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WO2025261671A1 - Dispositif de soupape et système de direction électrohydraulique - Google Patents

Dispositif de soupape et système de direction électrohydraulique

Info

Publication number
WO2025261671A1
WO2025261671A1 PCT/EP2025/063282 EP2025063282W WO2025261671A1 WO 2025261671 A1 WO2025261671 A1 WO 2025261671A1 EP 2025063282 W EP2025063282 W EP 2025063282W WO 2025261671 A1 WO2025261671 A1 WO 2025261671A1
Authority
WO
WIPO (PCT)
Prior art keywords
slide unit
connection
section
valve assembly
housing body
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.)
Pending
Application number
PCT/EP2025/063282
Other languages
German (de)
English (en)
Inventor
Aymen Tayari
Falk Hecker
Klaus Peterreins
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.)
Kb Intellectual Property & Co Kg GmbH
Original Assignee
Kb Intellectual Property & Co Kg 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 Kb Intellectual Property & Co Kg GmbH filed Critical Kb Intellectual Property & Co Kg GmbH
Publication of WO2025261671A1 publication Critical patent/WO2025261671A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
    • 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
    • B62D5/062—Details, component parts
    • 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
    • B62D5/087—Sliding spool 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0407—Means for damping the valve member movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • 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
    • F15B13/12—Special measures for increasing the sensitivity of the system
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/042—Controlling the temperature of the fluid
    • F15B21/0427—Heating
    • 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
    • F15B2013/008—Throttling member profiles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0412—Valve members; Fluid interconnections therefor with three positions
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/61—Secondary circuits
    • F15B2211/611—Diverting circuits, e.g. for cooling or filtering
    • 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
    • F15B2211/62—Cooling or heating means
    • 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
    • F15B2211/66—Temperature control methods

Definitions

  • the present invention relates to a valve assembly and an electro-hydraulic steering system for a vehicle, in particular a commercial vehicle. Furthermore, the present invention relates to a vehicle, in particular a commercial vehicle, with such a valve assembly and/or such an electro-hydraulic steering system.
  • valve devices only allow adjustment or the setting of a new position in the sense of a valve switching process against an internal fluid pressure. Therefore, the actuation speed of the respective valve device is also limited.
  • a vehicle equipped with such a valve in an associated electro-hydraulic steering system may experience a drop or decrease in operating pressure in the steering system's piston chamber, particularly at low temperatures. This behavior can slow down an electro-hydraulic steering system and/or impair steering response in general.
  • the object of the present invention is to provide a valve device that is cost-effective, efficient, and requires little maintenance, occupies a small installation space, and can provide improved system dynamics and/or system response, and is flexibly designed. Furthermore, the invention aims to provide an electro-hydraulic steering system and a vehicle.
  • valve device according to independent claim 1, with regard to the electro-hydraulic steering system by the subject matter according to claim 13 and with regard to the vehicle by the subject matter of claim 15.
  • a valve assembly particularly for an electro-hydraulic steering system of a vehicle, is provided with at least one housing body having at least one main chamber and at least one slide unit, wherein the slide unit is movably arranged within the main chamber of the housing body, preferably translationally displaceable.
  • the slide unit divides the main chamber into a first section and a second section, wherein the at least one slide unit is designed as a pressure-balanced slide unit and is configured such that at least substantially the same fluid pressure is present in the first section and in the second section, in particular pressure equalization between the first section and the second section is provided via the at least one slide unit.
  • the present invention is based on the fundamental idea that pressure equalization within the main chamber, i.e. between the first section and the second section, results in a lower load on the valve element or valve unit, and thus reduces leakage and wear of the valve assembly.
  • valve assembly leads to a more dynamic and faster adjustment of the slide unit within the Main chamber.
  • the movable slide unit must, at least primarily, only be moved against mechanical resistances, such as frictional forces, in order to provide a new position for the valve assembly.
  • venting a (pressure) connection for example into a hydraulic tank, or connecting or separating two (pressure) connections can be carried out advantageously.
  • the translational displaceability or mobility of the slide unit is understood to mean, in particular, that the slide unit is displaceable within the housing body.
  • the valve assembly or the housing body may have a longitudinal axis so that the slide unit is arranged to be displaceable or movable in the longitudinal direction.
  • the slide unit divides the main chamber into a first section and a second section.
  • the slide unit is therefore positioned within the main chamber in such a way that the volumes of the first and second sections can be changed based on the movement of the slide unit.
  • the slide valve unit or valve assembly can be designed as a unidirectional valve assembly or as a bidirectional valve assembly.
  • the at least one slide unit is designed as a pressure-balanced slide unit.
  • the slide unit is configured such that the fluid pressure in the first section and the second section is at least substantially the same.
  • pressure equalization between the first section and the second section can be provided via or by means of the at least one slide unit, in particular by means of the design of the at least one slide unit.
  • the pressure-balanced design of the valve unit can preferably be understood to mean that a hydraulic short-circuit connection between the first section and the The second section of the main chamber is provided. Therefore, there is no hydraulic separation between the first and second sections by means of the valve unit.
  • valve assembly can be changed or determined based on the pressure-balanced slide unit or the positioning position of the pressure-balanced slide unit within the main chamber, among other things to bring about a hydraulic separation or connection between ports of the valve assembly.
  • the present invention provides a low-maintenance, efficient, and in particular efficiently adjustable, as well as dynamically adjustable valve device.
  • the slide unit in particular a cover element of the slide unit, has at least one through-opening so that a fluid connection between the first section and the second section of the main chamber is provided or can be provided.
  • a hydraulic fluid such as oil
  • a hydraulic fluid can flow from the first or second section to the second or first section along a pressure differential across the passage opening of the valve unit.
  • pressure equalization of the oil or hydraulic fluid within the main chamber i.e., between the first and second sections, can occur across the valve unit.
  • a passage opening can be understood to be a bore, a fluid channel, or the like. Further elements such as throttling elements, filter elements, or the like can be provided within the passage opening.
  • the passage opening of the valve unit allows for the formation of a (temporary) fluid connection between the first and second sections of the main chamber, enabling pressure equalization or a pressure-balanced valve unit.
  • a displacement or change in the position of the slide unit should preferably only occur against mechanical resistance forces, such as internal frictional forces of the valve assembly, but in particular not against a pressure difference between the first and second section of the main chamber.
  • the valve device has at least one sleeve element which is arranged inside the housing body, in particular is arranged immovably, wherein an inner side of the sleeve element and an outer side of the movable slide unit are provided to interact, in particular to form a sealing or fluid-tight sliding connection section by section.
  • a fluid-tight connection of different ports of the valve assembly can be achieved by means of the interaction of at least one section of the outer surface of the slide unit and at least one section of the inner surface of the sleeve element.
  • ports can be separated from one another by means of the interacting surfaces, or a fluid connection can be provided between ports in the valve direction as required.
  • the housing body has at least one first connection, wherein the sleeve element has at least one first connection opening, wherein the first connection opening along the sleeve element is designed to correspond to the first connection of the housing body, so that a fluid connection between the main chamber and the first connection of the housing body can be provided as required, in particular depending on a positioning position of the movable slide unit relative to the sleeve element.
  • the housing body has at least one second connection, wherein the sleeve element has at least one second connection opening.
  • the second connection opening is configured along the sleeve element corresponding to the second connection of the housing body. so that a fluid connection between the main chamber and the second connection of the housing body can be provided as required, in particular depending on a positioning position of the movable slide unit relative to the sleeve element.
  • the housing body has at least one third connection, wherein the third connection is designed along the housing body in such a way that a fluid connection to the main chamber is provided regardless of the position of the movable slide unit.
  • the slide unit is designed and movable in such a way, in particular the outside of the slide unit is provided to interact section by section with the inside of the sleeve element, such that depending on a positioning position of the slide unit
  • a fluid connection can be provided between the first port and the second port of the housing body
  • a fluid connection can be provided between the first port and the third port of the housing body
  • a fluid connection between the second port and the third port of the housing body can be provided and/or
  • a fluid connection between the main chamber and at least one connection of the housing body can be provided via at least one connection opening of the sleeve element.
  • a fluid connection to the main chamber in particular for a first connection and a second connection, can be provided or disconnected via the movable slide unit.
  • first connection or multiple first connections may be provided, which are connectable or disconnectable.
  • second connection or a plurality of second connections may be provided, which is/are connectable or disconnectable.
  • a single third port or a plurality of third ports may be provided, which has/have a permanent fluid connection to the main chamber.
  • a fluid connection between connections of the housing body via the main chamber can be provided by releasing or separating a connection opening of the sleeve element through such interaction.
  • a multitude of fluid connections between the first, second and/or third ports of the housing component can be provided by means of the pressure-balanced slide unit in operative connection with the sleeve elements via/along the main chamber in order to ensure appropriate interconnection or use of the valve assembly.
  • the slide unit has at least one sealing section along the outside for interaction with the inside of the sleeve element, in particular for interaction with a counter section of the inside of the sleeve element, so that a fluid connection between the first port, the second port and/or the third port can be disconnected as required.
  • sections may be provided along the outside of the slide unit and along the inside of the sleeve element which are designed and intended to interact with each other, in particular so that a sealing effect can be provided as required.
  • fluid connections between various ports of the housing components can be established or disconnected depending on the position of the pressure-balanced slide unit.
  • the sealing section of the slide unit designed to interact with the opposite section of the sleeve element, is provided in such a way, in particular with an effective surface designed in such a way in combination with the opposite section of the sleeve element, that the at least one sealing section forms a stop for the movable slide unit with the at least one opposite section.
  • a sealing section of the slide unit can have a specific geometric design, so that a fluid-sealing end stop can be provided for the pressure-balanced slide unit.
  • the valve assembly has a drive unit, preferably an electromagnet, for moving the slide unit, preferably for translational movement in a longitudinal direction of the valve assembly.
  • a drive unit preferably an electromagnet
  • the drive unit ensures targeted and efficient positioning and movement of the pressure-balanced slide unit within the main chamber.
  • the valve assembly has at least one preloading element, in particular a spring element, for preloading the slide unit in a direction of movement of the slide unit.
  • a preloading element is arranged in the slide unit.
  • the pre-tensioning element can be used in particular to provide pre-conditioning of the pressure-balanced slide unit.
  • an electro-hydraulic steering system for a vehicle in particular a commercial vehicle, is provided with a valve device according to the invention.
  • the steering system further comprises:
  • At least one steering gear in particular a screw steering gear
  • valve device connected or connectable to the first line and/or the second line according to one of the preceding claims for pressure reduction in the first line and/or the second line, wherein the valve device is actuable as required, in particular electromagnetically actuated.
  • valve assembly with a pressure-balanced slide unit ensures a targeted, efficient and dynamic supply of changing or alternating fluid connections along first, second and/or third ports.
  • an advantageous pressure reduction within the electro-hydraulic steering system can be achieved by means of the valve device. This must be ensured to guarantee the proper and safe functioning of the steering system.
  • a vehicle in particular a commercial vehicle, is provided with an electro-hydraulic steering system according to the present invention and/or a valve device according to the invention.
  • Fig. 1 shows a sectional view of an embodiment of a valve device in various switching states
  • Fig. 2 shows a sectional view of another embodiment of a
  • Fig. 3 shows a sectional view of another embodiment of a
  • Fig. 4 shows a representation of different configurations for a valve device, in particular according to one of the embodiments shown in Figs. 1 to 3;
  • Fig. 5 shows a sectional view of another embodiment of a
  • Fig. 6 shows a sectional view of another embodiment of a
  • Fig. 7 shows a circuit arrangement of an embodiment of a steering system
  • Fig. 8 shows a representation of a circuit arrangement of another
  • Fig. 9 shows a representation of a circuit arrangement of another
  • Fig. 10 shows a representation of a circuit arrangement of another
  • Fig. 11 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system
  • Fig. 12 shows a schematic representation of a circuit arrangement of another embodiment of a steering system
  • Fig. 13 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system
  • Fig. 14 shows a schematic representation of a circuit arrangement of another
  • Fig. 15 shows a sectional view of another embodiment of a valve device.
  • Fig. 1 shows a sectional view of an embodiment of a valve device 100 in various switching states.
  • the valve assembly 100 is provided according to Fig. 1 with a housing body 110 in which a main chamber 120 is formed, with a slide unit 130, a sleeve element 140 and a drive unit 150.
  • valve assembly according to Fig. 1 is designed as a normally open 3/3 valve.
  • the housing body 110 can be designed in one piece or in multiple parts. According to Fig. 1, a multi-part design is provided, wherein the housing body 110 can be provided with a separately designed upper part for closing the main chamber 120.
  • the housing body 110 can extend along a longitudinal axis X as shown in Fig. 1.
  • the drive unit 150 is attached to a longitudinal end of the housing body 110.
  • the slide unit 130 is movable within the main chamber 120 by means of the drive unit 150, in particular translationally displaceable in the direction of the longitudinal axis X.
  • the housing body 110 and the components arranged therein can be designed symmetrically, in particular rotationally symmetrically, with respect to the longitudinal axis X.
  • a piston rod 152 extends from the drive unit 150 into the main chamber 120 and into the slide unit 130.
  • the slide unit 130 is coupled to the drive unit 150 via the piston rod 152.
  • the housing body is designed with at least one first (hydraulic) connection 111, at least one second (hydraulic) connection 112 and at least one third (hydraulic) connection 113.
  • the first and second ports 111 and 112 can, for example, serve as hydraulic connections for hydraulic lines, preferably for a bidirectional steering gear.
  • the third port 113 can, for example, serve as a connection for a supply line to a hydraulic tank.
  • the first and third ports 111 and 113 are provided as pressure ports (designation according to Fig. 1: P1, P2), with the second port 112 being provided as a port for a hydraulic tank (designation according to Fig. 1: T).
  • the slide unit 130 and the sleeve element 140 are arranged within the housing body 110.
  • the sleeve element 140 is fixedly arranged within the housing body 110.
  • the slide unit 130 is movable within the main chamber 120, in particular translationally displaceable.
  • the slide unit 130 can be understood as being arranged in the main chamber 120.
  • the sleeve element can be understood as being arranged within the housing body 110, wherein the main chamber 120 is determined or defined by the sleeve element 140 in conjunction with the housing body 110.
  • the sleeve element 140 can be configured with at least one first connection opening 141 and at least one second connection opening 142. As shown in Fig. 1, preferably at least two first and second connection openings 141 and 142 are provided.
  • the first connection opening 141 is designed along the sleeve element 140 such that it is essentially aligned with or oriented towards the first connection 111 of the housing body 110.
  • the second connection opening 142 is designed along the sleeve element 140 such that it is essentially aligned with or oriented towards the second connection 112 of the housing body 110.
  • the sleeve element 140 is designed along one outer surface such that a flow path from the first and second connection openings 141 and 142 to the first and second connections 111 and 112, respectively, is ensured.
  • the sleeve element 140 has a flow path groove 148 along its outer surface for the first and second connection openings 141 and 142.
  • the flow path grooves 148 can each be circumferential flow path grooves 148, so that a fluid connection is provided between several first or second connection openings 141 ; 142 arranged distributed along a circumference of the sleeve element 140 and to the first or second connection 111 ; 112 of the housing body 110.
  • Adjacently arranged flow path grooves 148 can be hydraulically separated from each other by means of sealing elements on the sleeve element 140 and/or on the housing body 110.
  • the sleeve element 140 has an inner surface 144.
  • the inner surface 144 is designed to interact or interact, particularly sectionally, with the slide unit 130, and in particular with an outer surface 136 of the slide unit 130.
  • the slide unit 130 can be designed as a single piece or as a multi-piece unit. According to Fig. 1, the slide unit 130 has a separately formed cover element 132, in conjunction with a shell section or shell element.
  • the slide unit 130 can essentially be designed in a pot shape.
  • the slide unit is provided to be movable, in particular to be displaceable along the longitudinal axis X of the valve assembly 100.
  • the valve unit 130 divides the main chamber 120 into a first section 122 and a second section 124.
  • the volumes of the two sections 122 and 124 can differ. Depending on the position of the slide unit 130 within the main chamber 120, they complement each other to form the main chamber 120 as a whole.
  • the main chamber 120 can be understood as being limited or formed by an inner side of the housing body 110 and an inner side 144 of the sleeve element 140.
  • the slide unit 130 has at least one through-opening 134, so that a fluid connection between the first section 122 and the second section 124 of the main chamber 120 can be provided.
  • two or more passage openings 134 symmetrically designed with respect to the longitudinal axis X, can be provided.
  • the at least one through-opening 134 can be configured as a fluid connection, a fluid channel, or the like, in the sense of a short circuit.
  • filter elements, throttling elements, or the like can be provided in the at least one through-opening 134.
  • the adjustment or movement of the slide element 130 within the main chamber 120 shall occur, at least substantially, independently of or without the influence of a fluid pressure difference between the first and second sections 122; 124.
  • the slide unit 130 is designed as a pressure-balanced slide unit, at least substantially.
  • the sliding unit 130 has an outer surface 136.
  • the outer surface 136 of the slide unit 130 is provided, at least in sections, for interaction with the inner surface 144 of the sleeve element, in particular for the joint formation of a fluid-tight sliding connection along which the slide unit 130 is movable within the main chamber 120.
  • the outer surface 136 can have a U-shaped basic form.
  • the gate unit 130 can be designed with a flow path groove 137 along the outside 136.
  • the at least one flow path groove 137 along the outer side 136 of the slide element 130 is designed such that a fluid connection between the at least one first and second connection opening 142 of the sleeve element 140 can be provided as required by means of the flow path groove 137 of the slide unit 130, in particular depending on the positioning position of the slide unit 130 within the main chamber 120.
  • a fluid connection between the at least one first and second connection opening 142 of the sleeve element 140 can be separated as required by means of the fluid-tightly interacting outer surface 136 and inner surface 144, in particular if the slide unit 136 assumes a different or different position within the main chamber 120.
  • the housing body 110 has a third connection 113.
  • the third connection 113 can be formed at a longitudinal end, preferably opposite the drive unit 150.
  • the third connection 113 can be provided in such a way that a continuous fluid connection to the main chamber 120, in particular to the second section 124, is present, regardless of the position of the slide unit 130.
  • a fluid connection between the first port 111 and the third port 113 can be provided via the main chamber 120 or the second section 124, the first port opening 141 and the associated flow path groove 148 of the sleeve element (see Fig. 1, left illustration).
  • the slide unit 130 can assume a position by which the second port opening 142 of the sleeve element 140 can be covered fluid-tight by means of the outer surface 136 of the slide unit 130, in conjunction with the inner surface 144.
  • a fluid connection between the first port 111 and the second port 112 can be provided via the first and second port openings 141 and 142 and the respective associated flow path grooves 148 of the sleeve element 140 (see Fig. 1, center view).
  • the specific position of the slide unit 130 can align the flow path groove 137 with respect to the first and second port openings 141 and 142 such that a fluid-tight fluid connection is provided within the main chamber 120, in particular fluid-tightly separated from the first and second sections 122 and 124.
  • the flow path groove 137 of the slide unit 130 can be understood as a type of short circuit.
  • the slide unit 130 with the flow path groove 137 provides a direct and isolated fluid connection between the first and second port openings 141 and 142. 142 or the first and second connections 111; 112 are ready.
  • a fluid connection between the second and third ports 112 and 113 can be provided by means of a further positioning position of the slide unit 130 (see Fig. 1, right-hand illustration).
  • the slide unit 130 can be positioned such that the first connection opening 141 is fluid-tightly separated by the outer surface 136 of the slide unit 130, in particular from the main chamber 120.
  • the flow path groove 137 of the slide unit 130 can completely overlap and encompass the first connection opening 141.
  • the fluid connection can extend from the first port 112, via the flow path groove 148 and the second connection opening 142 of the sleeve element 140, into the main chamber 120 and thus provide access to the third port 113.
  • the fluid connection can extend from the first port 112 within the main chamber 120.
  • Section 122 extends via at least one passage opening 134 of the slide unit 130 into the second section 122, to which the third connection 113 according to Fig. 1 is directly connected.
  • valve device 100 As shown in a first embodiment according to Fig. 1, it is conceivable to implement various functionalities in an electro-hydraulic steering gear.
  • a leakage function to facilitate pump operation, to minimize (pressure/volume flow) fluctuations at low speeds and/or to increase the efficiency of the pump function, in particular by skipping or omitting a critical operating range of the pump (due to mixing and friction behavior) and ensuring an optimal operating range;
  • a parking heater function can be implemented during idling (see Fig. 1, left illustration).
  • a normally open 3/3-way valve can be implemented by means of various positioning positions of the pressure-balanced slide unit 130 within the main chamber 120.
  • the normally open position of the valve assembly 100 is to be understood as a fluid connection of the pressure ports according to the first with the third port 111 ; 113 (in Fig. 1 : P1 and P2) according to Fig. 1.
  • the at least one first connection opening 141 is covered and hydraulically separated by means of the outer surface 136 of the slide unit 130.
  • the pretensioning element 160 pretensions the slide unit 130 in one direction of movement.
  • Fig. 2 allows for the implementation of various functionalities in an electro-hydraulic steering gear, starting from the functions described in the embodiment shown in Fig. 1:
  • a leakage function to facilitate pump operation, to minimize (pressure/volume flow) fluctuations at low speeds and/or to increase the efficiency of the pump function, in particular by skipping or omitting a critical operating range of the pump (due to mixing and friction behavior) and ensuring an optimal operating range;
  • a heating function for warming the hydraulic fluid, the hydraulic pump 1114 and/or the steering gear 1102 during operation i.e. by means of a connection between one of the pressure ports P1 or P2 with the hydraulic tank T), whereby heating in only unidirectional (delivery) direction or in bidirectional (delivery seal of the hydraulic pump 1114) is conceivable;
  • a normally closed 3/3-way valve can be implemented according to Fig. 2.
  • Fig. 4 shows a representation of various configurations for a valve assembly 100, in particular according to one of the embodiments according to Figs. 1 to 3.
  • Fig. 4 shows an outside of the sleeve element 140 in expanded form.
  • connection openings 141 ; 142 along the sleeve element 140 can be used to influence, in particular, the control behavior in operative connection with the slide unit 130, especially the outside 136 of the slide unit 130, and/or the flow behavior during the presence of a (partial) fluid connection.
  • Fig. 5 shows a sectional view of another embodiment of a valve device 100. The differences compared to the embodiments described above will be discussed in detail below.
  • a fluid connection can be provided using the opposing sections 146 as (end) stops for a positioning position of the slide unit 130.
  • a hydraulic fluid connection between the second port 112 (according to Fig. 5: pressure port P2) and the third port 113 (according to Fig. 5: pressure port P1) is not provided according to Fig. 5.
  • the embodiment shown in Fig. 6 can preferably act or be used as a proportional valve.
  • the housing body has only the first connection 111 and the third connection 113.
  • the first connection 111 and the second connection 112 can be used as pressure connections (P1 and P2, as shown in Fig. 6).
  • one of the first and third connections 111 and 113 could be connected to a (hydraulic) tank.
  • the sleeve element 140 is designed with at least one first outlet opening 141 and an associated flow path groove 148.
  • the outer surface 136 of the slide unit 130 is designed according to Fig. 6 to interact with the inner surface 144 of the sleeve element 140 in such a way that a counter section 146 forms a single stop for the sealing section 138 of the outer surface 136.
  • the sealing section 138 at a longitudinal end of the slide unit 130 can be designed as a single-stage or multi-stage chamfer of the outer surface 136 such that the slide unit 130 can come into contact with the opposite section 146 in a corresponding positioning position, in order to form a fluid-tight (contact) connection.
  • sealing section 138 can be formed along the outside 136 at one end of the slide unit 130 facing the drive unit or the third connection 113.
  • the slide unit 130 If the slide unit 130 is moved to a further positioning position, the fluid-sealing contact between the counter section 146 and the sealing section 138 is released, and a fluid connection can be established from the first port 111 via the flow path groove 148, which provides at least one first connection opening 141 into the first section 122 of the main chamber 120. From the first section 122 of the main chamber 120, the fluid connection can be continued via the at least one through-opening 134 of the pressure-balanced slide unit 130 into the second section 124 and up to the third port 113 of the housing body 110.
  • the sealing section 138 is illustrated in Fig. 6 as a two-stage sealing section 138, wherein the sealing section 138 has two differently shaped areas, in particular two areas with different chamfers.
  • the two or more areas of the sealing section 138 can be in The fluid-tight contact with the sleeve element is separated from each other by the opposite section 146.
  • sealing section 138 As a multi-stage sealing section 138, a changing behavior of the slide unit 130 during pressure build-up before, during and after the occurrence or dissolution of a (fluid-)sealing contact between the slide unit 130 and the sleeve element 140 can be provided.
  • the preload element 160 preferably in the form of a (compression) spring, can be provided within the main chamber 120, in particular the second section 124, and in direct contact with the slide unit 130.
  • the preloading element 160 can be used to preload the slide unit 130 in the direction of or against the opposite section 146 as a stop.
  • Fig. 6 illustrates the implementation of various functionalities in an electro-hydraulic steering gear, starting from the functions described in Fig. 1:
  • - a leakage function to facilitate pump operation, to minimize (pressure/volume flow) fluctuations at low speeds and/or to increase the efficiency of the pump function, in particular by skipping or omitting a critical operating range of the pump (due to mixing and friction behavior) and ensuring an optimal operating range; a heating function to warm the hydraulic fluid, the hydraulic pump 1114 and/or the steering gear 1102, during the idling of the hydraulic pump (i.e., hydraulic short circuit within the valve assembly 100 between the pressure ports P1 and P2), wherein heating in only a unidirectional (delivery) direction or in a bidirectional (delivery) direction of the hydraulic pump 1114 is conceivable; - a damping function based on a (targeted) leakage between the pressure side P1 ; P2 and the tank T (in Fig. 2: first or third port 111 ; 113 in conjunction with the second port 112);
  • a normally closed 2/2-way valve or 2/2-proportional valve can be implemented.
  • valve device 100 shown within the scope of this invention can be designed as a directional control valve, a spool valve, or an on/off valve, or as a proportional valve with appropriately designed, in particular single-stage or multi-stage beveled, sealing sections 138 along the outside 136 of the spool unit 130.
  • the design as a proportional valve can be provided by a targeted structuring or surface (size) modification of the outside 136 of the slide unit 130, for example in the form of grooves or the like.
  • Fig. 7 shows a representation of a circuit arrangement of an embodiment of a steering system 1000.
  • the electro-hydraulic steering system 1000 can have a valve device 100 according to one of the embodiments described above in Figs. 1 to 6.
  • the electro-hydraulic steering system 1000 for a commercial vehicle has a steering gear 1102 in the form of a spindle steering gear.
  • the screw steering gear 1102 can be designed as a ball screw steering gear, although other types of gears are also conceivable.
  • the electro-hydraulic steering system 1000 further includes a first line 1104 through which the steering gear 1102 can be supplied with hydraulic fluid and controlled. Accordingly, the electro-hydraulic steering system 1000 has a second line 1106 through which the steering gear 1102 can also be supplied with hydraulic fluid and controlled.
  • the steering system 1000 has a valve assembly 100, preferably a valve assembly 100 according to one of the embodiments shown in Figs. 1 to 6.
  • the valve assembly 100 can, for example, be designed as a 3/3-way valve assembly, an on/off valve assembly, or a low-pressure valve assembly.
  • the valve assembly 100 is connected on the input side to the first line 1104 and also on the input side to the second line 1106.
  • valve assembly 100 is also connected or connectable on the output side via a return line 1112 of the steering system 1000 to a hydraulic tank 1110.
  • a hydraulic fluid can be transferred or forwarded to the hydraulic tank 1110 via the valve device 100.
  • valve device 100 can, for example, be used for pressure reduction in the first line 1104 and/or the second line 1106.
  • the valve assembly 100 can be actuated or controlled on demand, preferably electromagnetically, by means of a control unit that is assigned to or associated with the steering system 1000 and is not shown in the figures.
  • the pump unit 1114 is connected to the first and second lines 1104, 1106.
  • the pump unit 1114 can be designed as a double-acting hydraulic pump, so that depending on the direction of rotation either the first line 1104 or the second line 1106 can be printed. Alternatively, it may also be conceivable that only a single-acting hydraulic pump is provided and is connected to the first and second lines 1104; 1106 via a corresponding switching valve (not shown in the figures), which connects the hydraulic pump to the first or the second line 1104; 1106 depending on the switching logic.
  • pump units 1114 could be provided, with one pump unit 1114 being assigned to or connected with the first or the second line 1104, 1106.
  • the pump unit 1114 in Fig. 7 can be connected to the steering gear 1102 via the first line 1104 and, alternatively, via the second line 1106, so that the actual connection depends on a direction control of the pump unit 1114.
  • Such control can be effected by a control unit that is assigned to or associated with the steering system 1000 and is not shown in the figures.
  • the hydraulic tank 1110 is symbolically shown outside a module 1126 of the pump unit 1114.
  • the hydraulic tank 1110 or an additional hydraulic tank can also be provided inside the module 1126 of the pump unit 1114 (see the following embodiments according to Figs. 11 to 13).
  • the first line 1104 and the second line 1106 are connected to the hydraulic tank 1110 via the check valves 1118; 1120 (not explicitly illustrated in Fig. 7).
  • the two check valves 1118; 1120 can be arranged in such a way that hydraulic fluid can be supplied from the hydraulic tank 1110 to the pump 1114 via the check valves 1118; 1120, while preventing backflow towards the hydraulic tank 1110.
  • the first check valve 1118 and the second check valve 1120 can also serve and/or function as suction valves in this case.
  • a pressure build-up in particular a pressure build-up controllable or controlled via a control unit assignable or associated to the steering system 1000, for example the already named, can thus take place under the influence, preferably support, of the suction valves.
  • first and second check valves 1118; 1120 can assist the pump 1114 in building up pressure, especially along the first and second lines respectively up to the steering gear 1102.
  • the pump unit 1114 or the construction module 1126 can also be assigned a temperature sensor 1122 and a pressure sensor 1124, which are provided, for example, along the at least one suction line 1116.
  • the temperature sensor 1122 and the pressure sensor 1124 can be connected or linked to the control unit of the pump unit 1114 and/or a control unit that can be assigned or associated with the steering system 1000, for example the one already mentioned above, for controlling an operation and/or partial operation of the steering system 1000 via signal technology.
  • an additional backup valve 1160 can be provided on the steering gear 1102.
  • a backup valve 1160 can, for example, be integrated into the valve assembly 100.
  • the backup valve 1160 can be connected, at least indirectly, to the first line 1104 via the pressure chamber of the steering gear 1102 assigned to the first line 1104.
  • the backup valve 1160 can be indirectly connected to the second line 1106 via the respective pressure chamber of the steering gear 1102 assigned to the second line 1106.
  • the respective pressure chambers of the steering gear 102 can be connected and preferably short-circuited by means of the backup valve 1160, especially in an emergency situation or in the event of a fault.
  • the backup valve 1160 can thus form and/or enable a fault circuit that is not specifically indicated in the figures and/or function as such.
  • the backup valve 1160 can switch from its closed position to a through position in order to provide a fluid short circuit between the two pressure chambers of the steering gear 1102.
  • the backup device or the backup valve device in particular the backup valve 1160, can be controlled or controlled via a control unit that can be assigned to or associated with the steering system 1000.
  • the pump 1114 As soon as the pump 1114 is driven by the drive unit or the electric motor (e.g. counterclockwise), it can pressurize the section of the first line 1104, which extends to the steering gear 1102 and to a first connection 1128 of the valve assembly 100, with hydraulic fluid pressure. With regard to the short-term and/or long-term temperature control of the hydraulic fluid during commissioning or continuous operation of the electro-hydraulic steering system 1000, the hydraulic fluid can be circulated by means of the pump unit 1114 and via the valve device 100 along the return line 1112.
  • the pump 1114 can pump the hydraulic fluid via the first or second pump fluid connection along the first or second line 1104; 1106 to the valve assembly 100 with the inlet connections 1128; 1130.
  • the hydraulic fluid can be returned directly to the hydraulic tank 1110 via the return line 1112.
  • pressure build-up for the application of steering assistance can be carried out using the present steering system 1000 as described below:
  • the hydraulic pump 1114 can be supported by the second check valve 1120, which acts as a suction valve, especially if the pump 1114 generates a sufficient negative pressure along the second line 1106, which leads to the opening of the second check valve 1120.
  • the pump 1114 and the steering gear 1102 are connected to each other via the first line 1104 and the connection of the steering gear 1102 connected to the first line 1104 is printed.
  • the second pressure chamber can be understood as a low-pressure chamber.
  • the pressure in the opposite second pressure chamber is therefore lower because the connection of the steering gear 1102 is connected to the return line 1112 via the section of the second line 1106 and via the valve assembly 100.
  • the hydraulic fluid is displaced from the opposite, second pressure chamber and via the valve assembly 100 into the return line 1112 and then fed back to the hydraulic tank 1110 via the return line 1112.
  • a rapid return of the hydraulic fluid can be initiated, for example, if the operating pressure in the first line 1104 is higher compared to the operating pressure in the second line 1106 and the second line 1106 is connected to the return line 1112 by means of the at least partially controllable valve device 100.
  • the second line 1106 can be connected to the return line 1112 depending on the pressure difference between the first line 1104 and the second line 1106 and the actuable valve device 100.
  • the pump 1114 can preferably only be driven in one direction of rotation and therefore only the first or the second line 1104, 1106 can be printed on at any given time.
  • first line 1104 is therefore printed by the hydraulic pump 1114, whereas the second line 1106 is not printed, at least in the section between pump 1114 and steering gear 1102 and/or valve assembly 100. If the direction of rotation of pump 120 is reversed, the previously described relationship or case occurs in exactly the opposite way, as described below:
  • the pump 1114 As soon as the pump 1114 is driven by the drive unit or the electric motor (now clockwise), it prints the section of the second line 1106, which extends to the steering gear 1102 and to a second connection 1130 of the valve assembly 100.
  • the pump 1114 is supported by the first check valve 1118, which acts as a suction valve.
  • the pressure in the associated second pressure chamber of the steering gear 1102 increases, and the piston is forced into a displacement movement because the pressure in the opposite first pressure chamber is now lower, thus achieving steering assistance.
  • the first pressure chamber of the steering gear 1102 can be considered a low-pressure chamber.
  • the pressure in the opposite first pressure chamber is therefore lower because the connection of the steering gear 1102 is connected to the return line 1112 via the section of the first line and via the valve assembly 100.
  • the hydraulic fluid is displaced from the opposite, first pressure chamber and directed via the valve assembly 100 into the return line 1112 and then fed back to the hydraulic tank 1110 via the return line 1112.
  • a rapid return of the hydraulic fluid can be initiated if the operating pressure in the second line 1106 is higher compared to the operating pressure in the first line 1104 and by means of the at least partially controllable Valve assembly 100 connects the first line 1104 to the return line 1112.
  • the first line 1104 can be connected to the return line 1112 depending on the pressure difference between the first line 1104 and the second line 1106 by means of the actuable valve device 100, preferably by means of the actively controllable valve device 100.
  • the pump 120 can preferably only be driven in one direction of rotation, and therefore only the first or the second line 1104; 1106 can be printed on at any given time.
  • the second line 1106 is therefore printed by the (hydraulic) pump 120, whereas the first line 1104 is not printed, at least in the section between pump 1114 and steering gear 1102 and/or valve assembly 100.
  • either the first or the second line 1104; 1106 is printed, so that the steering gear 1102 is preferably always printed by only one of the lines 1104; 1106 and thus the other line 1 104, 1106 (which is not printed) can be connected or is connected to the return line 1112 via the valve device 100.
  • the control/pressure of the steering gear 1102 via the first line 1104 or the second line 1106 also changes accordingly.
  • the piston displacement direction can be rapid, and a fast and dynamic change of steering direction can be achieved.
  • Fig. 8 shows a representation of a circuit arrangement of a further embodiment of a steering system 1000. The differences compared to the embodiments described above will be discussed in detail below.
  • an additional or supplementary hydraulic tank 1210 can be provided within the assembly module 1126.
  • the additional or supplementary hydraulic tank 1210 can be provided as an integral component of the assembly module 1126, for example, the hydraulic pump 1114, parallel to the hydraulic tank 1110 connected to or flanged to the assembly module 1126.
  • a return line check valve 1202 is provided along the return line 1112 between the (hydraulic) tank 1210 and the valve assembly 100.
  • the return line check valve 1202 can be arranged along the return line 1112 in such a way that an oil flow or oil leakage from the valve assembly 100 via return line 1112 into the hydraulic tank 1210 is provided or enabled and an opposite backflow, i.e. from the hydraulic tank 1210 via the return line 1112 to the valve assembly 100, can be prevented.
  • Fig. 9 shows a representation of a circuit arrangement of a further embodiment of a steering system 1000. The differences compared to the embodiments described above will be discussed in detail below.
  • the embodiment according to Fig. 9 differs from the embodiment according to Fig. 7 in particular in the design of the hydraulic pump 1114 and the connection of the hydraulic tank 1110.
  • the hydraulic pump 1114 is connected to the hydraulic tank 1110 only via the leakage line 1115.
  • the hydraulic tank 1110 has a fluid connection to the steering gear 1102 and the hydraulic pump 1114 via the return line 1112 with the valve assembly 100.
  • Fig. 10 shows a representation of a circuit arrangement of a further embodiment of a steering system 1000. The differences compared to the embodiments described above will be discussed in detail below.
  • Fig. 10 in comparison to the embodiment according to Fig. 9, it is particularly provided that the steering system 1000 is designed without a separate backup valve 1160.
  • the backup valve 1160 can be integrated into the valve assembly 100.
  • the steering system 1000 can be configured without a backup valve 1160.
  • Fig. 11 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system 1000.
  • Fig. 11 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system 1000.
  • an additional or supplementary hydraulic tank 1210 in addition to and preferably in connection with the hydraulic tank 1110, can be provided within the construction module 1126 as a possible alternative.
  • the valve assembly 100 is connected or connectable on the output side via the return line 1112 to the pump unit 1114, in particular to the module 1126 of the pump unit 1114, and to the associated hydraulic tank 1210, as shown in Fig. 11.
  • a filter unit 1208 can also be provided along the return line 1112, as shown in Fig. 11.
  • the filter unit can be arranged between the additional hydraulic tank 1210 and the return line check valve 1202.
  • the filter unit can be designed as part of the module 1126, as shown in Fig. 11, or it can be attached to or flanged to the module 1126.
  • the filter unit 1208 can be provided independently of the module 1126 along the return line 1112.
  • the valve device 100 can therefore transfer or forward a hydraulic fluid to the construction module 1126 of the hydraulic pump 1114 and into the hydraulic tank 12120, for example for efficient temperature control of the hydraulic fluid, for example during the initial commissioning of the electro-hydraulic steering system 1000.
  • the hydraulic tank 1210 As can be seen in Fig. 11, the hydraulic tank 1210, as part and/or supplement to the hydraulic tank 1110, is symbolically represented within the construction module 1126, in the sense of an integrated design.
  • valve assembly 100 Using the valve assembly 100, the hydraulic fluid can be returned directly to the hydraulic pump module 1114 via the return line 1112 in order to return to the hydraulic tanks 1110; 1210.
  • the valve assembly 100 preferably enables a short-circuit circulation of the hydraulic fluid via the hydraulic tanks 1110 and 1210 of the hydraulic pump 1114. This allows for the short-term adjustment of the hydraulic fluid's operating temperature and/or temperature control of the pump unit 1114 and other components of the steering system 1000.
  • efficiency can be increased and the operating temperature of the pump unit 1114 can be appropriately set by circulating only the smallest possible volume of hydraulic fluid via the short-circuited fluid connection along the valve assembly 100 and by increasing or adjusting the fluid temperature primarily within the construction module 1126 of the pump unit 1114.
  • a return line check valve 1202 and a filter device 1208 are provided along the return line 1112 between the pump unit 1114 and the valve assembly 100.
  • This arrangement has the advantage that the filter or filter assembly 1208 does not need to be located on the high-pressure side, but rather on the low-pressure side in the return line 1112. Consequently, the filter assembly 1208 can be mechanically less robust and structurally simpler, as it is not subjected to such high pressures. As a result, cost advantages can also be realized through this type of filter design.
  • the return line check valve 1202 according to Fig. 9 is provided between the filter device 1208 and the valve device 100.
  • the return line check valve 1202 can be arranged along the return line 1112 in such a way that an oil flow or oil leakage from the valve assembly 100 via the filter assembly 1208 and a hydraulic fluid connection into the hydraulic tank 1210 is provided or enabled, and an opposite backflow, i.e. from the hydraulic tank 1210 via the filter assembly 1208 to the valve assembly 100, can be prevented.
  • Fig. 12 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system 1000. The differences compared to the embodiments described above will be discussed in detail below.
  • the filter unit 1208, in particular exclusively the filter unit 1208, is arranged along the return line.
  • a steering system 1000 according to Fig. 12 can be designed along the return line 1208 without a check valve 1202.
  • a third check valve 1152 can be arranged in the first line 1104 and a fourth check valve 1154 in the second line 1106, in particular between the valve assembly 100 or the steering gear 102 and the hydraulic pump 1114, so that backflow to the hydraulic pump 1114 or the baud module 1126 and the suction of hydraulic fluid from the steering gear 1102 by the pump 1114 can be prevented.
  • two check valves 1118; 1120; 1152; 1154 can each be arranged, so that, depending on a direction of rotation or delivery of the pump 120, a targeted suction of hydraulic fluid from the hydraulic tank 1110 is made possible.
  • the check valves 1118; 1120; 1152; 1154 prevent or stop the (hydraulic) pump 120 from drawing hydraulic fluid from the steering gear 1102 or the valve device 1108 along the first or second line 1104; 1106.
  • Fig. 13 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system 1000. Particular attention is drawn below to the Differences compared to the exemplary embodiments described above have been addressed.
  • Fig. 13 represents an embodiment in the sense of a combination of the embodiments according to Figs. 11 and 12.
  • the return line check valve 1202 is provided along the return line 1112 next to the filter unit 1208 to prevent hydraulic backflow from the hydraulic tank 1210 to the valve assembly 100.
  • third and fourth check valves 1204 and 1206 are arranged along the first and second lines 1104 and 1106 to prevent hydraulic flow from the steering gear 1102 towards the hydraulic pump 1114.
  • Fig. 14 shows a schematic representation of a circuit arrangement of a further embodiment of a steering system 1000. The differences compared to the embodiments described above will be discussed in detail below.
  • valve assembly 100 is designed without a return line 1112.
  • valve assembly 100 does not have a return line 1112 to the hydraulic tank 1110.
  • the valve assembly 100 is exclusively connected to the first line 1104 and the second line 1106 via the first and second connections 1128 and 1130, respectively.
  • the valve assembly 100 according to Fig. 14 can, for example, be designed as a valve assembly 100 according to the embodiment shown in Fig. 6, in the sense of a 2/2-way valve.
  • Fig. 15 shows a sectional view of another embodiment of a valve device 100. The differences compared to the embodiments described above will be discussed in detail below.
  • valve assembly 100 is provided as a proportional valve, wherein the slide unit 130 has at least one sealing section 138.
  • the sealing section 138 at a longitudinal end of the slide unit 130 is designed as a single-stage sealing section 138, preferably as a continuously uniformly chamfered surface.
  • the design according to Fig. 15 can be understood as providing single-stage proportional behavior, whereas the design according to Fig. 6 allows for multi-stage proportional behavior.
  • the one-piece or multi-piece sleeve element 140 may not have a specifically designed counter-section 146 along its inner surface 144 for interaction with the sealing section 138.
  • interaction between the outer surface 136 of the slide unit 130 and the inner surface 144 of the sleeve element 140 may be provided.
  • the proportional behavior, in particular exclusively the proportional behavior, of the valve assembly 100 or the slide unit 130 is determined by means of the sealing section 138 of the slide unit 130.
  • the implementable functionalities in the case of the embodiment according to Fig. 15 are, in particular the design of the pressure connections P1 ; P2 as first connection 111 and third connection 113, comparable to the functionalities described for the embodiment according to Fig. 6. Based on the design of the valve assembly 100 according to Fig. 15, a normally closed 2/2-way valve or 2/2-proportional valve can be implemented.
  • 3 may be provided, preferably in a recess of the housing body 110 on the drive unit 150 and preferably arranged concentrically to the piston rod 152.
  • the present invention advantageously provides a valve device 100 with a pressure-balanced slide unit 130, which advantageously allows efficient control of hydraulic connections in, for example, an electro-hydraulic steering system 1000.
  • valve device 100 enables the system dynamics or system response of the steering system 1000 to be reliably increased or accelerated during operation, especially during fast steering maneuvers.
  • valve unit 100 can ensure a cost-effective, low-maintenance and simple implementation for reliable and rapid pressure control, e.g. in the sense of pressure reduction in a (low) pressure chamber of the steering gear.
  • the electromagnetically controllable and/or adjustable valve unit 100 allows for an advantageous design with regard to the installation space, the cost and the weight of a steering system in accordance with the present invention.

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  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne un dispositif de soupape (100) ayant au moins un corps de boîtier (110), qui comprend au moins une chambre principale (120), et au moins une unité coulissante (130). L'unité coulissante (130) est positionnée de façon mobile à l'intérieur de la chambre principale (120) du corps de boîtier (110) et divise la chambre principale (120) en un premier compartiment (122) et un second compartiment (124). Ladite unité coulissante (130) est prévue sous la forme d'une unité coulissante à compensation de pression (130) et est conçue de sorte qu'une pression de fluide au moins sensiblement égale règne à l'intérieur de la chambre principale (120) dans le premier compartiment (122) et dans le second compartiment (124). L'invention concerne également un système de direction électrohydraulique et un véhicule.
PCT/EP2025/063282 2024-06-18 2025-05-14 Dispositif de soupape et système de direction électrohydraulique Pending WO2025261671A1 (fr)

Applications Claiming Priority (2)

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DE102024117078.6 2024-06-18
DE102024117078.6A DE102024117078A1 (de) 2024-06-18 2024-06-18 Ventileinrichtung und elektrohydraulisches Lenksystem

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WO2025261671A1 true WO2025261671A1 (fr) 2025-12-26

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WO (1) WO2025261671A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2063937A (en) * 1931-01-10 1936-12-15 John J Kundig Fluid pressure actuator
US2972984A (en) * 1959-01-23 1961-02-28 Chrysler Corp Staggered land spool valve
DE102009008056A1 (de) * 2009-02-09 2010-08-12 Schaeffler Technologies Gmbh & Co. Kg Steuerventile zur Steuerung von Druckmittelströmen

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041025A1 (de) * 2004-03-17 2005-12-08 Continental Teves Ag & Co. Ohg Fahrzeugstabilisierungssystem
JP4905111B2 (ja) * 2006-12-18 2012-03-28 日産自動車株式会社 操舵アシスト装置
DE202019101522U1 (de) * 2019-03-18 2019-04-12 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Lenkunterstützungsvorrichtung für ein Fahrzeug
DE102021212444A1 (de) * 2021-11-04 2023-05-04 Continental Automotive Technologies GmbH Elektromagnetventil, insbesondere zur Anordnung zwischen einem hydraulischen Druckerzeuger und einer schlupfgeregelten Radbremse

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2063937A (en) * 1931-01-10 1936-12-15 John J Kundig Fluid pressure actuator
US2972984A (en) * 1959-01-23 1961-02-28 Chrysler Corp Staggered land spool valve
DE102009008056A1 (de) * 2009-02-09 2010-08-12 Schaeffler Technologies Gmbh & Co. Kg Steuerventile zur Steuerung von Druckmittelströmen

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