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
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
  • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
  • F16K31/0644—One-way valve
  • F16K31/0655—Lift valves
  • F16K31/0665—Lift valves with valve member being at least partially ball-shaped
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
  • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
  • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
  • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
  • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
  • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
• • 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
  • F16K31/00—Actuating devices; Operating means; Releasing devices
  • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
  • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
  • F16K31/0644—One-way valve
  • F16K31/0655—Lift valves

Definitions

• the invention relates to a solenoid valve according to the preamble of independent claim 1.
• a conventional solenoid valve in particular for a hydraulic unit, which is used for example in an anti-lock braking system (ABS) or a traction control system (ASR system) or an electronic stability program system (ESP system) is shown in Figure 1.
• ABS anti-lock braking system
• ASR traction control system
• ESP electronic stability program system
• a conventional normally closed solenoid valve 1 which is designed as a switching valve, a valve cartridge 2 and a magnet assembly 13.
• the valve cartridge 2 comprises a
• Valve body 9 having a main valve seat 10 which is arranged between at least a first flow opening 11 and a second flow opening 12.
• the valve body 9 is also designed as a sleeve.
• the magnet assembly 13 includes a winding support 13.1, a housing shell 13.2, a coil winding 13.3 with electrical connections 13.5 and a cover 13.4.
• the axially movable armature 4 When the magnet assembly 13 is energized, ie when the current is applied to the coil winding via the electrical connections 13.5, the axially movable armature 4 is counteracted by a generated magnetic force F Magn et within the valve core 5 against a spring force F spring of a restoring spring 6 and against a fluid force F H yd r au hk against the pole core 3 moves to lift the closing element 8 from the main valve seat 10 and to allow fluid flow between the at least one first flow opening 11 and the second flow opening 12.
• the maximum possible che stroke of the armature 4 and the closing element 8 is determined by the air gap 7 between the pole core 3 and the armature 4.
• Exhaust valves in the ABS / ESP system have so far been designed as pure switching valves, which can be quasi-stationary only fully open or fully closed.
• the outlet valve is traversed as a non-continuous switching valve typically in the stroke-closing direction. This happens against the background that high wheel pressures support the valve tightness. This low spring preloads enough, which allows a lower total force level and thus fast valve reactions.
• Continuous valves have the advantage over switching valves that can be adjusted by adjusting partial strokes between the fully closed and the fully open position arbitrarily adjustable intermediate positions and thus any flow cross sections released or any flow rates can be adjusted through the valve.
• a continuous valve which flows in the opening direction, requires a high spring preload to seal off a required wheel pressure, for example a blocking pressure level.
• the solenoid valve according to the invention with the features of independent claim 1 has the advantage that the stroke-dependent curves of the magnetic force, the spring force and the fluid force over a stroke of an armature and a closing element between a closed position and an open position are combined so that between the closed position and the open position of the armature and the closing element is adjustable at least one further stable operating point, which represents a force equilibrium point with a negative Backraftgradienten. Due to the special selection of the force curves of the spring force, the magnetic force and the fluid force in response to the valve lift, it is possible to set stable working points in a designed as a switching valve solenoid valve, which is flowed through in the closing direction and thus to operate as a continuous valve. Thus, the solenoid valve according to the invention has the advantages of continuous valves while maintaining the advantages, such as tightness at any high pressures, fast valve reactions and low overall force level, a flow-through in the closing direction switching valve.
• the course of the magnetic force brought about by the current flow of the armature and of the closing element between the closed position and the open position by supplying a magnet assembly of the solenoid valve according to the invention is set as flat as possible by specifying geometries of the armature and of the pole core.
• the electric current for energizing the magnet assembly for example as a function of a pressure sensor signal, can be regulated with a valve current regulator.
• the current for energizing the magnet assembly can be adjusted without a pressure sensor.
• the armature can be moved with the closing element by adjusting the current for energizing the magnet assembly by a partial stroke to lift the closing element from the main valve seat and operate the solenoid valve in a quasi-stationary partially open state.
• the current intensity can be adjusted, for example for a short pulse time, by specifying a pulse width modulation ratio (PWM ratio).
• PWM ratio pulse width modulation ratio
• the armature is designed for example as a plunger armature, which forms a single-stage or multi-stage immersion stage with a correspondingly designed pole core.
• the armature can be designed as a flat armature, which cooperates with a pole core having a flat pole face up.
• the corresponding magnetic force has a flat course only from a predetermined width of an air gap between the armature and the pole core.
• the return spring to provide the spring force on a large spring constant.
• the return spring has, for example, a linearly designed spring characteristic with a constant spring rate.
• the return spring can alternatively be designed in such a way that the spring force provided by the return spring overlies Hubverlauf the armature and the closing element has a progressive course.
• This means that the spring rate of the return spring is changed depending on the stroke of the armature and the closing element between the closed position and the open position. Due to the progressive course of the spring force, the stability behavior of the armature with the closing element can be improved and the stable operating range can be widened, the progressive course of the spring force overcompensating for the increase in magnetic force gradient with the stroke.
• the progressive spring force curve of the return spring generates the negativePolkraftgradien- th over an increased stroke range in an advantageous manner.
• the lower spring rates for small strokes allow a higher tolerance of the components, which facilitates mass production.
• the course of the fluid force caused by the fluid flow between the first flow opening and the second flow opening becomes over the course of the stroke of the armature and of the closing element set as flat as possible between the closed position and the open position by specifying flow geometries of the closing element and the main valve seat.
• the flat course of the fluid force over the stroke profile of the armature and the closing element can be predetermined for example by a small opening angle between the closing element and the main valve seat.
• a sealing region of the closing element can be designed, for example, as a ball or as a cone, while a sealing region of the main valve seat is designed as a hollow cone.
• Fig. 1 shows a schematic sectional view of a conventional normally closed solenoid valve.
• FIGS. 2a to 2c show schematic sectional views of a first embodiment of a valve cartridge of a normally closed solenoid valve according to the invention.
• 3a to 3c show schematic sectional views of a second embodiment of a valve cartridge of a normally closed solenoid valve according to the invention.
• FIG. 5 shows a schematic course of a spring rate, which can be changed over a stroke, of a return spring for a solenoid valve according to the invention.
• a conventional solenoid valve valve 1 designed as a flow-closing directional valve has the schematic curves of the magnetic force F Magn et, the spring force F Fe and the fluid force F Hy shown in column 1.
• a conventional solenoid valve 2 designed as a continuous valve through which the air flows in a stroke-opening direction has the schematic curves of the magnetic force F Magn et, the spring force F spring and the fluid force F Hy d r au k shown in column 2.
• a solenoid valve according to the invention designed as a continuous valve through which the closing direction flows has the schematic diagrams of the magnetic force F Magn et, the spring force F spring and the centrifugal force F Hy d r au k shown in column 3.
• the force curve of the magnetic force F Magn et should be as flat as possible over the stroke.
• the return spring should be made as stiff as possible, ie the return spring 26 should have a high spring stiffness.
• the force curve of the fluid force F Hy d r au rii k over the stroke should also be as flat as possible.
• Fp f yd r auii k are inventively combined so that between the closed position and the open position of the armature and the closing element at least one further stable operating point is adjustable, which represents an equilibrium point with a negative Backraftgradienten.
• the total force gradient for the solenoid valve according to the invention results from equation (1).
• a first exemplary embodiment of a valve cartridge 22 for a solenoid valve according to the invention analogous to the conventional solenoid valve 1 shown in FIG. 1, comprises a pole core 23, a valve insert 25 connected to the pole core 23, one inside the Valve insert 25 between a closed position and an open position axially movably guided armature 24 which is coupled to a closing element 28, and connected to the valve insert 25 valve body 29 til stresses 29 with a main valve seat 30, between at least a first flow opening 31 and a second flow opening 32nd is arranged.
• the in Fig. 1 set magnetic bauble to be used.
• the armature 24 is moved in the direction Polkern 23 and lifted the closing element 28 from the main valve seat 30 so that a fluid flow between the at least one first flow opening 31 and the second flow opening 32 set can be.
• the stroke-dependent courses of the magnetic force F Magn et, the spring force F spring and the fluid force F Hy d r au are k by geometry specifications for the armature 24 and the pole core 23, the design of the return spring 26 and by geometry for the flow path between the first flow opening 31st and the second flow opening 32 is generated.
• the armature is designed as a plunger armature 24, which forms a two-stage immersion stage 22.1 with a correspondingly designed pole core 23.
• the plunger armature 24 has two armature stages 24.1, and the pole core 23 has two corresponding pole core stages 23.1, which dip into the armature stages 24.1.
• the course of the magnetic force F magn et caused by the energization of the magnet assembly 13 is set as flat as possible over the stroke progression of the armature 24 and the closure element 28 as desired.
• the armature is designed as a flat armature, which cooperates with a pole core, which has a flat pole face.
• the corresponding magnetic force has a flat course only from a predetermined width of an air gap between the armature and the pole core.
• a sealing region 28. 1 of the closing element 28 as a ball and a sealing region 30. 1 of the main valve seat 30 are configured as hollow cones.
• a small opening angle can be specified in this embodiment between the closing element 28 and the main valve seat 30, the example here, the desired flat profile of the fluid force F H yd r au hk over the stroke course of the armature 24 and the closing element 28 between the closed position and the open position allows.
• a second exemplary embodiment of a valve cartridge 42 for a solenoid valve according to the invention comprises a pole core 43, one with the pole core, analogous to the first exemplary embodiment of the valve cartridge 22 for a solenoid valve according to the invention 43, an armature 44 which is axially movably guided within the valve insert 45 between a closed position and an open position and which is coupled to a closing element 48, and a valve body 49 connected to the valve insert 45
• Main valve seat 50 which is arranged between at least a first flow opening 51 and a second flow opening 52.
• the magnet assembly shown in FIG. 1 can also be used.
• the stroke-dependent curves of the magnetic force F Magn et, the spring force F spring and the fluid force F Hy d r are au k by geometry specifications for the
• Anchor 44 and the pole core 43 the execution of the return spring 46 and generated by geometry specifications for the flow path between the first flow port 51 and the second flow port 52.
• the armature of the second exemplary embodiment is also embodied as a plunger armature 44, which forms a two-stage immersion stage 42. 1 with a correspondingly designed pole core 43.
• the plunger armature 44 likewise has two armature stages 44.1, and the pole core has two corresponding pole core stages 43.1, which dip into the armature stages 44.1.
• Closing element 48 designed as a cone and a sealing region 50.1 of the main valve seat 50 as a hollow cone.
• a small opening angle can be specified between the closing element 48 and the main valve seat 50, which again exemplifies the desired flat Course of the fluid force F Hy d r au k over the stroke course of the armature 44 and the closing element 48 between the closed position and the open position allows.
• the return spring 26, 46 for providing the spring force F spring has a large spring rate and thus a high rigidity.
• a particular advantage is obtained when the spring force F spring provided by the restoring spring 26, 46 has a progressive course over the course of the stroke of the armature 24, 44 and the closing element 28, 48.
• the stability behavior of the solenoid valve according to the invention can be improved and the stable working range can be extended with a negative Intelkraftgradienten.
• the magnetic force gradient rising with the stroke is overcompensated by the progressive course of the spring force F spring .
• the lower spring rates for small strokes allow a higher tolerance of the components, which advantageously facilitates mass production.
• a concrete behavior of the spring rate C Q1) should depend on the stroke h between a minimum permitted course of the spring rate C ⁇ min and a maximum permitted course of the spring rate C ⁇ max.
• the diagram of FIG. 5 shows an optimal course of the spring rate Cosopt.
• the optimum course of the spring rate Cosopt is preferably very progressive for small strokes and ensures the existence of stable operating points for the corresponding solenoid valve according to the invention.
• the current curve for generating the magnetic force F Magn et can be specified so that desired ramps for the pressure reduction in a wheel brake can be traversed without major deviations and thus gentle Radtikregelungen are possible.
• the current to the Current supply of the magnetic bauble can also be adjusted without a pressure sensor.
• the magnetic assembly of the corresponding solenoid valve for example, for a short pulse time with variable currents, which are adjustable, for example, by specifying a pulse width modulation ratio (PWM ratio), are energized.
• PWM ratio pulse width modulation ratio
• solenoid valve according to the invention does not open completely, but only up to a certain partial stroke, which is variable by the set current. For finer metered pressure reduction stages are possible than in a pure switching valve, whereby the noise behavior can be improved.
• the erf ⁇ ndungshiele in hubumblede direction flowed through solenoid valve advantageously has both the benefits of continuous valves while maintaining the benefits, such as tightness at any high pressures, fast valve reaction and low overall force level, a flowing in the closing direction switching valve on.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Electromagnetism (AREA)
• Fluid Mechanics (AREA)
• Transportation (AREA)
• Magnetically Actuated Valves (AREA)
• Regulating Braking Force (AREA)
• Electromagnets (AREA)
• Valves And Accessory Devices For Braking Systems (AREA)

Applications Claiming Priority (2)

Publications (1)

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• 2007
  • 2007-07-10 DE DE102007031981.0A patent/DE102007031981B4/de not_active Expired - Fee Related
• 2008
  • 2008-07-02 JP JP2010515469A patent/JP5535068B2/ja not_active Expired - Fee Related
  • 2008-07-02 WO PCT/EP2008/058469 patent/WO2009007278A1/de not_active Ceased
  • 2008-07-02 US US12/668,595 patent/US8596609B2/en not_active Expired - Fee Related
  • 2008-07-02 CN CN200880023821.XA patent/CN101688625B/zh not_active Expired - Fee Related
  • 2008-07-02 EP EP08785895A patent/EP2167857A1/de not_active Withdrawn

Non-Patent Citations (1)

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