EP1245834A1 - Dispositif de commande hydraulique avec priorité - Google Patents

Dispositif de commande hydraulique avec priorité Download PDF

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Publication number
EP1245834A1
EP1245834A1 EP02005603A EP02005603A EP1245834A1 EP 1245834 A1 EP1245834 A1 EP 1245834A1 EP 02005603 A EP02005603 A EP 02005603A EP 02005603 A EP02005603 A EP 02005603A EP 1245834 A1 EP1245834 A1 EP 1245834A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure medium
hydraulic control
working group
medium source
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
EP02005603A
Other languages
German (de)
English (en)
Other versions
EP1245834B1 (fr
Inventor
Gottfried Olbrich
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 EP1245834A1 publication Critical patent/EP1245834A1/fr
Application granted granted Critical
Publication of EP1245834B1 publication Critical patent/EP1245834B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B13/022—Flow-dividers; Priority 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
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • 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
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a hydraulic control device according to the closer in the preamble of claim 1 defined type.
  • a hydraulic control device is known from DE 36 29 471 A1 with a first working group made up of load pressure sensors Directional control valves and a second control circuit with neutral circulation known in which the division of the currents from one Pump to both working groups of one as a pressure compensator working throttle valve is controlled.
  • the throttle valve lies in a connection between a pump connection or a pressure medium source to a continuation connection, to the successive the second working group or the secondary working group connected.
  • the flow resistance in the neutral position of the two working groups or Control circuits keep the throttle valve open.
  • a priority provided working group, called primary working group, which with load-sensing directional valves in one design for one closed circuit is formed, can be with the subordinate working group or secondary working group combine that energy losses are low are kept and versatile adjustments are possible.
  • the throttle valve is in a connection plate of the primary working group housed, the connection plate one has inlet connection connected to the pressure medium source, of which an inlet channel bypassing the actual one Throttle valve to an opening in a flange surface the connection plate leads.
  • the throttle valve or its Pressure compensator valve is provided with two control edges and is designed as a 3/3-way valve.
  • connection between the pressure medium source and the secondary working group a facility for Regulation of a quantity of pressure medium supplied to the secondary working group has the advantage that when the connection is open between the pressure medium source and the secondary working group a current regulation for the continuation or a regulated quantity of pressure medium supplied to the secondary working group is adjustable or limited.
  • the facility for regulating those fed to the secondary working group Pressure medium amount on an orifice, over which the regulated pressure medium flow supplied to the secondary working group is set and limited. This ensures that the pressure medium amount from a certain preset Value is limited or cut off and the Supply of an impermissibly large pressure medium flow to the Secondary working group is avoided.
  • the embodiment of the invention without expensive constructive measures in already developed systems Can find application.
  • FIG. 1 shows one hydraulic control device 1 with two from a pressure medium source 2, which is designed as a constant pump, workable groups 3, 4, being a primary working group 3 directly connected to the pressure medium source 2 is and a secondary working group 4 or a supply of Pressure medium to the secondary working group 4 via a 3/3-way valve trained throttle valve 5 is controlled.
  • a pressure medium source 2 which is designed as a constant pump
  • workable groups 3, 4 being a primary working group 3 directly connected to the pressure medium source 2 is and a secondary working group 4 or a supply of Pressure medium to the secondary working group 4 via a 3/3-way valve trained throttle valve 5 is controlled.
  • the secondary working group 4 exhibits a neutral circulation in a so-called "open center” Execution in such a way that in a certain Switch position of a directional valve 6 to the secondary working group 4 pressure medium flow supplied via a relay 7 via a return line 8 to a pressure medium container or tank 9 is supplied.
  • the throttle valve 5 is in a directional valve block 10 of the Primary working group 3 arranged and via a pump feed line 11 and a line 12 branching therefrom with the Pressure medium source 2 connected.
  • FIG. 2 shows part of a constructive design of the directional valve block 10 of the primary working group 3 in shown a longitudinal section, wherein the throttle valve 5th with a pressure compensator valve 13 and a first pressure chamber 14 and a second pressure chamber 15 is executed.
  • the first Pressure chamber 14 and the second pressure chamber 15 are from the directional valve block 10 or the connecting plate of the primary working group 3 and the ends of the pressure compensator slide, the two pressure chambers 14, 15 each having a first Control line 16 and a second control line 17 for adjustment a pressure drop on the pressure compensator slide 13 are connected.
  • the first control line 16 branches from the pump feed line 11, with which the pump inlet pressure in the first pressure chamber 14 is present.
  • the second control line 17 branches from one Pressure tap line 18 and is with a throttle 19th Mistake.
  • the throttle 19 is for setting a pressure gradient between the pressure tap line 18 and the second Pressure chamber 15 is provided. This is to ensure that in the case of an undesirably high pressure at which one between the second pressure chamber 15 and another Return line 21 arranged pressure relief valve 20 opens, a pressure medium flow or a quantity of pressure medium only to a limited extent into the further return line 21 flows.
  • the arrangement of the throttle 19 in the second control line 17 dynamic stabilization of the pressure compensator slide 13, which in particular at Pressure fluctuations damping the response of the Pressure compensator slide 13 causes.
  • the damping arises a, since the pressure medium volume of the second pressure chamber 15, one acting on the pressure compensator slide 13
  • Return spring 22 receives, by throttling the throttle 19 replace only at a limited speed can.
  • a shuttle valve 23 is provided evaluates an incoming pressure signal and the highest forwards the applied pressure signal to the second pressure chamber 15.
  • each a pressure signal of the pressure tap line 18 and an additional control line 24 a, which with a further shuttle valve 25 of the primary working group 3 communicates. That means that Shuttle valve 23 reacts to an incoming pressure signal and the larger pressure signal via a so-called center tap to the pressure compensator slide designed as a control element 13 or in the second spring-loaded pressure chamber 15 leads.
  • a prioritization of the pressure medium supply between the Primary working group 3 and the secondary working group 4 will controlled by the throttle valve 5 operating as a pressure compensator, being in a connection between the pressure medium source 2 and the secondary working group 4 a device 26 for Regulating the amount of pressure medium supplied to the secondary working group 4 is switched.
  • the device 26 is with a Orifice plate and two control edges 27, 31 formed, the orifice plate having a first control edge 27 of the pressure compensator slide 13, via which the connection between the pressure medium source 2 and the secondary working group 4 is lockable.
  • the control orifice plate is a combination from the first control edge 27, an annular groove 28 with a corresponding paragraph 29 on the pressure compensator slide 13 and a variable axial positioning of the Pressure compensator slide 13 in the directional valve block 10.
  • the pressure compensator slide 13 has a second control edge 31 for controlling a pressure medium flow from the Pressure medium source 2 in the further return line 21.
  • the first control edge 27 and the second control edge 31 are in the axial direction of the pressure compensator slide 13 this provided that with an axial adjustment of the Pressure compensator slide 13 due to an applied to it Pressure drop first the connection between the pressure medium source 2 and the secondary working group 4 and one increasing adjustment of the slide valve 13 also the connection between the pressure medium source 2 and the another return line 21 is opened.
  • the regulation of the pressure medium flow from the pressure medium source 2 to the secondary working group 4 takes place from a Interplay between the position of the pressure compensator slide 13 and a very specific, defined pressure drop, that on the orifice plate and the annular groove 28 and so corresponding paragraph 29 of the pressure compensator slide 13 takes place.
  • This pressure drop acts as a differential pressure on the two end faces of the slide valve 13 and leads to the fact that in the case of a too large pressure medium flow the pressure drop increases. This, in turn, results different pressures on the two faces of the Pressure compensator slide 13, and the pressure compensator slide 13 is moved against the return spring 22.
  • This direction of movement of the pressure compensator slide 13 leads to the fact that the pressure medium volume flow in the direction of the orifice flows, is reduced because the second control edge 31 Connection between the pressure medium source 2 and the other Return line 21 releases.
  • the amount of pressure medium, which from the pressure medium source 2 to the secondary working group 4 is led through the Control edges 27, 31 or by adjusting the width of the gap between the control edges 27, 31 and thus corresponding housing edges controlled.
  • the regulation of the pressure medium flow from the pressure medium source 2 to the secondary working group takes place via the orifice plate, i.e. about the mobility or axial positioning of the Pressure compensator valve 13, the first control edge 27, the downstream annular groove 28 and its shoulder 29.
  • the geometric configuration of the device 26 or its The measuring orifice can be used depending on the current Use case arbitrarily, the amount of Limitation of the pressure medium flow depending on of the throttle parameter of the orifice plate is determined.
  • the size of the Paragraph 29 or its diameter the throttle parameter the orifice is determined.
  • the hydraulic control device behaves 1 as with a load-sensing parallel connection. Is the pressure in primary working group 3 compared to the pressure in the secondary working group 4 the higher Load pressure in the hydraulic control device 1, so the directional control valve 32A, 32B or 32C primarily with pressure medium supplied, the downstream secondary working group 4th only applied with a residual pressure medium flow becomes.
  • the pressure in the primary working group 3 is the lower Load pressure, the forwarding 7 becomes a regulated maximum Pressure medium volume flow supplied.
  • the pressure compensator slide 13 wherein the pressure relief valve 20 responds and creates a pressure drop, so that the pressure compensator slide 13 is displaced in such a way that the connection between the pressure medium source 2 and the Tank 9 is opened and forwarding a prohibited large pressure medium flow is avoided.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP20020005603 2001-03-29 2002-03-12 Dispositif de commande hydraulique avec priorité Expired - Lifetime EP1245834B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10115650 2001-03-29
DE2001115650 DE10115650A1 (de) 2001-03-29 2001-03-29 Hydraulische Steuereinrichtung

Publications (2)

Publication Number Publication Date
EP1245834A1 true EP1245834A1 (fr) 2002-10-02
EP1245834B1 EP1245834B1 (fr) 2005-09-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020005603 Expired - Lifetime EP1245834B1 (fr) 2001-03-29 2002-03-12 Dispositif de commande hydraulique avec priorité

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EP (1) EP1245834B1 (fr)
DE (2) DE10115650A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046561A1 (fr) 2002-11-15 2004-06-03 Studio Tecnico 6 M S.R.L. Circuit dynamique de fluide pour l'alimentation en utilisation primaire et auxiliaire selon des priorites predefinies
WO2006037318A1 (fr) * 2004-10-06 2006-04-13 Bosch Rexroth Ag Systeme de commande hydraulique
WO2007096030A1 (fr) * 2006-02-23 2007-08-30 Robert Bosch Gmbh Dispositif de commande hydraulique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020210441A1 (de) 2020-08-17 2022-02-17 Hawe Hydraulik Se Proportional-Schieberventil mit einem Druckbegrenzungsventil, Druckbegrenzungsventil und Hydrauliksystem

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629471A1 (de) * 1986-08-29 1988-03-03 Bosch Gmbh Robert Hydraulische steuereinrichtung
US5398594A (en) * 1992-11-10 1995-03-21 Hydraulik-Ring Antriebs- Und Steuerungstechnik Gmbh Volume flow control for hydraulic systems of vehicles, especially for steering devices of motor vehicles

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3629471A1 (de) * 1986-08-29 1988-03-03 Bosch Gmbh Robert Hydraulische steuereinrichtung
US5398594A (en) * 1992-11-10 1995-03-21 Hydraulik-Ring Antriebs- Und Steuerungstechnik Gmbh Volume flow control for hydraulic systems of vehicles, especially for steering devices of motor vehicles

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046561A1 (fr) 2002-11-15 2004-06-03 Studio Tecnico 6 M S.R.L. Circuit dynamique de fluide pour l'alimentation en utilisation primaire et auxiliaire selon des priorites predefinies
US7204186B2 (en) 2002-11-15 2007-04-17 Studio Tecnico 6 M S.R.L. Fluid circuit for feeding primary and auxiliary users with preset priorities
WO2006037318A1 (fr) * 2004-10-06 2006-04-13 Bosch Rexroth Ag Systeme de commande hydraulique
US7870728B2 (en) 2004-10-06 2011-01-18 Bosch Rexroth, AG Hydraulic control arrangement
WO2007096030A1 (fr) * 2006-02-23 2007-08-30 Robert Bosch Gmbh Dispositif de commande hydraulique
US8286544B2 (en) 2006-02-23 2012-10-16 Robert Bosch Gmbh Hydraulic control system

Also Published As

Publication number Publication date
EP1245834B1 (fr) 2005-09-14
DE10115650A1 (de) 2002-10-02
DE50204217D1 (de) 2005-10-20

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