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
  • F16K13/00—Other constructional types of cut-off apparatus; Arrangements for cutting-off
• • 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
  • B60T8/3655—Continuously controlled electromagnetic valves
  • B60T8/366—Valve details
  • B60T8/367—Seat valves, e.g. poppet valves
• • 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
  • B60T15/00—Construction arrangement, or operation of valves incorporated in power brake systems and not covered by groups B60T11/00 or B60T13/00
  • B60T15/02—Application and release valves
  • B60T15/025—Electrically controlled valves
  • B60T15/028—Electrically controlled valves in hydraulic systems
• • 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
  • 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
  • F15B13/044—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

Definitions

• Hydraulic solenoid-operated seat valve in particular for brake systems in motor vehicles
• the invention relates to a hydraulic, solenoid-operated valve according to the preamble of claim 1.
• Such a valve is already known (DE 41 29 638 AI), in which a hollow cylindrical guide body is pressed into the valve housing at a distance from the valve body.
• the guide body has a sleeve-shaped projection directed against the valve body, with which a ball attached to the end of a valve tappet is encompassed approximately as a large circle as the closing body of a seat valve.
• the edge of the guide body which is delimited in the form of a cutting edge on the valve seat side, merges with the concavely curved outer surface to the inner circumference of the valve housing and delimits with the valve body a relatively large valve chamber of the valve housing, two of which are diametrically located
• the guide body has the purpose of diverting the pressure medium flowing along the ball surface when the seat valve is open and thus preventing instabilities of the pressure medium flow along the Spread the plunger into a space in the valve housing in which there is a magnet armature for the seat valve.
• the approach to the guide body must therefore encompass the ball of the valve tappet with little play.
• valve according to the invention with the features of claim 1 is distinguished by the following advantages:
• the pressure medium flow flowing between the valve seat and the front end of the closing body is released from the closing body at the sharp-edged transition to the stem and follows the course of the valve seat as a hollow cone jet.
• the pressure medium jet is taken up by the guide channels when it exits the valve seat and is diverted into the ring channel to the outlet opening.
• the passage of the closing body through the guide body can therefore be provided with a relatively large amount of play, since the area of the guide body which is penetrated by the closing body remains essentially unaffected by the beam guidance due to the aforementioned design.
• valve Since the annular channel, in which the pressure medium flow is deflected relatively strongly, is relatively far from the valve seat, instabilities of the pressure medium flow caused by the deflection largely have no influence on the space in contact with the closing body on the valve seat side. For this reason, the space of the valve housing filled with pressure medium, which contains actuating means of the valve and is connected to the valve seat by the guide body through the guide body, is free from disturbing flow forces.
• the valve is therefore with known methods of electrical control with high Accuracy steplessly controllable in any stroke position of its locking element.
• the course of the guide channels specified in claim 4 is conducive to the deflection of the pressure medium flow from the hollow cone jet to the annular channel.
• a unit of guide body and valve body is created, in which the spatial assignment of the two parts to one another is achieved by a form-fitting connection which is favorable for assembly.
• valve characterized in claim 6 has the advantage that the valve housing, which fits around the spring tongues of the guide body, permanently maintains the positive connection between the guide body and the valve body.
• FIG. 1 shows a Longitudinal section of a hydraulic solenoid-operated valve with a guide body for pressure medium emerging from a valve seat
• Figure 2 in section the area of the valve provided with the guide body on a larger scale
• Figure 3 seen a view of the guide body in the direction of arrow III in Figure 2
• Figure 4 one Section through the guide body along the line IV-IV in Figure 3
• Figure 5 shows a section through the guide body along the line VV in Figure 3.
• solenoid valve essentially has the following components in the same axis
• a thin-walled, tubular valve housing 11 at one end section of which a valve body 12 which is pressure-tightly fixed in the valve housing 11 is arranged, a guide body 13 for pressure medium accommodated in the valve housing 11 and supported on the end face on the valve body 12, a magnet armature 14 guided in the valve housing 11 in a longitudinally movable manner a plunger 15 pressed into this guide body side, a pole core 16 which closes the valve housing 11 at its other end section and is connected to it in a pressure-tight manner, one between the
• Magnetic armature 14 and the pole core 16 arranged return spring 17, a coil 18 encompassing the pole core 16 and the valve housing 11 with an electrical winding 19 and a magnetic flux-conducting housing 20 enclosing the coil 18 with winding 19.
• the magnet armature 14 and the return spring 17 are actuating means of the solenoid valve 10; they are located in a space 21 of the valve housing 11 between the guide body 13 and the pole core 16.
• the valve body 12 has an axis-parallel inlet bore 24 for pressure medium, which merges into a through-bore 25 of smaller diameter and, following this, into a hollow-conical valve seat 26 (FIG. 2).
• the valve seat 26 ends on the mouth side with a sharp edge on an end face 27 on the guide body side, running radially to the longitudinal axis of the valve body.
• the valve seat 26 is assigned a spherical section 28 on an end face of a cylindrical shaft 29, which forms a closing body 30 integral with the tappet 15.
• the closing body 30 is supported with its spherical end face under the action of the return spring 17 on the valve seat 26 of the valve body 12.
• the closing body 30 and the valve seat 26 form a seat valve 31 of the normally closed solenoid valve 10.
• the cylindrical shaft 29 of the closing body 30 has a diameter which is approximately midway between the small diameter determined by the through bore 25 and the orifice-side diameter of the valve seat 26.
• the radius of the ball section 28 is in turn larger than half the diameter of the cylindrical shaft 29 of the closing body 30, so that the transition between the ball section and the cylindrical shaft takes place along a sharp edge 32.
• Closing bodies 30 are coordinated with one another in such a way that a tangent in the axial plane shown in FIG. 2 in the region of the edge 32 on the spherical section approximately follows the opening angle of the valve seat 26.
• the closing body 30 can be lifted off the valve seat 26.
• the edge 32 on the closing body 30 does not emerge from the valve body 12 via the mouth of the valve seat 26.
• the guide body 13 which is supported on the end face of the valve body 12, has a radially projecting, circumferential collar 35 on the magnet armature side, with which it is accommodated in a radially fitting manner in the valve housing 11 (FIG. 2).
• the guide body 13 separates the with its collar 35
• the guide body 13 also has a central through hole 38 for the closing body 30 of the seat valve 31.
• the guide body 13 also has three substantially radially extending ones
• the guide channels 39 are delimited with parallel walls by their side walls 40 and are formed as slots which are open towards an end face 41 of the guide body on the valve body side and the annular channel 36, each of which runs symmetrically to the axial planes of the guide body.
• the bottom 42 of the guide channels 39 is, seen in the longitudinal section of the guide body 13, slightly concave
• the bottom 42 of the guide channels 39 also extends approximately at an angle to the longitudinal axis of the guide body, which corresponds to half the cone angle of the valve seat 26 (FIG. 2).
• the bottom 42 of the guide channels 39 is seen from the end face 41 of the guide body 13 on the valve body side, axially set back so far that an imaginary extension of the bottom 42 opens into the valve seat cross section.
• the three guide channels 39 overlap the outlet-side valve seat outline because of the width of the guide channels in full.
• the guide body 13 is provided on the circumference with three axially extending spring tongues 45 extending between the guide channels 39 (FIGS. 3 and 5). These protrude beyond the end face 41 of the guide body 13 on the valve body side and have a radially inward projection 46 at their free end. With this projection 46, the spring tongues 45 engage in a circumferential groove 47 of the
• Valve body 12 a ( Figure 2).
• the spring tongues 45 are reinforced at the ends corresponding to the collar 35 of the guide body 13 so that their protrusion-side end section is accommodated in the valve housing 11 in a radially fitting manner.
• the guide body 13 can advantageously be produced as a plastic injection molded part.
• the solenoid valve 10 is powered by z. B. current ramp control or pulse width modulation of its electrical winding 19 steplessly controllable in any intermediate positions between the closed position and the position of the maximum valve lift of its seat valve 31.
• the pressure medium present in the inlet bore 24 of the valve body 12 exits the valve seat 26 in the form of a hollow cone jet when the seat valve 31 is open.
• the edge 32 promotes the trouble-free detachment of the hollow cone jet from the closing body 30.
• the hollow cone jet is detected by the three guide channels 39 as it exits the valve seat 26 and is diverted to the annular channel 36. There is a deflection of the pressure medium flow to the outlet openings 37, from which it flows out of the solenoid valve 10.
• the pressure medium flow is largely free of flow instabilities, while those on the outflow side of the guide channels 39 occur.
• Pressure disturbances caused thereby have essentially no effect in the space 21 containing the actuating means 14, 17 of the solenoid valve 12, which is filled with pressure medium and is connected to the valve seat 26 with the valve seat 26 in a pressure medium-conducting connection via the through-hole 38 in the guide body 13 because of the described flow deflection on the valve seat side.
• the pressure-balanced magnet armature 14 is therefore only subjected to hydraulic forces on the ball section 28 of its closing body 30.
• the force of the return spring 17 thus acts on the magnet armature 14 and the hydraulic force on the closing body 30 and the magnetic force open.
• the seat valve 31 can therefore be safely controlled in stable intermediate positions.
• the arrangement of the guide body 13 according to the invention can also be used with a solenoid valve 10
• the guide body 13 can also be provided with only two guide channels or with more than three guide channels.
• the number of spring tongues 45 can also be different or the fastening of the guide body 13 in the
• Valve housing 11 take place in a different way than that described.
• the solenoid valve 10 is used in hydraulic brake systems of motor vehicles, for. B. with slip control, with driver-independent brake pressure control and with brake-by-wire actuation.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Mechanical Engineering (AREA)
• Electromagnetism (AREA)
• Fluid Mechanics (AREA)
• General Engineering & Computer Science (AREA)
• Transportation (AREA)
• Magnetically Actuated Valves (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=7855427

Family Applications (1)

Country Status (6)

Families Citing this family (22)

Family Cites Families (11)

• 1998
  • 1998-01-23 DE DE19802464A patent/DE19802464A1/de not_active Withdrawn
  • 1998-11-20 WO PCT/DE1998/003436 patent/WO1999037517A1/de not_active Application Discontinuation
  • 1998-11-20 EP EP98965088A patent/EP1049613A1/de not_active Withdrawn
  • 1998-11-20 US US09/600,915 patent/US6322049B1/en not_active Expired - Fee Related
  • 1998-11-20 JP JP2000528457A patent/JP2002500986A/ja active Pending
  • 1998-11-20 KR KR1020007007998A patent/KR20010034287A/ko not_active Application Discontinuation

Non-Patent Citations (1)

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