EP1984629A1 - 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

Info

Publication number
EP1984629A1
EP1984629A1 EP07711381A EP07711381A EP1984629A1 EP 1984629 A1 EP1984629 A1 EP 1984629A1 EP 07711381 A EP07711381 A EP 07711381A EP 07711381 A EP07711381 A EP 07711381A EP 1984629 A1 EP1984629 A1 EP 1984629A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
chamber
hydraulic control
arrangement according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07711381A
Other languages
German (de)
English (en)
Other versions
EP1984629B1 (fr
Inventor
Thomas Weickert
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1984629A1 publication Critical patent/EP1984629A1/fr
Application granted granted Critical
Publication of EP1984629B1 publication Critical patent/EP1984629B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—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 actuating a hydraulic cylinder is known, for example, from Komatsu's "Structure and Function CLSS, Arm Regeneration Circuit.”
  • This conventional control arrangement has a directional control valve whose valve spool controls the pressure medium connection between a pressure medium source, a tank and two pressure chambers the lowering of the hydraulic cylinder is adjustable and a lowering brake valve arranged axially parallel to the directional valve in the control arrangement for the flow control of the pressure medium volume flow with pulling load whose control piston is acted upon by the force of a spring in the closing direction and the pressure in the expanding pressure chamber in the opening direction.
  • the US 5,832,808 Bl 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.
  • 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 valve whose 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 lowering brake valve for sequencing the pressure medium flow of a decreasing pressure chamber, the control piston is acted upon in the closing direction by the force of a spring and in the opening direction of the pressure in the expanding pressure chamber, wherein for regeneration pressure medium from the running pressure medium flow upstream of the lowering brake valve via a in the direction of the 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.
  • the check valve is integrated in the valve slide, wherein the pressure acting in the opening direction on the lowering brake valve pressure is reported through the check valve.
  • control piston of the lowering brake valve is arranged coaxially to the check valve in a common receiving bore of the valve spool.
  • 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 Schlie ⁇ redesign is executed 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 frontally supported on 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 clearance, so that pressure 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 space 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 spool to the tank, which is closed in further working positions of the valve spool by a wall of the valve bore, so that the logic valve is locked in its closed position.
  • Figure 1 is a circuit diagram of a hydraulic control arrangement according to the invention
  • Figure 2 is a sectional view of a first concrete embodiment of the control arrangement of Figure 1;
  • Figure 3 is a sectional view of the shifted to the right valve spool of Figure 2;
  • Figure 4 is an enlarged view of the directional control valve in the region of the check valve and lowering brake valve of Figure 3;
  • Figure 5 is a sectional view of the left shifted valve spool of Figure 2;
  • FIG. 6 shows a longitudinal section through an inventive directional control valve according to an embodiment for leakage-free support of the hydraulic cylinder
  • Figure 7 is an enlarged view of the shifted to the right valve spool in the region of the logic valve.
  • Figure 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.
  • the pressure medium supply of the hydraulic cylinder 2 via 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 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 Pressure in the cylinder chamber 8 of the hydraulic cylinder 2 or more precisely is acted upon by the pressure in the flow line 7.
  • pressure medium For regeneration pressure medium from the running out of the annulus 12 pressure medium flow upstream of the lowering brake valve 20 via a arranged in a regeneration line 30 and in the direction of increasing cylinder chamber 8 opening check valve 28 is branched off and summable to the pressure medium volume flow in the inlet of the cylinder chamber 8.
  • FIG. 2 shows a first concrete exemplary embodiment of the control arrangement 1 according to the invention from FIG. 1.
  • This has a directional control valve 34, with a valve bore 36 introduced into a valve housing 35 in which a valve slide 38 is guided in an axially displaceable manner.
  • the directional control 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 Weghoffm 44, a Vorlaufhoffm 46, a downstream of a schematically indicated pressure compensator 48 arranged pressure compensator chamber 50, a compensation chamber 52, a pressure upstream of the scale 48 arranged connecting space 54, a Zulaufhoffm 56, an upstream of the pressure compensator 48 arranged further pressure compensator space 58, arastlaufhoffm 60 and a further furnishhoffm 62 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 discharge 56 are connected to a pressure connection P.
  • the supply 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 remindlaufhoffm 60 is connected to a working port B, via which the annular space 12 of the hydraulic cylinder 2 according to Figure 1 can be supplied with pressure medium.
  • the two pressure compensator chambers 50, 58 are connected to the pressure compensator outlet P "via a curved passage 84, so that the same pressure is applied in the spaces 50, 58.
  • the connecting space 54 communicates with a pressure compensator input P '.
  • a feed control groove 86, two horrinnuten 88, 90 and a wastewater spraynut 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 remindlaufhoffm 60 and the pressure compensator space 58 is opened or closed.
  • Vorlaufberichtnut 86 two control edges 106, 108 are formed.
  • the connection between the Vorlaufhoffm 46 and the pressure compensator chamber 50 is opened or closed, while on the control edge 106, the connection between the Vorlaufhoffm 46 and the drain chamber 44 up or is controlled.
  • the control edges 106, 108 are each designed with fine control notches 110.
  • 114 are formed with Feinberichtkerben 116, 118 which form the metering orifice 10 of Figure 1 in cooperation with the annular web 74, on the case of an axial displacement of the valve spool 38 from the illustrated basic position to the left and right a connection from Zulaufhoffm 56 to the connection space 54 and thus to the schematically indicated pressure compensator 48 is opened.
  • the metering orifice 10 is controlled, so that the connection between the inlet chamber 56 and the connecting space 54 is shut off.
  • 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 toward the increasing cylinder chamber 8 opening check valve 28 in the regeneration line 30 (see Figure 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 coaxial with the check valve 28 in a common, formed as a stepped blind hole 120 extending axially receiving bore 122 of the valve slide 38 which in an end face 124 (right in Figure 3) of the valve spool 38th empties.
  • 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 valve seat 128 limited end face 132 and a spring chamber 134 limiting 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 annular shoulder 146 arranged beyond the valve seat 128 and acts in the opening direction.
  • the annular shoulder 146 is via radial bores 148 and throttling notches 150 which open out into the adjustable throttle 32 (see FIG. 1) 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 remindlaufhoffm 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 on which a first end section 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 Figure 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.
  • FIG. 5 which shows the valve slide 38, which is displaced to the left, from FIG. 2, the connection from the inlet chamber 56 via the metering orifice 10 to the connecting chamber 54 is also controlled in these working positions, 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 Figure 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 Figure 1) is relieved.
  • the hydraulic cylinder 2 retracts.
  • the function of the control arrangement 1 according to the first exemplary embodiment is explained below with reference to FIGS. 2 to 5.
  • the pressure medium can enter the pressure compensator chambers 50, 58 from the pressure port P via the inlet chamber 56 and the controlled metering orifice 10 into the connecting space 54 and via the pressure compensator 48 and the arc channel 84.
  • the valve spool 38 and the annular collar 96 is shifted to the right, so that the connection from the pressure compensator chamber 50 is opened to the flow chamber 46 via the flow control groove 86 - the pressure medium flows through the flow chamber 46 and the working port A to the cylinder chamber 8 of the hydraulic cylinder 2 ( see FIG. 1).
  • the hydraulic cylinder 2 extends.
  • the valve slide 38 For retracting the hydraulic cylinder 2, the valve slide 38 is moved from the basic position shown in Figure 2 to the left, in its working positions shown in Figure 5. In these working positions, 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 remindlauf devisnut 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.
  • 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 Figures 2 to 5, ie also in this variant, a check valve 28 and a lowering brake valve 20 ⁇ 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 Axialbohrung- 200, on the shown in the left shifted working position of the valve spool 38, the pressure fluid from the annular space 12 via the return line 14, the remindlaufhoffm 60, the transverse bores 142 and the open via the annular shoulder 146 check valve 28 via a logic valve 202 the lead clearance 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 as well as via radial bores 224 relieved to the discharge chamber 62, so that the logic valve 202 via the annular surface 218 and the end face 213 acted upon pressures in Vorlaufhoffm 46 and in the axial bore 200 against the force of spring 206 can be brought into its open position.
  • FIG. 7 which shows an enlarged view of the valve slide 38 shifted to the right in the region 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 slide 38.
  • the logic valve 202 is blocked and can not be controlled by the pressure medium volume flow passing through the radial shoulder 218 from the working port A via the flow control groove 86 to the tank 16 (see FIG. 1).
  • the preliminary 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)

Abstract

L'invention concerne un système de commande hydraulique qui commande un consommateur, en particulier un vérin hydraulique, et qui présente une soupape (34) dont le coulisseau (38) de soupape peut être déplacé entre une source de fluide sous pression, un réservoir et deux chambres sous pression du consommateur pour commander la liaison au fluide sous pression, et une soupape (20) de freinage d'abaissement qui commande l'évolution du débit volumique de fluide sous pression qui provient d'une chambre sous pression qui se rétrécit et dont le piston pilote (22) est sollicité dans la direction de fermeture par la force d'un ressort (24) et dans la direction d'ouverture par la pression qui règne dans la chambre sous pression qui s'agrandit. Pour la régénération, le fluide sous pression qui provient de l'écoulement volumique de fluide sous pression peut être dérivé en amont de la soupape de freinage d'abaissement dans un conduit de régénération par un clapet anti-retour (28) qui s'ouvre en direction de la chambre sous pression qui s'agrandit et peut être ajouté au débit volumique de fluide sous pression dans l'amenée. Selon l'invention, le clapet anti-retour est intégré dans le coulisseau de soupape et la pression qui agit sur la soupape de freinage d'abaissement dans la direction d'ouverture est transmise par l'intermédiaire du clapet anti-retour.
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

Publications (2)

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

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Application Number Title Priority Date Filing Date
EP07711381A Active EP1984629B1 (fr) 2006-02-09 2007-01-25 Systeme de commande hydraulique a regeneration et soupape de frein d'abaissement

Country Status (5)

Country Link
EP (1) EP1984629B1 (fr)
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
WO2015024152A1 (fr) * 2013-08-19 2015-02-26 江苏恒立液压有限公司 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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See references of WO2007090522A1 *

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JP2009526177A (ja) 2009-07-16
JP4824777B2 (ja) 2011-11-30
WO2007090522A1 (fr) 2007-08-16
DE102006006228A1 (de) 2007-08-16
KR20080104122A (ko) 2008-12-01
EP1984629B1 (fr) 2013-03-13
KR101011944B1 (ko) 2011-01-31

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