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WO2005110834A1 - Direction assistee hydraulique - Google Patents

Direction assistee hydraulique Download PDF

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Publication number
WO2005110834A1
WO2005110834A1 PCT/EP2005/051539 EP2005051539W WO2005110834A1 WO 2005110834 A1 WO2005110834 A1 WO 2005110834A1 EP 2005051539 W EP2005051539 W EP 2005051539W WO 2005110834 A1 WO2005110834 A1 WO 2005110834A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure medium
power steering
hydraulic power
steering
delivery device
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.)
Ceased
Application number
PCT/EP2005/051539
Other languages
German (de)
English (en)
Inventor
Wilfried Leutner
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 Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of WO2005110834A1 publication Critical patent/WO2005110834A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/08—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by type of steering valve used
    • B62D5/083—Rotary valves
    • B62D5/0835—Rotary valves characterised by means for actively influencing the deflection angle of the valve, e.g. depending on driving parameters

Definitions

  • the invention relates to a hydraulic power steering system for a vehicle according to the preamble of claim 1.
  • Hydraulic power steering systems are known in particular in motor vehicles, in which, in addition to a steering movement supported by a steering actuator as a function of a setpoint input on a steering handle, an auxiliary steering movement generated by a servo device is additionally superimposed. In this way, the steering movement of steered wheels of the vehicle can be varied depending on the speed.
  • DE 20304336 U1 describes a hydraulic power steering system for a vehicle with a first pressure medium delivery device, which is connected as a control hydraulic pump to a steering handle, and with a second pressure medium delivery device, which is designed as a modulator pump.
  • the pressure medium flow rate of the modulator pump is added to the pressure medium flow rate of the control hydraulic pump via a complex circuit of valves, check valves and a pressure accumulator and fed to a steering actuator.
  • four operating modes of the hydraulic power steering can be basically represent the operation of the power steering according to the vehicle speed and vehicle yaw rate.
  • US 5845736 describes a hydraulic power steering system in the manner of a “steer-by-wire” steering system for a vehicle.
  • a steer-by-wire steering system is proposed whose hydraulic servo valve is designed as a rotary slide valve, two control elements of the rotary slide valve according to a setpoint input on a steering handle by an electric servo motor, and a pressure medium flow is measured by a hydraulic steering actuator
  • the hydraulic actuating cylinder or steering torque servomotor is acted upon by the delivery pressure of an additional hydraulic pump via directional control valves.
  • the known hydraulic power steering systems are complex, since the pressure medium delivery flow of their additional, second pressure medium delivery devices is regulated via valves and pressure sensors.
  • the invention has for its object to provide a hydraulic power steering, the second pressure medium flow is inexpensive and easy to represent.
  • the pressure medium pressure of the second pressure medium delivery device is controlled directly by the speed or the torque of the electric servomotor and without using a hydraulic control path, by supplying an electrically or electronically directly controlled current signal or voltage signal, which can be field-oriented, to the electric servomotor is and the pressure medium flow is supplied to the steering torque servomotor arranged in the steering or rotary slide valve.
  • the second pressure medium delivery device which is provided with a pressure medium delivery flow for influencing or overriding the steering activity of the driver, is designed as a master cylinder, preferably as a double-acting master cylinder.
  • a piston in the hydraulic master cylinder displaces on both sides in working spaces of the master cylinder depending on its direction of displacement. located pressure medium.
  • the piston is preferably directly penetrated by a spindle, which forms an output member of the electric servomotor, and axially displaced in the longitudinal direction when the spindle rotates. In this way, the speed and the torque of the electric servomotor directly influence the pressure medium pressure of the second pressure medium delivery device formed in this way.
  • the thread of the spindle forms a non-self-locking motion screw with the piston of the master cylinder.
  • Devices are provided by means of which the second pressure medium delivery device can be synchronized with the steering actuator for compensation purposes.
  • the pressure in the steering actuator and the Displacement of the steering actuator corresponds to the ratio of the end faces of the piston in the master cylinder and the end faces of a piston in the steering torque actuator. Due to the spindle, which sealingly projects through the piston in the master cylinder, the torque of the electric servomotor is proportional to the pressure generated in the master cylinder. The current consumption of the electric servomotor is therefore proportional to the pressure in the steering torque servomotor.
  • the master cylinder it can be expedient to provide a pressure medium pump which delivers on both sides in the second pressure medium delivery device and is driven by the electric servomotor.
  • the speed and the torque of the electric servomotor which is preferably connected directly to the pressure medium pump, determines the control of the steering actuator.
  • the pressure medium pump it can be expedient to form the pressure medium pump as a pressure medium pump that delivers on one side and to determine the direction of delivery in working spaces of the steering torque servomotor by a directional control valve.
  • the torque of the electric servomotor of the second pressure medium delivery device is proportional to the pressure medium pressure in the steering torque servomotor of the steering valve.
  • the system pressure in the hydraulic circuit on the second pressure medium delivery device can be determined indirectly by the electrical current consumption of the electric servomotor, since the pressure in the hydraulic circuit in question is proportional to the current of the electric servomotor.
  • the hydraulic power steering system according to the invention is suitable for controlling the second pressure medium delivery device as a function of the vehicle and travel parameters, and thus the pressure applied to the steering actuator and in the working spaces of a hydraulic actuator of the steering actuator.
  • the hydraulic power steering can be designed both as an auxiliary power steering and as an external power steering in the manner of a steer-by-wire steering.
  • Fig. 3 shows an equivalent circuit diagram of a second pressure medium delivery device of a hydraulic power steering.
  • FIG. 1 shows a schematic longitudinal section through essential components of a hydraulic power steering system 1, which is designed as an auxiliary power steering system for a motor vehicle.
  • a rotary slide valve 22 is arranged coaxially in a rotary slide valve bushing 21.
  • the steering valve 17 has a pressure connection 23 which is acted upon by a first pressure medium delivery device 2 with pressure medium from a container 24.
  • the steering valve 17 has a low-pressure connection 25, which is also fluidly connected to the container 24.
  • two pressure medium lines 26, 27 are arranged diametrically to the low pressure connection 25 and pressure connection 23, each of which is fluidly connected to a working space 14, 14 'of a hydraulic steering actuator 3.
  • the working spaces 14, 14 ' are arranged on both sides of a piston of the hydraulic steering actuator 3 designed as a servo cylinder.
  • the steering valve 17 has an open center, with all of the pressure medium line connections mentioned on the steering valve 17 communicating with one another when the rotary slide bushing 21 and the rotary slide valve 22 assume a central position relative to one another.
  • the rotary slide valve 22 is connected to the rotary slide valve bushing 21 by a torsion bar 28 running axially through these components of the steering valve 17 and can be rotated to a limited extent with respect to one another.
  • a steering handle 4 is rotatably connected to the rotary valve 22, whereby the Rotary slide valve 22 3, the torsion bar 28 and subsequently also the rotary slide valve bushing 21 can be rotated in the housing 20.
  • the hydraulic power steering system 1 is designed as an external power steering system, the rotary valve 22 is rotated via an electric motor or a hydraulic servomotor and rotated relative to the rotary valve bushing 21.
  • the pressure medium delivery flow of the first pressure medium delivery device 2 is directed differentially by the steering valve 17 into one or the other pressure medium line 26, 27 and thereby one Generating force directed in one direction or the other in the working spaces 14, 14 'of the steering actuator 3, which, in addition to the positioning force on the rack, contributes to the steering angle adjustment of the steered wheels.
  • a second pressure medium delivery device 5 which is driven by an electric servomotor 6, is provided.
  • the pressure medium delivery flow of the second pressure medium delivery device 5 is indirectly superimposed on the pressure medium delivery flow of the first pressure medium delivery device 2 by feeding it to a steering torque servomotor 16 in the steering valve 17.
  • a direct drive of a master cylinder 7 by the electric servomotor 6 is provided in the exemplary embodiment in FIG. 1, so that it depends on the direction of rotation and the number of revolutions of a rotor 30 of the electric servomotor 6 drives a piston 9 with a spindle 8 connected in a rotationally fixed manner to the rotor 30.
  • the rotor 30 and a stator 31 of the electric servomotor 6 are in the exemplary embodiment in FIG. 1 arranged coaxially to the longitudinal axis 32 of the master cylinder 7.
  • Another arrangement can also be provided, for example with a gear arranged between the spindle 8 and the electric servomotor 6.
  • the spindle 8 has a non-self-locking thread 10, so that the master cylinder 7 and the electric servomotor 6 remain controllable by the steering torque servomotor 16 and can also be synchronized with the steering valve 17 and the steering actuator 3.
  • a directional control valve 33 is able to fluidly separate the master cylinder 7 and the second pressure medium flow from the other components of the hydraulic power steering 1. In the position of the directional control valve 33 as in FIG.
  • the pressure in the working spaces 15, 15 'of the steering torque servomotor 16 corresponds to the ratio of the areas between the pistons 9 and 34 of the master cylinder 7 and the steering torque servomotor 16.
  • the torque of the electric servomotor 6 is proportional to the pressure in the working spaces 14, 14 'of the master cylinder 7. If one or the other working space 15, 15' of the hydraulic steering torque servomotor 16 in the steering valve 17 is pressurized - depending on the direction and length of the displacement path of the piston 9 in the master cylinder 7 - a more or less large pressure difference is set at the connections of the pressure medium lines 26, 27 of the steering actuator 3 to the steering valve 17 and the steering actuator 3 carries out an actuating stroke independently of the setpoint input on the steering handle 4. This can be done by an actuating signal from a control and / or regulating device of the hydraulic power steering 1, which causes a change in the power supplied, for example by changing the current or the voltage or the frequency of the current, in a field-oriented manner.
  • FIG. 2 shows a further exemplary embodiment of a hydraulic power steering system 1, with the difference from the power steering system in FIG. 1 that the second pressure medium delivery device 5 is formed by a pressure medium pump 11 which delivers on both sides and whose pressure and delivery direction are directly proportional to the speed and the direction of rotation of the electric servomotor 6 driving them.
  • the same reference numerals as in FIG. 1 apply to the same components.
  • FIG. 3 shows an exemplary embodiment of a second pressure medium delivery device 5 which has a pressure medium pump 12 which delivers on one side and is driven by the electric servomotor 6.
  • the pressure medium flow of the pressure medium pump 12 is from a 3/2-way valve 13 that the control and / or control device of the vehicle is controlled, optionally metered to the working spaces 15, 15 'of the steering torque servomotor 16.
  • the displacement spaces of the respective second pressure medium delivery device 5 are fluidly connected to a pressure medium container 19 via orifices 18, 18 ', whereby an open pressure medium circuit is formed which enables gas inclusions in the pressure medium to be removed.
  • the pressure of the pressure medium of the second pressure medium delivery device 5 can be determined indirectly by the current consumption of the electric servomotor 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Power Steering Mechanism (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)

Abstract

L'invention concerne une direction assistée hydraulique (1) destinée à un véhicule et comprenant un premier dispositif d'alimentation en agent de pression (2) permettant de délivrer une pression de l'agent de pression à un actionneur de direction (3) soumis à une valeur théorique d'entrée au niveau d'une manette de direction (4), et un deuxième dispositif d'alimentation d'agent de pression (5) entraîné par un servomoteur électrique (6) et dont le débit d'agent de pression représente une deuxième valeur théorique d'entrée qui peut l'emporter sur la valeur théorique d'entrée au niveau de la manette de direction (4). L'invention vise à créer une direction assistée hydraulique dont le débit d'agent de pression peut être représenté de manière simple et économique. A cet effet, la pression de l'agent de pression du deuxième dispositif d'alimentation d'agent de pression (5) est commandée directement par la vitesse ou le couple du servomoteur électrique (6).
PCT/EP2005/051539 2004-05-03 2005-04-07 Direction assistee hydraulique Ceased WO2005110834A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200410021629 DE102004021629A1 (de) 2004-05-03 2004-05-03 Hydraulische Servolenkung
DE102004021629.0 2004-05-03

Publications (1)

Publication Number Publication Date
WO2005110834A1 true WO2005110834A1 (fr) 2005-11-24

Family

ID=34965768

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/051539 Ceased WO2005110834A1 (fr) 2004-05-03 2005-04-07 Direction assistee hydraulique

Country Status (2)

Country Link
DE (1) DE102004021629A1 (fr)
WO (1) WO2005110834A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1625992A3 (fr) * 2004-08-11 2007-08-08 ZF-Lenksysteme GmbH Direction assistée hydraulique et son procédé d'opération
WO2009037169A1 (fr) * 2007-09-18 2009-03-26 Zf Friedrichshafen Ag Dispositif de réglage électrohydraulique
DE102014206934B4 (de) 2014-04-10 2022-05-12 Zf Friedrichshafen Ag Stellmotor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006034143A1 (de) * 2006-07-24 2008-01-31 Trw Automotive Gmbh Drehmomentsensor sowie Lenksystem für ein Kraftfahrzeug

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168949A (en) * 1990-04-19 1992-12-08 Jidosha Kiki Co., Ltd. Steering force control system for power steering
EP0580997A1 (fr) * 1992-07-31 1994-02-02 Man Nutzfahrzeuge Ag Direction assistée pour véhicule à moteur
US5517899A (en) * 1993-09-08 1996-05-21 Mercedes-Benz Ag Hydraulic servosystem with externally controllable setting assembly
DE20304336U1 (de) * 2003-03-18 2003-07-31 TRW Fahrwerksysteme GmbH & Co KG, 40547 Düsseldorf Servolenksystem
DE202004013834U1 (de) * 2004-02-17 2005-02-03 Trw Automotive Gmbh Servolenkventil für eine Fahrzeug-Servolenkung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4435148A1 (de) * 1994-07-19 1996-01-25 Bosch Gmbh Robert Hydraulischer Stellantrieb für die Achselenkung eines Kraftfahrzeuges
DE19541749C1 (de) * 1995-11-09 1997-05-22 Daimler Benz Ag Servolenkung für Kraftfahrzeuge
DE19820381B4 (de) * 1998-05-07 2007-01-25 Trw Fahrwerksysteme Gmbh & Co Kg Verfahren zur Beeinflussung der Ventilkennlinie
US6298941B1 (en) * 1999-01-29 2001-10-09 Dana Corp Electro-hydraulic power steering system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5168949A (en) * 1990-04-19 1992-12-08 Jidosha Kiki Co., Ltd. Steering force control system for power steering
EP0580997A1 (fr) * 1992-07-31 1994-02-02 Man Nutzfahrzeuge Ag Direction assistée pour véhicule à moteur
US5517899A (en) * 1993-09-08 1996-05-21 Mercedes-Benz Ag Hydraulic servosystem with externally controllable setting assembly
DE20304336U1 (de) * 2003-03-18 2003-07-31 TRW Fahrwerksysteme GmbH & Co KG, 40547 Düsseldorf Servolenksystem
DE202004013834U1 (de) * 2004-02-17 2005-02-03 Trw Automotive Gmbh Servolenkventil für eine Fahrzeug-Servolenkung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1625992A3 (fr) * 2004-08-11 2007-08-08 ZF-Lenksysteme GmbH Direction assistée hydraulique et son procédé d'opération
WO2009037169A1 (fr) * 2007-09-18 2009-03-26 Zf Friedrichshafen Ag Dispositif de réglage électrohydraulique
DE102014206934B4 (de) 2014-04-10 2022-05-12 Zf Friedrichshafen Ag Stellmotor

Also Published As

Publication number Publication date
DE102004021629A1 (de) 2005-12-01

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