
  • the return line 14 is a continuously adjustable, provided with a throttle 18 Senkbremsventil 20 for sequence control of the pressure medium flow from the annular space 12 of the hydraulic cylinder 2 is arranged, the control piston 22 in the closing direction by the force of a spring 24 and in the opening direction via a control channel 26 from the pressure in Cylinder chamber 8 of the hydraulic cylinder 2 or more precisely acted upon by the pressure in the flow line 7.
  • Senkbremsventil 20 for sequence control of the pressure medium flow from the annular space 12 of the hydraulic cylinder 2 is arranged, the control piston 22 in the closing direction by the force of a spring 24 and in the opening direction via a control channel 26 from the pressure in Cylinder chamber 8 of the hydraulic cylinder 2 or more precisely acted upon by the pressure in the flow line 7.
  • FIG. 2 shows a first concrete embodiment of the control arrangement 1 according to the invention FIG. 1 ,
  • This has a directional control valve 34, with an inserted into a valve housing 35 valve bore 36 in which a valve slide 38 is guided axially displaceable.
  • the directional valve 34 has a directional part 40 and a speed part 42 via which, as will be explained in more detail below, the pressure medium flow direction or the pressure medium volume flow to the hydraulic cylinder 2 (see FIG. 1 ) is adjustable.
  • the valve bore 36 of the directional control valve 34 is in the radial direction from left to right to a drain chamber 44, a flow chamber 46, a downstream of a schematically indicated pressure compensator 48 disposed pressure compensator chamber 50, a compensation chamber 52, a upstream of the pressure compensator 48 arranged connecting space 54, an inlet chamber 56, a further pressure compensator space 58 arranged upstream of the pressure compensator 48, a return space 60 and a further outflow space 62 are expanded.
  • the pressure medium flow rate is kept constant by the metering orifice 10 independent of load.
  • These spaces 44 to 62 are spaced apart by annular webs 64 to 82 of the valve housing 35.
  • the two drainage spaces 44, 62 are connected to a tank connection T and the inlet space 56 to a pressure connection P.
  • the flow chamber 4 communicates with a working port A, via which the cylinder chamber 8 of the hydraulic cylinder 2 can be supplied with pressure medium (see FIG. 1 ).
  • the return chamber 60 is connected to a working port B, via which the annular space 12 of the hydraulic cylinder 2 according to FIG. 1 can be supplied with pressure medium.
  • the two pressure compensator chambers 50, 58 are connected to the pressure compensator outlet P "via an arc channel 84, so that the same pressure is applied in the chambers 50, 58.
  • the connecting chamber 54 communicates with a pressure compensator input P '.
  • a feed control groove 86, two horrinnuten 88, 90 and a montlaufberichtnut 92 are provided, which are bounded by annular collars 94 to 102.
  • fine control notches 104 of the return control groove 92 a control edge is formed, via which the connection between the return chamber 60 and the pressure compensator chamber 58 is opened or closed.
  • Vorlaufberichtnut 86 two control edges 106, 108 are formed.
  • the control edges 106, 108 are each designed with fine control notches 110.
  • FIG. 3 which the shifted to the right valve spool 38 of the directional control valve 34 from FIG. 2 shows, in these working positions, the connection from the connected to the pressure port P inlet space 56 to the connecting space 54 through the metering orifice 10 (ring collar 98) controlled, the control over the Feinêtkerbe 116 takes place.
  • the pressure medium can enter from the pressure port P via the inlet chamber 56 and the controlled metering orifice 10 into the connecting space 54 and from there via the pressure compensator 48 and the arc channel 84 into the pressure compensator chambers 50, 58.
  • the lowering brake valve 20 For flow control of the pressure medium flow from the annular space 12 of the hydraulic cylinder 2 at pulling load the directional control valve 34, the lowering brake valve 20 is assigned, the control piston 22 is acted upon in the closing direction by the force of the spring 24 and in the opening direction of the pressure in the cylinder chamber 8, wherein for the regeneration pressure medium from the expiring Pressure medium volume flow upstream of the lowering brake valve 20 via the in the direction of the increasing cylinder chamber 8 opening check valve 28 in the regeneration line 30 (see FIG. 1 ) can be branched off and summed to the pressure medium volume flow in the inlet.
  • the check valve 28 is integrated in the valve slide 38, wherein the pressure acting in the opening direction on the lowering brake valve 20 pressure is reported through the check valve 28 therethrough.
  • control piston 22 of the lowering brake valve 20 is coaxial with the check valve 28 in a common, formed as a stepped blind hole 120 extending in the axial direction receiving bore 122 of the valve slide 38 arranged in an end face 124 (right in FIG. 3 ) of the valve spool 38 opens.
  • FIG. 4 it can be seen that an enlarged view of the directional control valve 34 in the region of Check valve 28 and lowering brake valve 20 off FIG. 3 shows, the check valve 28 has a closing body 126 which is biased against a valve seat 128 of the valve spool 38 and having a through hole 130, so that a limited by the valve seat 128 end face 132 and a spring chamber 134 defining rear surface 136 with the pressure in a control chamber 138 of the blind hole 120 of the valve spool 38 is acted upon.
  • the control chamber 138 is acted upon on the one hand in a circumferential groove 140 of the valve spool 38 and on the other hand in the pressure compensator chamber 58 opening transverse bores 142 in the valve spool with the pressure in the cylinder chamber 8 of the hydraulic cylinder 2. Via the transverse bores 142, a connection from the pressure compensator chamber 58 to the blind borehole 120 is opened in the illustrated to the right shifted working positions of the valve slide 38.
  • the closing body 126 of the check valve 28 is designed as a stepped piston and has an open beyond the valve seat 128, acting in the opening direction annular shoulder 146.
  • the annular shoulder 146 is through radial bores 148 and in this emptying, the adjustable throttle 32 (see FIG. 1 ) forming throttle notches 150 via the return chamber 60 with the pressure in the annular space 12 of the hydraulic cylinder 2 acted upon.
  • the annular shoulder 146 defines a check valve inlet space 152, which is connectable via the radial bores 148 and the adjustable throttle 32 with the return chamber 60 in which the pressure is applied upstream of the lowering brake valve 20.
  • the through hole 130 of the closing body 126 has on the bottom side a radial extension at the first end portion of a compression spring 154 engages.
  • the compression spring 154 is supported with its second end portion on an end-face annular surface 156 of the control piston 22, which in turn with a stepped End portion 158 extends into the spring 24, which is supported on a closure member 160. This is screwed into the blind bore 120 at the end face and brought into abutment with an abutment shoulder 164 of the valve slide 38 via an annular flange 162.
  • the closing body 126 is biased against the valve seat 128.
  • the control piston 22 of the lowering brake valve 20 is designed as a stepped piston and extends with an end portion 166 in a bore 168 of the closure member 160 and limited with this a spring chamber 170 of the spring 24.
  • the control piston 22 has a radially projecting stop collar 174, which dips into a receiving space , which is limited on the one hand by a radial shoulder 178 of the valve slide 38 and the other by an annular end face 182 of the closure member 160, so that the axial displacement of the control piston 22 is limited by running on the radial shoulder 178 or on the annular end face 182.
  • the control piston 22 In the closing direction of the control piston 22 is biased by the spring 24 with a stop surface 176 of the stop collar 174 against the radial shoulder 178 of the stepped blind hole 120. In the opening direction, the stop collar 174 can be brought into contact with the annular end face 182 of the closure part 160 via a contact surface 180.
  • the receiving space of the stop collar 174 is connected in the illustrated, shifted to the right working position of the valve spool 38 via an obliquely running tank bore 184 in the valve spool with the return chamber 62 and thus relieved to the tank.
  • the control piston 22 has an axial bore 186, which opens via a throttle bore 187 in the spring chamber 170.
  • the end face 156 acting in the opening direction and a stepped rear face 188 delimiting the spring chamber 170 in the closing direction are acted upon by the pressure in the control chamber 138 of the valve slide 38, which corresponds to the pressure in the cylinder chamber 8, so that the spring 24 is supported by the force acting on the rear surface 188 of the control piston 22 force and thus a weaker spring 24 can be used, as if in the spring chamber 170, the tank pressure would act.
  • the end face 156, which acts in the opening direction of the control piston 22, has a larger cross section relative to the rear face 188, so that the control piston 22 can be actuated against the force of the spring 24 in its open position.
  • a circumferential groove 190 is inserted, which is connected via shell bores 192 to the return chamber 60 and is connected to the right shifted control piston 22 via oblique tank holes 194 in the valve spool with the drain chamber 62, so that pressure medium from the decreasing annulus 12th of the hydraulic cylinder 2 can flow to the tank 16 (see FIG. 1 ).
  • the throttle cross-section of the lowering brake valve 20 is determined by a control edge formed by an end face 191 of the circumferential groove 190.
  • the left shifted valve spool 38 from FIG. 2 shows, in these working positions, the connection from the inlet chamber 56 via the metering orifice 10 to the connecting space 54 is also controlled, so that the pressure compensator chambers 50, 58 are supplied with pressure medium.
  • the pressure compensator chamber 58 is connected via the fine control groove 104 with the return chamber 60, so that the annular space 12 of the hydraulic cylinder 2 (see FIG. 1 ) is supplied with pressure medium.
  • the flow chamber 46 is connected via the fine control notch 110 with the drain chamber 44, so that the cylinder chamber 8 to the tank 16 (see FIG. 1 ) is relieved.
  • the hydraulic cylinder 2 retracts.
  • valve spool 38 In the in FIG. 2 illustrated basic position (middle position) of the valve spool 38, the pressure port P and the working ports A, B are shut off. It is now assumed that the valve spool 38 from the in FIG. 2 shown basic position is shifted to the right.
  • the throttle notches 150 on the valve spool 38 in this case determine the size of the regenerated pressure medium flow in the small flow range.
  • the valve spool 38 from the in FIG. 2 shown basic position to the left, in his in FIG. 5 shifted work items shown.
  • the connection from the inlet space 56 via the metering orifice 10 to the connecting space 54 is controlled, so that the pressure compensator spaces 50, 58 are supplied with pressure medium.
  • the pressure compensator chamber 58 is connected via the fine control groove 104 and the remindlaufberichtnut 92 with the return chamber 60, so that the annular space 12 of the hydraulic cylinder 2 is supplied via the working port B with pressure medium.
  • the flow chamber 46 is connected via the flow control groove 86 and the fine control notch 110 with the drain chamber 44, so that the cylinder chamber 8 is relieved via the working port B to the tank 16.
  • the hydraulic cylinder 2 enters without regeneration.
  • control assembly 1 are provided with unlockable load-holding valves 196, which prevent a pressure fluid flow from the hydraulic cylinder 2 to the tank 16.
  • FIG. 6 shows a longitudinal section through an inventive directional control valve 198 according to an embodiment for leakage-free support of acted upon by a pulling load F hydraulic cylinder 2.
  • the basic structure of this directional control valve 198 corresponds to that of the FIGS. 2 to 5 , ie, in this variant, a check valve 28 and a lowering brake valve 20 are arranged coaxially in the valve spool 38, which in principle have the same structure as in the above-described embodiment.
  • This embodiment differs from that described above essentially in that in the bow channel 84 downstream the pressure compensator 48 is provided in each case one in the direction of the pressure compensator 48 closing unlockable load-holding valve 196 for leak-free support of the hydraulic cylinder 2.
  • valve spool 38 Since the regeneration can not take place in this variant due to the load-holding valves 196 via the bow channel 84, the valve spool 38 is provided in this embodiment with a continuous, stepped executed axial bore 200, on the shown in the left shifted working position of the valve spool 38, the pressure medium from the annular space 12 via the return line 14, the return chamber 60, the transverse bores 142 and the open via the annular shoulder 146 check valve 28 via a logic valve 202 to the flow chamber 46 can be fed.
  • the axial bore 200 is limited on the side of the flow chamber 46 via a screwed into the valve spool 38 screw 204, on which a spring 206, a closing body 208 of the logic valve 202 is supported, while on the side of the return chamber 60, as already explained, the check valve 28 and the lowering brake valve 20 are provided.
  • the closing body 208 of the logic valve 202 is biased against a valve seat 210 and has a throttle bore 212, so that an area bounded by the valve seat 210 face 213 and a spring chamber 214 limiting rear surface 216 is acted upon by the pressure in the axial bore 200 of the valve spool 38.
  • the closing body 208 of the logic valve 202 is embodied as a stepped piston and has an annular surface 218 arranged beyond the valve seat and acting in the opening direction, which can be acted upon by the working connection A and a jacket bore 220 with the pressure in the enlarging cylinder chamber 8 of the hydraulic cylinder 2.
  • the spring chamber 214 of the closing body 208 is in the illustrated, shifted to the left working position of the valve spool 38 via a circumferential gap 222 between the axial bore 200 and an outer peripheral portion of the screw plug 204 and via radial bores 224 relieved to the drain chamber 62, so that the logic valve 202 can be brought over the annular surface 218 and the end face 213 acted upon pressures in the flow chamber 46 and in the axial bore 200 against the force of the spring 206 in its open position.
  • FIG. 7 showing an enlarged view of the valve spool 38 shifted to the right in the area of the logic valve 202
  • the radial bores 224 are closed by a wall 226 of the valve bore 36 in this working position of the valve spool 38.
  • the logic valve 202 is locked and can not from the working port A via the flow control groove 86 to the tank 16 (see FIG. 1 ) running off pressure fluid flow over the radial shoulder 218 are turned on.
  • the flow chamber 46 is connected to the drainage chamber 62 via a fine control notch 228 which opens into the flow control groove 86.
  • a hydraulic control arrangement 1 for controlling a consumer, in particular a hydraulic cylinder 2, with a directional control valve 34, 198, the valve spool 38 is adjustable for controlling the pressure medium connection between a pressure medium source 4, a tank 16 and two pressure chambers 8, 12 of the consumer 2, and with a lowering brake valve 20 for sequence control of the pressure medium volume flow of a decreasing pressure chamber 12, the control piston 22 is acted upon in the closing direction by the force of a spring 24 and in the opening direction of the pressure in the expanding pressure chamber 8, wherein for regeneration pressure medium from the running pressure medium volume flow upstream of the lowering brake valve 20 via a in the direction of increasing pressure chamber 8 opening check valve 28 in a regeneration line 30th branched off and can be summed to the pressure medium volume flow in the inlet.
  • the check valve 28 is integrated in the valve slide 38, wherein the pressure acting in the opening direction on the lowering brake valve 20 pressure is reported through the check valve 28 therethrough.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (18)

  1. Système de commande hydraulique destiné à amorcer un consommateur, en particulier un cylindre hydraulique (2), avec une soupape de distribution (34, 198), dont le tiroir de soupape (38) est déplaçable pour commander la liaison de fluide sous pression entre une source de fluide sous pression (4), un réservoir (16) et deux chambres de pression (8, 12) du consommateur, et avec une soupape de frein d'abaissement (20) pour la commande de décharge du courant volumique de fluide sous pression à partir d'une chambre de pression qui se réduit (12), dont le piston de commande (22) est soumis dans la direction de fermeture à la force d'un ressort (24) et dans la direction d'ouverture à la pression dans la chambre de pression qui s'agrandit (8), dans lequel, pour la régénération, du fluide sous pression peut être dérivé du courant volumique de fluide sous pression de décharge en amont de la soupape de frein d'abaissement (20) par un clapet anti-retour (28) s'ouvrant en direction de la chambre de pression qui s'agrandit (8) et intégré dans le tiroir de soupape (38), vers une conduite de régénération (30) et peut être ajouté au courant volumique de fluide sous pression qui arrive, caractérisé en ce que le piston de commande (22) de la soupape de frein d'abaissement (20) est disposé coaxialement au clapet anti-retour (28) dans un alésage de réception commun (122) du tiroir de soupape (38) et en ce que la pression agissant sur la soupape de frein d'abaissement (20) dans la direction d'ouverture est signalée à travers le clapet anti-retour (28).
  2. Système de commande hydraulique selon la revendication 1, dans lequel le clapet anti-retour (28) comprend un corps de fermeture (126), qui est précontraint contre un siège de soupape (128) et présente un alésage de passage (130), de telle manière que la face frontale (132) limitée par le siège de soupape (128) et une face arrière (136) limitant une chambre de ressort (134) soient soumises à la pression dans une chambre de commande (138) du tiroir de soupape (38), qui correspond à la pression dans la chambre de pression qui s'agrandit (8).
  3. Système de commande hydraulique selon la revendication 2, dans lequel la chambre de commande (138) peut être soumise à la pression dans la chambre de pression qui s'agrandit (8) par au moins un alésage transversal (142) dans l'enveloppe latérale du tiroir de soupape.
  4. Système de commande hydraulique selon la revendication 2 ou 3, dans lequel le corps de fermeture (126) est réalisé sous la forme d'un piston étagé et comprend un épaulement annulaire (146) disposé de l'autre côté du siège de soupape (128) et agissant dans la direction d'ouverture, et qui peut être soumis à la pression dans la chambre de pression qui se réduit (12).
  5. Système de commande hydraulique salon la revendication 4, dans lequel l'épaulement annulaire (146) limite une chambre d'entrée de clapet anti-retour (152), qui peut être raccordée par au moins un alésage radial (148) dans l'enveloppe latérale du tiroir de soupape à une chambre de retour (60) d'un alésage de soupape (36) contenant le tiroir de soupape (38), dans laquelle règne la pression en amont de la soupape de frein d'abaissement (20).
  6. Système de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel un étrangleur (32) est monté en amont du clapet anti-retour (28).
  7. Système de commande hydraulique selon la revendication 5 et 6, dans lequel l'étrangleur (32) est formé par au moins une encoche d'étranglement (150) débuchant dans l'alésage radial (148).
  8. Système de commande hydraulique selon l'une quelconque des revendications 2 à 7, dans lequel le corps de fermeture (126) est précontraint contre le siège de soupape (128) par la force d'un ressort de pression (154), qui prend appui côté frontal sur le piston de commande (22) de la soupape de frein d'abaissement (20), qui prend appui de son côté via le ressort (24) sur une partie de fermeture (160) fixée dans l'alésage de réception (122).
  9. Système de commande hydraulique selon la revendication 8, dans lequel une partie d'extrémité (156) du piston de commande (22) plonge dans un alésage (168) de la partie de fermeture (160) et limite avec celle-ci une chambre de ressort (170) du ressort (24).
  10. Système de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel le piston de commande (22) de la soupape de frein d'abaissement (20) est réalisé sous la forme d'un piston étagé.
  11. Système de commande hydraulique selon la revendication 10, dans lequel le piston de commande (22) comporte un alésage axial (186), de telle manière qu'une face frontale (156) agissant dans la direction d'ouverture et une face arrière (188) limitant la chambre de ressort (170) et agissant dans la direction de fermeture soient soumises à la pression dans la chambre de commande (138) du tiroir de soupape (38), qui correspond à la pression dans la chambre de pression qui s'agrandit (8).
  12. Système de commande hydraulique selon la revendication 11, dans lequel un étrangleur (187) est prévu dans l'alésage axial (186) du piston de commande (22).
  13. Système de commande hydraulique selon la revendication 11 ou 12, dans lequel la face frontale (156) du piston de commande (22) agissant dans la direction d'ouverture présente une section transversale plus grande que la face arrière (188).
  14. Système de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel une rainure périphérique (190) est pratiquée sur la périphérie extérieure du piston de commande (22), rainure qui est soumise par au moins un alésage (192) de l'enveloppe latérale à la pression dans la chambre de pression qui se réduit (12) et qui peut être raccordée, dans la position d'ouverture du piston de commande (22), à une chambre de décharge (62) par des alésages de réservoir (194) dans l'enveloppe latérale du tiroir de soupape, de telle manière que du fluide sous pression puisse s'écouler de la chambre de pression qui se réduit (12) du consommateur (2) vers le réservoir (16).
  15. Système de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel l'alésage de réception (122) est réalisé sous la forme d'un alésage borgne (120).
  16. Système de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel des soupapes de retenue de charge (196) sont disposées dans un canal coudé (84) et la régénération est effectuée au moyen de l'alésage de réception (122) réalisé sous la forme d'un alésage axial (200).
  17. Système de commande hydraulique selon la revendication 16, dans lequel il est prévu une soupape logique (202) dans l'alésage axial (200).
  18. Système de commande hydraulique selon la revendication 17, dans lequel une chambre de ressort (214) d'un corps de fermeture (208) de la soupape logique (202) est déchargée vers le réservoir par au moins un alésage radial (224) dans des premières positions de travail du tiroir de soupape (38), qui, dans d'autres positions de travail du tiroir de soupape (38), est fermé par une paroi (226) de l'alésage de soupape (36) et la soupape logique (202) est bloquée dans sa position de fermeture.
EP07711381A 2006-02-09 2007-01-25 Systeme de commande hydraulique a regeneration et soupape de frein d'abaissement Active EP1984629B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006006228A DE102006006228A1 (de) 2006-02-09 2006-02-09 Hydraulische Steueranordnung
PCT/EP2007/000611 WO2007090522A1 (fr) 2006-02-09 2007-01-25 SystEme de commande hydraulique A regeneration et soupape de frein d'abaissement

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EP1984629A1 EP1984629A1 (fr) 2008-10-29
EP1984629B1 true EP1984629B1 (fr) 2013-03-13

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JP (1) JP4824777B2 (fr)
KR (1) KR101011944B1 (fr)
DE (1) DE102006006228A1 (fr)
WO (1) WO2007090522A1 (fr)

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KR101868169B1 (ko) * 2013-06-20 2018-06-15 현대건설기계 주식회사 굴삭기의 전자유압 밸브 시스템
EP2944828B1 (fr) * 2013-08-19 2018-02-21 Jiangsu Hengli Hydraulic Co., Ltd. Clapet principal de commande hydraulique à recyclage d'énergie
KR101998302B1 (ko) * 2014-12-08 2019-10-02 현대건설기계 주식회사 건설기계의 암 유압 제어장치
DE102015209325A1 (de) * 2015-05-21 2017-01-26 Robert Bosch Gmbh Hydraulische Anordnung zur Regeneration von Druckmittel eines hydraulischen Verbrauchers
DE102016223099A1 (de) * 2016-11-23 2018-05-24 Robert Bosch Gmbh Elektrohydraulische Anordnung und Hydraulische Achse
CN110374949B (zh) * 2018-04-13 2020-12-04 丹佛斯动力系统（浙江）有限公司 阀和具有该阀的液压系统

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JP3549126B2 (ja) 1994-08-05 2004-08-04 株式会社小松製作所 方向制御弁
KR100208732B1 (ko) 1996-05-21 1999-07-15 토니헬샴 가변 재생기능이 구비된 중장비용 콘트롤밸브
JPH11230375A (ja) * 1998-02-18 1999-08-27 Hitachi Constr Mach Co Ltd 再生回路を有する方向制御弁
JP3544173B2 (ja) * 2000-08-17 2004-07-21 株式会社カワサキプレシジョンマシナリ 油圧シリンダの再生切換弁
JP2006002918A (ja) * 2004-06-21 2006-01-05 Hitachi Constr Mach Co Ltd 再生機能付き弁装置

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KR20080104122A (ko) 2008-12-01
EP1984629A1 (fr) 2008-10-29
JP2009526177A (ja) 2009-07-16
DE102006006228A1 (de) 2007-08-16
JP4824777B2 (ja) 2011-11-30
KR101011944B1 (ko) 2011-01-31
WO2007090522A1 (fr) 2007-08-16

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