EP2601084A1 - Électrovalve et dispositif d'aide à la conduite comportant une telle électrovalve - Google Patents

Électrovalve et dispositif d'aide à la conduite comportant une telle électrovalve

Info

Publication number
EP2601084A1
EP2601084A1 EP11726119.8A EP11726119A EP2601084A1 EP 2601084 A1 EP2601084 A1 EP 2601084A1 EP 11726119 A EP11726119 A EP 11726119A EP 2601084 A1 EP2601084 A1 EP 2601084A1
Authority
EP
European Patent Office
Prior art keywords
armature
solenoid valve
damping element
magnet armature
flow path
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.)
Withdrawn
Application number
EP11726119.8A
Other languages
German (de)
English (en)
Inventor
Klaus-Dieter Fietz
Volker Unsoeld
Manfred Maerz
Valentin Schubitschew
Scott Ducworth
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2601084A1 publication Critical patent/EP2601084A1/fr
Withdrawn legal-status Critical Current

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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F16K47/023—Means in valves for absorbing fluid energy for preventing water-hammer or noise for preventing water-hammer, e.g. damping of the valve movement
    • 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
    • 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
    • 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
    • B60T8/365—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems combining a plurality of functions in one unit, e.g. pressure relief
    • 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
    • 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
    • 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
    • F16K31/0658—Armature and valve member being one single element
    • 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
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0696—Shock absorbing, e.g. using a dash-pot
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/088—Electromagnets; Actuators including electromagnets with armatures provided with means for absorbing shocks

Definitions

  • the invention relates to a solenoid valve having a magnet armature, which is operatively connected to a sealing element of the solenoid valve for its displacement, and at least one flow path, via which fluid chambers arranged on opposite sides of the magnet armature are fluid-connectable or fluid-connected.
  • the invention further relates to a driver assistance device.
  • Solenoid valves of the type mentioned are known from the prior art. They are usually used for driver assistance devices, in particular ABS, TCS or ESP devices.
  • the solenoid valve has the armature, which, in particular axially, is arranged displaceably in the solenoid valve.
  • the armature is operatively connected to the sealing element of the solenoid valve, so that when a shift of the armature and the
  • the sealing element is usually provided to close or release a valve opening of the solenoid valve. If the sealing element is arranged to close the valve opening, it usually sits in a valve seat of the solenoid valve, which is associated with both the valve opening and the sealing element.
  • the sealing element is introduced into a recess of the magnet armature and held therein, wherein the recess is preferably provided on a side facing away from the armature counterpart end face of the magnet armature.
  • the solenoid valve has an actuating device, which is formed by the armature together with an armature counterpart.
  • the solenoid valve thus also has the armature counterpart.
  • This is designed for example as a pole core.
  • the pole core is usually referred to lent a housing of the solenoid valve held stationary while the armature is displaceable relative to the housing. To effect this displacement, the armature and armature counterpart cooperate.
  • the armature counterpart for example, one or more coils, while the armature consists of a magnetizable or magnetic material.
  • the armature counterpart is provided on the front side of the magnet armature.
  • the armature and the armature counterpart are arranged to each other such that they, regardless of the displacement of the armature, can not communicate with each other. Accordingly, there is a gap, the so-called air gap or working air gap, between the magnet armature and the armature counterpart or the end face of the armature facing the armature counterpart and the armature counterpart facing the armature armature.
  • the size of the air gap is dependent on the position of the armature with respect to the armature counterpart. The size of the air gap changes accordingly when the armature is displaced.
  • the fluid chambers are present, wherein the air gap is at least partially formed by one of the fluid chambers.
  • the fluid chamber volume of the fluid chambers is dependent on the position of the armature with respect to the armature counterpart.
  • the fluid chambers can be fluidly connected to one another or fluid-connected via the flow path. This means that with a displacement of the magnet armature fluid from that fluid chamber, in the direction of the
  • Magnetic armature is displaced, in the displacement of the opposite fluid chamber is urged.
  • the flow path is formed by the armature itself.
  • the flow path is therefore defined by an outer contour of the magnet armature and an inner contour of the housing.
  • the solenoid valve with the features mentioned in claim 1 has the advantage that it works both low-vibration and low noise and at the same time allows a high actuating speed.
  • This is inventively achieved by at least one in the flow path at least partially projecting damping element is arranged to be displaceable in the axial direction in the solenoid valve.
  • the damping element can increase the damping of the magnetic valve or of the magnet armature by reducing the flow cross-section of the flow path or increasing the effective cross-section of the armature located in the flow path. This is achieved by the - usually the
  • Magnetic armature associated - damper element at least partially protrudes into the flow path.
  • the damping element should, in particular with respect to the armature, be displaced in the axial direction. It is thus displaceable at least between a first and a second position.
  • the damping element can be attached to the magnet armature or to another element bounding the flow path, for example the housing of the magnet valve. orders be.
  • the damping element projects beyond the outer contour of the magnet armature in the radial direction.
  • the flow path, via which the fluid chambers are fluid-connectable is produced by means of a recess or an opening of the magnet armature.
  • the damping element may also be arranged in a damping element chamber of the magnet armature.
  • the damping element is in particular arranged so displaceable in the axial direction that the damping of the solenoid valve only in at least one
  • Reduced position range which is selected such that a low-noise closing of the solenoid valve is made possible.
  • the damping element is therefore intended to reduce the flow area of the flow path only in a first position range of the armature and thus to increase the damping of the solenoid valve in this.
  • a second position range which is different from the first position range, the flow cross-section of the flow path and thus the damping of the solenoid valve remain unchanged.
  • the displacement of the armature is delayed, so that it moves in this at a lower speed.
  • a movement of the armature is allowed at a higher speed.
  • the movement or displacement of the magnet armature causes the fluid flow along the flow path, with the fluid flowing from one of the fluid chambers into the other of the fluid chambers or vice versa.
  • the fluid flow along the flow path causes a force on the damping element.
  • This actuating force causes the displacement of the damping element in the axial direction.
  • the damping element is mounted such that it can be easily displaced from the fluid flow.
  • no additional adjusting means for displacing the damping element are provided or necessary.
  • the magnet armature has at least one end stop for limiting an axial displacement of the damping element.
  • the axial displacement of the damping element takes place relative to the armature. If the damping element reaches the position of the end stop, this prevents further displacement of the damping element with respect to the magnet armature.
  • the end stop sets the damping element so far in at least one axial direction, as soon as it has reached a certain position with respect to the armature. If the magnet armature is subsequently displaced counter to this axial direction, the damping element is entrained by the magnet armature via the end stop. In this way, the effective cross section of the magnet armature is increased by the damping element or the flow cross section of the flow path is reduced and thus increases the damping of the solenoid valve.
  • a development of the invention provides that the damping element is mounted in a groove of the magnet armature.
  • the groove may be partially formed on the armature or only in one or more peripheral regions.
  • the damping element sits in such a way in the groove that it is mounted with respect to the magnet armature.
  • the groove may, for example, the at least one
  • End stop preferably two opposite end stops form.
  • a further development of the invention provides that the groove of the magnet armature is present between partial elements of the magnet armature.
  • the armature is thus a multi-part, in particular two parts, formed. Such a configuration of the solenoid valve or the magnet armature allows a simple
  • the damping element is assembled with a first of the sub-elements and then at least one further of the sub-elements is mounted on the first of the sub-elements. Subsequently, the damping element sits in the groove of the magnet armature and is held captive in this. Only disassembly of the sub-elements from each other allows removal of the damping element from the groove.
  • a development of the invention provides that one of the sub-elements at least partially, in particular clamping, engages in another of the sub-elements.
  • these interlock For attachment of the sub-elements to each other, it is therefore intended that these interlock.
  • a positive or positive fastening to each other can be realized.
  • the sub-elements engage one another in such a way that a clamping connection is realized.
  • a development of the invention provides that the damping element, the magnet armature at least partially, in particular completely encompasses.
  • the damping element is therefore provided on an outer contour of the magnet armature.
  • the gripping is at least partially provided, so that the damping element projects into at least one peripheral region of the flow path. It is particularly advantageous if the damping element completely engages around the magnet armature, so that-viewed in cross-section-the entire flow path can be acted upon by the damping element.
  • a development of the invention provides that the damping element has larger dimensions in the radial direction than the magnet armature. Accordingly, the damping element projects in the radial direction via the magnetic armature such that it projects further into the flow path than the magnet armature. In this way, the damping element can increase the damping of the solenoid valve in the first position range of the armature.
  • the magnet armature has a radial bearing for the damping element.
  • the radial bearing guides the damping element in the axial direction and prevents movement in the radial direction.
  • the radial bearing and the damping element are designed such that a tilting of the damping element is prevented with respect to the armature.
  • the invention further relates to a driver assistance device, in particular ABS, TCS or ESP device, with at least one solenoid valve, in particular according to the preceding embodiments, wherein the solenoid valve, a magnet armature, which is operatively connected to a sealing element of the solenoid valve to its displacement, and at least one Flow path, via which arranged on opposite sides of the magnet armature fluid chambers are fluid-connectable or fluid-connected has. It is provided that in the solenoid valve at least one at least partially projecting into the flow path damping element is arranged to be displaceable in the axial direction.
  • the solenoid valve of the driver assistance device can be developed further in accordance with the above explanations.
  • FIG. 1 shows a side sectional view of a solenoid valve with a magnetic armature, which is associated with a damping element
  • FIG. 3 shows the damping element in a first position
  • Figure 4 shows the damping element in a second position
  • Figure 5 is a diagram in which an attenuation of the solenoid valve is shown via a travel of the armature.
  • the figure shows a solenoid valve 1, which is for example part of a rempliassistz issued not shown here.
  • the solenoid valve 1 has a magnet armature 2, which is operatively connected to a sealing element 3 of the solenoid valve 1.
  • the seal member 3 cooperates with a valve seat 5 formed in a valve body 4 to release or interrupt a flow communication between an inlet port 6 and an outlet port 7 of the solenoid valve 1.
  • the outlet port 7 is associated with a filter 8 in the embodiment shown here. Additionally or alternatively, it is of course also possible for a filter to be assigned to the inlet connection 6 (not shown here).
  • the solenoid valve 1 shown here is designed according to the arrangement of inlet port 6 and outlet port 7 for an axial flow and a radial outflow (with respect to a longitudinal axis 9 of the solenoid valve 1). Of course, however, the direction of flow or the outflow direction can be arbitrarily provided.
  • the solenoid valve 1 has an armature counterpart 10, which forms an actuating device 1 1 of the solenoid valve 1 together with the armature 2.
  • the armature counterpart 10 is formed for example as a pole step and has at least one electric coil, so that by means of the anchor counterpart 10 by applying a voltage to the coil (ie by
  • a magnetic force can be exerted on the armature 2.
  • the armature 2 is mounted axially displaceable with respect to the longitudinal axis 9, wherein the storage is realized in particular by means of a housing 12 of the solenoid valve 1.
  • the anchor counterpart 10 and the valve body 4 are also held stationary.
  • the armature 2, influenced by the magnetic force generated by means of the armature counterpart 10, relative to the armature 2 and the valve body 4 are displaced in the axial direction.
  • the solenoid valve 1, which is shown in the figure, is a normally closed solenoid valve 1. This means that the sealing element 3 uses sealing in the valve seat 5, as long as the solenoid valve 1 is not energized, so no magnetic force by means of the armature counterpart 10 is generated.
  • the sealing element 3 On the armature counterpart 10 facing away from the side of the magnet armature 2, the sealing element 3 is introduced in a stepped bore 13. In this case, the sealing element 3 is preferably pressed into the stepped bore 13, so that it is held in this clamping.
  • a spring element 15 is arranged such that it comes into operative contact with both the magnet armature 2 and the armature counterpart 10.
  • the spring element 15, which is designed here as a spiral spring, causes a force acting on the armature 2 spring force, wherein it is supported on the armature counterpart 10. The spring force urges the magnet armature 2 in the direction away from the armature counterpart 10 direction.
  • the fluid chambers 16 and 17 are connected to one another via a flow path 18.
  • the flow path 18 is formed in the embodiment shown here between an outer contour of the magnet armature 2 and an inner contour of the housing 12.
  • the magnet armature 2 at each axial position in the radial direction smaller dimensions than an interior of the housing 12 in which the armature 2 is guided.
  • the armature 2 is shown in its closed position.
  • the solenoid valve 1 is energized, so that by means of the armature counterpart 10, a magnetic force is generated, which moves the armature 2 in the direction of the armature counterpart 10.
  • the valve seat 5 is released by the sealing element 3.
  • the solenoid valve 1 is deactivated, so that the magne- netkraft deleted and the spring force generated by the spring element 15, the armature 2 and thus the sealing element 3 in the direction of the valve seat 5 urges.
  • the path traveled by the magnet armature 2 between its open position and its closed position or vice versa is referred to below as the actuating path.
  • the positioning time is understood to mean the time required to move the armature 2 from its open position to the closed position or vice versa. Therefore occur, in particular when closing the valve seat 5 by the sealing element 3, so when moving the armature 2 in its closed position (as shown in Figure 1), pressure waves, which can cause disturbing noises. Magnetic valves 1 have therefore been proposed, which have a higher damping, so that the magnet armature 2 is displaced more slowly. The higher damping is achieved by a smaller flow cross section of the flow path 18. In this way, the solenoid valve 1 can be operated quietly. However, this measure also requires a longer positioning time of the solenoid valve. 1
  • a damping element 19 is provided, which projects into the flow path 18 between the fluid chambers 16 and 17 at least partially.
  • the damping element 19 is mounted in a groove 20 of the armature 2, wherein the groove 20 in the axial direction has a greater width than the damping element 19. In this way, the damping element 19 in the axial direction can be displaced.
  • the damping element 19 is accordingly assigned to the magnet armature 2.
  • the damping element 18 is displaceable in the axial direction along the flow path 18 by a fluid flow caused by a movement of the magnet armature 2.
  • the groove 20 forms two end stops 21 and 22 for the damping element 19. The end stops 21 and 22 limit the axial displacement of the damping element 19 with respect to the magnet armature 2.
  • FIG. 2 shows a detailed view of the magnet armature 2 and of the damping element 19. It becomes clear that the magnet armature 2 consists of two partial elements 23 and 24 exists.
  • the groove 20 is present between the sub-elements 23 and 24.
  • the sub-element 24 engages at least partially in the sub-element 23. In this way, a clamping connection between the sub-elements 23 and 24 is provided, so that the damping element 19 is held captive in the groove 20.
  • an assembly of the solenoid valve 1 is therefore initially the
  • Damping element 19 mounted on a central pin 25 of the sub-element 24 so that it preferably comes into contact with the end stop 22 or rests on this. Subsequently, the partial element 23 is pressed onto the journal 25 of the partial elements 24, so that a permanent connection between the partial elements 23 and 24 is produced. In the area of
  • Sub-element 23 the flow path 18 of radial projections 26, which emanate from the sub-elements 23 and the housing 12 oppose, divided.
  • the partial element 24 has a radial projection 27, which is circumferentially formed in the circumferential direction.
  • the radial projection 27 has a smaller radial extent than the radial projections 26 of the impact element 23.
  • the cross section of the subelement 24 decreases in the direction of the sealing element 3 via a radial step. From the figure 2 it is clear that the damping element 19, the armature
  • FIG. 3 shows a region of the magnet armature 2, the magnet armature 2 being in its open position.
  • the damping element 19 assumes, for example, the position shown in FIG. In this position, it is brought, for example, from restoring means, not shown here.
  • These return means comprise, for example, at least a spring element, which acts between the armature 2 and the damping element 19, to urge the damping element 19 in the position shown in Figure 3.
  • at least one spring element is arranged in each case on both sides of the damping element 19 in the groove 20.
  • two spring elements are provided diametrically opposite each other.
  • four or more spring elements are used.
  • the first position range contains insofar the positions of the magnet armature 2, for which the coupling element 19 rests against the end stop 21.
  • Position range contains the positions of the armature 2, in which the damping element 19 is not yet applied to the end stop 21.
  • FIG. 5 shows a diagram in which the damping k of the solenoid valve 1 is shown via the travel x of the magnet armature 2.
  • the damping is dimensionless, the travel of the armature 2 in millimeters indicated.
  • One A travel of zero means that the armature 2 is in its open position, and a travel of x g , that the armature 2 is in its closed position.
  • Das diagram of Figure 5 shows that the damping of the solenoid valve 1 in the first position range 29 is greater than in the second position range 30. It thus shows that the attenuation of the
  • Solenoid valve 1 only in a small position range - based on the total travel - is increased. In this way, a low-noise operation of the solenoid valve 1 is enabled at the same time high speed.

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

Abstract

L'invention concerne une électrovalve (1) comprenant une armature d'électro-aimant (2) qui est en liaison fonctionnelle avec un élément d'étanchéité (3) de l'électrovalve (1) pour son déplacement et au moins une voie d'écoulement (18) par laquelle des chambres à fluide (16, 17) disposées sur des côtés opposés de l'armature d'électro-aimant (2) peuvent être ou sont fluidiquement reliées. À cet effet, selon l'invention, au moins un élément amortisseur (19) faisant saillie au moins en partie dans la voie d'écoulement (18) est disposé de manière déplaçable dans la direction axiale dans l'électrovalve (1).
EP11726119.8A 2010-08-04 2011-06-10 Électrovalve et dispositif d'aide à la conduite comportant une telle électrovalve Withdrawn EP2601084A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010038900A DE102010038900A1 (de) 2010-08-04 2010-08-04 Magnetventil sowie Fahrerassistenzeinrichtung
PCT/EP2011/059715 WO2012016741A1 (fr) 2010-08-04 2011-06-10 Électrovalve et dispositif d'aide à la conduite comportant une telle électrovalve

Publications (1)

Publication Number Publication Date
EP2601084A1 true EP2601084A1 (fr) 2013-06-12

Family

ID=44310045

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11726119.8A Withdrawn EP2601084A1 (fr) 2010-08-04 2011-06-10 Électrovalve et dispositif d'aide à la conduite comportant une telle électrovalve

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US (1) US20130306891A1 (fr)
EP (1) EP2601084A1 (fr)
KR (1) KR20130095729A (fr)
CN (1) CN103052547A (fr)
DE (1) DE102010038900A1 (fr)
WO (1) WO2012016741A1 (fr)

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WO2012016741A1 (fr) 2012-02-09
US20130306891A1 (en) 2013-11-21
CN103052547A (zh) 2013-04-17
KR20130095729A (ko) 2013-08-28
DE102010038900A1 (de) 2012-02-09

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