EP0785885A1 - Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems - Google Patents

Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems

Info

Publication number
EP0785885A1
EP0785885A1 EP95934045A EP95934045A EP0785885A1 EP 0785885 A1 EP0785885 A1 EP 0785885A1 EP 95934045 A EP95934045 A EP 95934045A EP 95934045 A EP95934045 A EP 95934045A EP 0785885 A1 EP0785885 A1 EP 0785885A1
Authority
EP
European Patent Office
Prior art keywords
valve
seat
pressure
sleeve
tappet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
EP95934045A
Other languages
German (de)
French (fr)
Inventor
Martin Oehler
Günther HOHL
Hans-Peter Huebner
Norbert Mittwollen
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 EP0785885A1 publication Critical patent/EP0785885A1/en
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • 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
    • B60T8/50—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 having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5018—Pressure reapplication using restrictions
    • B60T8/5025—Pressure reapplication using restrictions in hydraulic brake systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/90—ABS throttle control
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S303/00—Fluid-pressure and analogous brake systems
    • Y10S303/901—ABS check valve detail

Definitions

  • the invention relates to a solenoid valve according to the preamble of the patent claim.
  • Such a solenoid valve is already known (DE 42 34 749 AI), which is arranged in slip-controlled brake systems of motor vehicles in a brake line between a master brake cylinder and the pressure side of a high-pressure pump conveying into the brake line, as described in the document DE 40 41 506 AI is.
  • the solenoid valve With traction control, the solenoid valve is switched to its closed position and the pressure limiting function is activated. If the pump pressure exceeds the opening pressure of the valve, its seat valve goes into the partially open position against the force of the pressure limiting spring, so that pressure medium can flow out to the master brake cylinder. Because of the pulsating pump, pressure surges occur in the downstream brake line part, which can cause disturbing noises in the motor vehicle interior. But that is particularly annoying Pressure surge that occurs when the valve is switched off from the closed position to the open position.
  • the solenoid valve according to the invention with the characterizing features of the claim has the advantage that a pressure medium flow into the gap space is caused by the shape of the valve seat, closing member and sleeve-shaped portion of the outer valve lifter part during the transition of the seat valve from the closed position to the partially open position, which creates a dynamic pressure there caused, which is transmitted through the pressure medium channel into the control chamber and exerts a force on the magnet armature, which counteracts the hydraulic opening force and thus greatly slows the opening process of the seat valve into the open position.
  • the volume flow of the pressure medium through the seat valve can only increase in a throttled manner, so that at most a very reduced pressure surge becomes effective in the downstream brake line part. This greatly improves the noise behavior of the brake system when the solenoid valve is switched off. But even with effective pressure limitation, considerable noise reduction is achieved through flow stabilization as a result of a defined flow guidance.
  • FIG. 1 shows a longitudinal section through a solenoid valve
  • FIGS. 2 and 3 flow curves in the seat valve area designated X in FIG. 1 of the valve which assumes its open position (FIG. 2) and its partially open position (FIG. 3).
  • the solenoid valve 10 with pressure limitation shown in Figure 1 is intended for use in slip-controlled brake systems of motor vehicles.
  • the solenoid valve 10 has a valve housing 11 which is intended to be received in a valve block (not shown) and which is connected to a yoke disk 12.
  • the valve housing 11 is continued beyond the yoke plate 12 with a pole core 13.
  • a closed, tubular valve dome 14 is attached to the pole core 13. This is tightly connected to the pole core 13 by welding.
  • the valve dome 14 facing away from the pole core is closed with a hemispherical cap 15.
  • the valve dome 14 is encompassed by an annular magnet coil 18.
  • a bell-shaped housing 19 engages the valve dome 14 on the one hand, and it is connected to the yoke disk 12 on the other hand.
  • valve dome 14 which is closed on the coil side, an essentially circular cylindrical magnet armature 22 is accommodated in a longitudinally movable manner.
  • a valve tappet 23 is supported on the magnet armature 22.
  • the magnet armature 22 and the valve tappet 23 are separate components which engage one another in a sealing seat 24.
  • the valve tappet 23 has a tubular, outer valve tappet part 25, in which a second, inner valve tappet part 26 is guided so as to be longitudinally movable.
  • a press-in sleeve 27 is seated in the outer valve-tappet part 25.
  • a pressure-limiting spring 28 in the form of a helical compression spring is located in the valve tappet 23 between the press-in sleeve 27 of the outer valve tappet part 25 and the inner valve tappet part 26. This engages with prestress on the one hand on the press-in sleeve 27 and on the other hand on a collar 29 of the inner valve lifter part 26, which in turn is supported on a shoulder 30 of the outer valve lifter part 25.
  • valve stem 23 is received in a through bore 33 of the valve housing 11 so as to be longitudinally movable. Polkernabge andt a valve body 34 of a seat valve 35 is pressed into the housing bore 33.
  • the valve tappet 23 is supported on the magnet armature 22 by a return spring 36 acting on the one hand on the valve body 34 and on the other hand on the outer valve tappet part 25.
  • the valve body 34, the parts 25 and 26 of the valve stem 23 and the magnet armature 22 are arranged in the longitudinal axis 37 of the solenoid valve 10.
  • the seat valve 35 is located in the region of a valve chamber 40 which has the bore 33 with a transverse bore 41 of the valve housing 11 forms.
  • the seat valve 35 has a valve seat 43 formed in the valve body 34 and enclosing a valve opening 42 in a hollow cone shape (FIGS. 2 and 3).
  • the valve seat 43 is located in a straight, circular-cylindrical recess 44 in the valve body 34.
  • the recess 44 is delimited against the valve chamber 40 by a sharp edge 45 by an end face 46 of the valve body 34 running at right angles to the longitudinal axis 37 of the valve.
  • valve chamber 40 While the valve chamber 40 is connected to a pressure medium inlet 47 through the transverse bore 41, the valve opening 42 is connected through the perforated valve body 34 to a pressure medium outlet 48 of the solenoid valve 10.
  • the pressure medium inlet 47 is connected to a master brake cylinder, the pressure medium outlet 48 with at least one wheel brake cylinder and the high pressure side of a return pump of the hydraulic brake system of the motor vehicle, not shown, for example known from DE 40 41 506 A1.
  • the seat valve 35 has a closing element 51 which interacts with the valve seat 43 and which is formed by a straight circular cylindrical section 52 of the inner valve lifter part 26 with a reduced diameter.
  • the section 52 merges into a spherical segment 54 of low height against the valve seat 43, forming a sharp edge 53.
  • the ball segment 54 assumes a position approximately in the region of the end face 46 of the valve body 34.
  • the section 52 of the inner valve lifter part 26 is encompassed by a sleeve-shaped section 57 of the outer valve lifter part 25.
  • the sleeve-shaped section 57 extends at a radial distance from the circular-cylindrical section 52, ie the inner lateral surface 58 of the sleeve-shaped section has one even distance from the circular cylindrical section.
  • a gap 59 is formed between the sleeve-shaped section 57 and the circular-cylindrical section 52, which is open towards the valve chamber 40.
  • the sleeve-shaped section 57 has an axial residue with respect to the ball segment 54.
  • the recess 44 has a diameter which is equal to or smaller than the inner diameter of the sleeve-shaped section 57, in the exemplary embodiment shown approximately between the latter and the section 52 of the inner valve lifter part 26.
  • the tangent 60 strikes the jacket wall 62 of the recess 44.
  • the sleeve-shaped section 57 has a considerably smaller axial distance from the end face 46 of the valve body 34 than in the open position.
  • a pressure medium channel 65 extending essentially in the longitudinal valve axis 37 extends from the gap space 59. Only on the inner valve tappet part 26 is the pressure medium channel 65 formed as at least one recess 66 following the circular cylindrical section 52 in the form of a longitudinal notch or groove. Following the recess 66, the pressure medium channel runs 65 in the interior of the outer valve lifter part 25 and the press-in sleeve 27 and, after the sealing seat 24, merges into a longitudinal bore 67 of the armature 22.
  • the pressure medium channel 65 opens into a control chamber 68 which is delimited on the one hand by the cap 15 and on the other hand by the end face 69 of the magnet armature 22 remote from the seat valve.
  • the control chamber 68 is sealed on the circumferential side of the armature 22 against the valve dome 14. For this purpose there is a sealing sleeve on the magnet armature
  • the armature 22 can also be sealed with a gap seal 72 against the valve dome.
  • the solenoid valve 10 has the following mode of operation:
  • the seat valve 35 When braking without slip control, the seat valve 35, which assumes its open position, is flowed through from the pressure medium inlet 47 to the pressure medium outlet 48 when pressure builds up in the wheel brake cylinders, and pressure medium flows in the opposite direction when the pressure is reduced.
  • the pressure medium takes a path through the seat valve 35 into the valve chamber 40, as is indicated by streamlines in FIG.
  • the pressure medium flowing through the valve seat 43 from the valve hope 42 is deflected approximately tangentially by the ball segment 54 of the closing element 51, the flow tearing off at the sharp edge 53 of the closing element 51.
  • the pressure medium leaves the recess 44 in the direction of the tangent 60 and partially meets the end face 61 of the sleeve-shaped section 57 of the outer valve lifter part 25. There, the pressure medium undergoes a radial deflection into the valve chamber 40, from which it flows out to the pressure medium inlet 47.
  • the collar 29 of the inner valve stem part 27 is overcome the biasing force of the pressure limiting spring 28 is raised from the shoulder 30 of the outer valve lifter part 25. While the force flow of the pressure limiting spring 28 was previously closed via the collar 29 of the inner valve tappet part 26, the outer valve tappet part 25 and the press-in sleeve 27, at the end of the armature stroke, the pressure limiting spring 28 exerts an axial force on the inner valve tappet part 26, with which this means by means of its closing member 51 engages the valve seat 43 of the valve body 34. The force of the pressure limiting spring 28 now acts as the closing force of the seat valve 35 which determines the opening pressure of the solenoid valve 10.
  • the solenoid valve 10 When the closing member 51 engages the valve seat 43, the solenoid valve 10 thus functions as a shut-off valve with a pressure-limiting effect on the part of the brake system on the side of the brake cylinder. If the opening pressure of the solenoid valve 10 is exceeded by the return pump, the pressure limiting function becomes effective. The closing member 51 lifts against the force of the pressure limiting spring 28 from the valve seat 43 and takes it A partially open position of the seat valve 35 shown in FIG. 3.
  • the streamlines take a course corresponding to the tangent 60 when penetrating the narrow gap between the valve seat 43 and the ball segment 54 and meet the casing wall 62 of the recess 44 when leaving the valve seat.
  • the streamlines experience an axial deflection so that they partly when leaving the recess 44 penetrate into the gap 59 between the closing member 51 and the sleeve-shaped section 57 and generate a dynamic pressure there, which also acts on the circumferential side on the circular cylindrical section 52 of the closing member 51.
  • This defined flow control suppresses possible instabilities of the present jet flow, so that the closing member 31 is not subjected to changing impulse forces and is therefore not excited to vibrate.
  • the dynamic pressure is also transmitted through the pressure medium channel 65 into the control chamber 68, where it causes a hydraulic force directed against the seat valve 35 on the magnet armature 22.
  • this force has no effect on the seat valve 35.
  • the pressure medium flow is directed out of the gap space 59, so that the pressure medium takes a radial path between the two end faces 46 and 61 of the valve body 34 and the sleeve-shaped section 57 in the direction of the pressure medium inlet 47.

Landscapes

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

Abstract

The invention is to provide a low-noise magnetic valve on switch-off from the pressure limitation function. The magnetic valve (10) has a two-part tappet (23), the inner component (26) of which comprises the closing member (51) of a seat valve (35). The closing member (51) is surrounded by and spaced from a sheath-like section (57) of the outer tappet component (25) forming a gap (59). From the gap, a pressure medium pipe (65) leads to a control chamber (68) between the end face, away from the seat valve, of a magnetic armature (22) co-operating with the tappet (23) and a valve dome (14). When the magnetic valve (10) is switched off, the seat valve (35) goes from its closed to a partly open position in which ram pressure in the gap (59) takes effect and is transferred through the pressure medium pipe (65) to the control chamber (68). The hydraulic force acting there on the magnetic armature (22) counteracts the opening forces of the magnetic valve (10) and slows its opening movement. A pressure surge is prevented through the thus throttled flow of the pressure medium through the seat valve (35). The magnetic valve (10) is applicable to controlled-slip motor vehicle braking systems.

Description

Magnetventil mit Druckbegrenzung für schlupfgereσelte Kraftfahrzeug-BremsanlagenSolenoid valve with pressure limitation for slip-resistant motor vehicle brake systems
Stand der TechnikState of the art
Die Erfindung geht aus von einem Magnetventil nach der Gattung des Patentanspruchs.The invention relates to a solenoid valve according to the preamble of the patent claim.
Es ist schon ein solches Magnetventil bekannt (DE 42 34 749 AI) , welches in schlupfgeregelten Bremsanlagen von Kraftfahrzeugen in einer Bremsleitung zwischen einem Hauptbremszylinder und der Druckseite einer in die Bremsleitung fördernden Hochdruckpumpe angeordnet wird, wie dies in der Druckschrift DE 40 41 506 AI beschrieben ist. Bei Antriebschlupfregelung wird das Magnetventil in seine Schließstellung geschaltet und die Druckbegrenzungsfunktion aktiviert. Wenn der Pumpendruck den Öffnungsdruck des Ventils überschreitet, geht dessen Sitzventil entgegen der Kraft der Druckbegrenzungsfeder in die Teiloffenstellung, so daß Druckmittel zum Hauptbremszylinder abströmen kann. Aufgrund der pulsierend fördernden Pumpe treten dabei Druckstδße in dem abstrδmseitigen Bremsleitungsteil auf, welche störende Geräusche im Kraftfahrzeug-Innenraum hervorrufen können. Besonders störend ist aber der Druckstoß, welcher beim Abschalten des Ventils von der Schließstellung in die Offenstellung auftritt.Such a solenoid valve is already known (DE 42 34 749 AI), which is arranged in slip-controlled brake systems of motor vehicles in a brake line between a master brake cylinder and the pressure side of a high-pressure pump conveying into the brake line, as described in the document DE 40 41 506 AI is. With traction control, the solenoid valve is switched to its closed position and the pressure limiting function is activated. If the pump pressure exceeds the opening pressure of the valve, its seat valve goes into the partially open position against the force of the pressure limiting spring, so that pressure medium can flow out to the master brake cylinder. Because of the pulsating pump, pressure surges occur in the downstream brake line part, which can cause disturbing noises in the motor vehicle interior. But that is particularly annoying Pressure surge that occurs when the valve is switched off from the closed position to the open position.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Magnetventil mit den kennzeichnenden Merkmalen des Patentanspruchs hat demgegenüber den Vorteil, daß durch die Formgebung von Ventilsitz, Schließglied und hülsenförmigem Abschnitt des äußeren Ventilstoßelteils beim Übergang des Sitzventils von der Schließstellung in die Teiloffenstellung eine Druckmittelstrδmung in den Spaltraum hervorgerufen wird, welche dort einen Staudruck verursacht, der durch den Druckmittelkanal in die Steuerkammer übertragen wird und eine Kraft auf den Magnetanker ausübt, die der hydraulischen Öffnungskraft entgegenwirkt und somit den ÖffnungsVorgang des Sitzventils in die Offenstellung stark verlangsamt. Dadurch kann sich der Volumenstrom des Druckmittels durch das Sitzventil nur gedrosselt vergrößern, so daß allenfalls ein sehr abgeschwächter Druckstoß im abströmseitigen Bremsleitungsteil wirksam wird. Damit ist das Geräuschverhalten der Bremsanlage beim Abschalten des Magnetventils sehr verbessert. Aber auch bei wirksamer Druckbegrenzung ist eine erhebliche Geräuschreduzierung durch die Strömungsstabilisierung infolge einer definierten Strömungsführung erzielt.The solenoid valve according to the invention with the characterizing features of the claim has the advantage that a pressure medium flow into the gap space is caused by the shape of the valve seat, closing member and sleeve-shaped portion of the outer valve lifter part during the transition of the seat valve from the closed position to the partially open position, which creates a dynamic pressure there caused, which is transmitted through the pressure medium channel into the control chamber and exerts a force on the magnet armature, which counteracts the hydraulic opening force and thus greatly slows the opening process of the seat valve into the open position. As a result, the volume flow of the pressure medium through the seat valve can only increase in a throttled manner, so that at most a very reduced pressure surge becomes effective in the downstream brake line part. This greatly improves the noise behavior of the brake system when the solenoid valve is switched off. But even with effective pressure limitation, considerable noise reduction is achieved through flow stabilization as a result of a defined flow guidance.
Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Patentanspruch angegebenen Magnetventils möglich.The measures listed in the subclaims allow advantageous developments and improvements of the solenoid valve specified in the claim.
Zweckmäßige Gestaltungen für den Sitzventilbereich sind in den Ansprüchen 2 bis 5 offenbart. Diese Gestaltungen sind mit geringem Fertigungsaufwand erzeugbar.Appropriate designs for the seat valve area are disclosed in claims 2 to 5. These designs can be produced with little manufacturing effort.
Mit der im Anspruch 7 angegebenen Maßnahme wird eine sichere Übertragung des Druckes in die Steuerkammer erreicht. Fertigungstechnisch bedingte Schiefstände zwischen dem Magnetanker und dem Ventilstδßel können toleriert werden, da sie nicht die Dichtheit des Druckmittelkanals beeinträchtigen.With the measure specified in claim 7, a secure transmission of the pressure is achieved in the control chamber. Production-related misalignments between the magnet armature and the valve tappet can be tolerated, since they do not impair the tightness of the pressure medium channel.
Die Weiterbildung der Erfindung nach Anspruch 8 oder 9 ist von Vorteil, weil hierdurch auf einfache Weise eine druckmäßige Trennung der Steuerkammer vom stδßelseitigen Ventildominneren geschaffen ist.The development of the invention according to claim 8 or 9 is advantageous because it creates a pressure separation of the control chamber from the ram-side valve domes in a simple manner.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 einen Längsschnitt durch ein Magnetventil, Figuren 2 und 3 Strδmungsverläufe im in Figur 1 mit X bezeichneten Sitzventilbereich des seine Offenstellung (Figur 2) und seine teiloffene Stellung (Figur 3) einnehmenden Ventils.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. FIG. 1 shows a longitudinal section through a solenoid valve, FIGS. 2 and 3 flow curves in the seat valve area designated X in FIG. 1 of the valve which assumes its open position (FIG. 2) and its partially open position (FIG. 3).
Beschreibung des AusführungsbeispielsDescription of the embodiment
Das in Figur 1 dargestellte Magnetventil 10 mit Druckbegrenzung ist zur Verwendung in schlupfgeregelten Bremsanlagen von Kraftfahrzeugen vorgesehen. Das Magnetventil 10 weist ein zur Aufnahme in einem nicht dargestellten Ventilblock bestimmtes Ventilgehäuse 11 auf, welches mit einer Jochscheibe 12 verbunden ist. Das Ventilgehäuse 11 ist über die Jochscheibe 12 hinaus mit einem Polkern 13 fortgesetzt. Auf den Polkern 13 ist ein geschlossener, rohrförmiger Ventildom 14 aufgesteckt. Dieser ist durch Schweißung mit dem Polkern 13 dicht verbunden. Polkernabgewandt ist der Ventildom 14 mit einer halbkugelförmigen Kappe 15 abgeschlossen. Der Ventildom 14 ist von einer ringförmigen Magnetspule 18 umgriffen. Ein glockenförmiges Gehäuse 19 greift einerseits am Ventildom 14 an, andererseits ist es mit der Jochscheibe 12 verbunden.The solenoid valve 10 with pressure limitation shown in Figure 1 is intended for use in slip-controlled brake systems of motor vehicles. The solenoid valve 10 has a valve housing 11 which is intended to be received in a valve block (not shown) and which is connected to a yoke disk 12. The valve housing 11 is continued beyond the yoke plate 12 with a pole core 13. A closed, tubular valve dome 14 is attached to the pole core 13. This is tightly connected to the pole core 13 by welding. The valve dome 14 facing away from the pole core is closed with a hemispherical cap 15. The valve dome 14 is encompassed by an annular magnet coil 18. A bell-shaped housing 19 engages the valve dome 14 on the one hand, and it is connected to the yoke disk 12 on the other hand.
Im spulenseitig geschlossenen Ventildom 14 ist ein im wesentlichen kreiszylindrischer Magnetanker 22 längsbewegbar aufgenommen. Am Magnetanker 22 ist ein Ventilstδßel 23 abgestützt. Der Magnetanker 22 und der Ventilstδßel 23 sind getrennte Bauteile, die in einem Dichtsitz 24 aneinander angreifen. Der Ventilstδßel 23 hat einen rohrförmigen, äußeren Ventilstδßelteil 25, in dem ein zweiter, innerer Ventilstδßelteil 26 längsbewegbar geführt ist. Magnetankerseitig sitzt im äußeren Ventilstδßelteil 25 eine Einpreßhülse 27. Im Ventilstδßel 23 befindet sich zwischen der Einpreßhülse 27 des äußeren Ventilstoßelteils 25 und dem inneren Ventilstδßelteil 26 eine Druckbegrenzungsfeder 28 in der Form einer Schraubendruckfeder. Diese greift mit Vorspannung einerseits an der Einpreßhülse 27 und andererseits an einem Bund 29 des inneren Ventilstoßelteils 26 an, der wiederum an einem Absatz 30 des äußeren Ventilstoßelteils 25 abgestützt ist.In the valve dome 14, which is closed on the coil side, an essentially circular cylindrical magnet armature 22 is accommodated in a longitudinally movable manner. A valve tappet 23 is supported on the magnet armature 22. The magnet armature 22 and the valve tappet 23 are separate components which engage one another in a sealing seat 24. The valve tappet 23 has a tubular, outer valve tappet part 25, in which a second, inner valve tappet part 26 is guided so as to be longitudinally movable. On the magnet armature side, a press-in sleeve 27 is seated in the outer valve-tappet part 25. A pressure-limiting spring 28 in the form of a helical compression spring is located in the valve tappet 23 between the press-in sleeve 27 of the outer valve tappet part 25 and the inner valve tappet part 26. This engages with prestress on the one hand on the press-in sleeve 27 and on the other hand on a collar 29 of the inner valve lifter part 26, which in turn is supported on a shoulder 30 of the outer valve lifter part 25.
Der Ventilstδßel 23 ist in einer durchgehenden Bohrung 33 des Ventilgehäuses 11 längsbewegbar aufgenommen. Polkernabge andt ist in die Gehäusebohrung 33 ein Ventilkδrper 34 eines Sitzventils 35 eingepreßt. Durch eine einerseits am Ventilkδrper 34 und andererseits am äußeren Ventilstδßelteil 25 angreifende Rückstellfeder 36 ist der Ventilstößel 23 am Magnetanker 22 abgestützt. Der Ventilkörper 34, die Teile 25 und 26 des Ventilstδßels 23 und der Magnetanker 22 sind in der Längsachse 37 des Magnetventils 10 angeordnet.The valve stem 23 is received in a through bore 33 of the valve housing 11 so as to be longitudinally movable. Polkernabge andt a valve body 34 of a seat valve 35 is pressed into the housing bore 33. The valve tappet 23 is supported on the magnet armature 22 by a return spring 36 acting on the one hand on the valve body 34 and on the other hand on the outer valve tappet part 25. The valve body 34, the parts 25 and 26 of the valve stem 23 and the magnet armature 22 are arranged in the longitudinal axis 37 of the solenoid valve 10.
Das Sitzventil 35 befindet sich im Bereich einer Ventilkammer 40, welche die Bohrung 33 mit einer Querbohrung 41 des Ventilgehäuses 11 bildet. Das Sitzventil 35 hat einen im Ventilkörper 34 geformten, eine Ventilδffnung 42 umschließenden Ventilsitz 43 in Hohlkegelform (Figuren 2 und 3) . Der Ventilsitz 43 liegt in einer geraden, kreiszylindrischen Eintiefung 44 des Ventilkδrpers 34. Die Eintiefung 44 ist gegen die Ventilkammer 40 nach einer scharfen Kante 45 durch eine rechtwinklig zur Ventillängsachse 37 verlaufende Stirnseite 46 des Ventilkδrpers 34 begrenzt. Während die Ventilkammer 40 durch die Querbohrung 41 mit einem Druckmitteleinlaß 47 in Verbindung steht, ist die Ventilöffnung 42 durch den durchbohrten Ventilkδrper 34 an einen Druckmittelauslaß 48 des Magnetventils 10 angeschlossen. Der Druckmitteleinlaß 47 steht mit einem Hauptbremszylinder, der Druckmittelauslaß 48 mit wenigstens einem Radbremszylinder sowie der Hochdruckseite einer Rückfδrderpumpe der nicht dargestellten, beispielsweise aus der Druckschrift DE 40 41 506 AI bekannten hydraulischen Bremsanlage des Kraftfahrzeugs in Verbindung.The seat valve 35 is located in the region of a valve chamber 40 which has the bore 33 with a transverse bore 41 of the valve housing 11 forms. The seat valve 35 has a valve seat 43 formed in the valve body 34 and enclosing a valve opening 42 in a hollow cone shape (FIGS. 2 and 3). The valve seat 43 is located in a straight, circular-cylindrical recess 44 in the valve body 34. The recess 44 is delimited against the valve chamber 40 by a sharp edge 45 by an end face 46 of the valve body 34 running at right angles to the longitudinal axis 37 of the valve. While the valve chamber 40 is connected to a pressure medium inlet 47 through the transverse bore 41, the valve opening 42 is connected through the perforated valve body 34 to a pressure medium outlet 48 of the solenoid valve 10. The pressure medium inlet 47 is connected to a master brake cylinder, the pressure medium outlet 48 with at least one wheel brake cylinder and the high pressure side of a return pump of the hydraulic brake system of the motor vehicle, not shown, for example known from DE 40 41 506 A1.
Das Sitzventil 35 hat ein mit dem Ventilsitz 43 zusammenwirkendes Schließglied 51, welches von einem im Durchmesser abgesetzten, geraden kreiszylindrischen Abschnitt 52 des inneren Ventilstoßelteils 26 gebildet ist. Gegen den Ventilsitz 43 geht der Abschnitt 52 unter Bildung einer scharfen Kante 53 in ein Kugelsegment 54 geringer Höhe über. In der in Figur 2 dargestellten Offenstellung des Sitzventils 35 nimmt das Kugelsegment 54 eine Position etwa im Bereich der Stirnseite 46 des Ventilkδrpers 34 ein.The seat valve 35 has a closing element 51 which interacts with the valve seat 43 and which is formed by a straight circular cylindrical section 52 of the inner valve lifter part 26 with a reduced diameter. The section 52 merges into a spherical segment 54 of low height against the valve seat 43, forming a sharp edge 53. In the open position of the seat valve 35 shown in FIG. 2, the ball segment 54 assumes a position approximately in the region of the end face 46 of the valve body 34.
Der Abschnitt 52 des inneren Ventilstoßelteils 26 ist von einem hülsenfδrmigen Abschnitt 57 des äußeren Ventilstoßelteils 25 umgriffen. Der hülsenförmige Abschnitt 57 erstreckt sich mit radialem Abstand zum kreiszylindrischen Abschnitt 52, d. h. die innere Mantelfläche 58 des hülsenförmigen Abschnitts weist einen gleichmäßigen Abstand zum kreiszylindrischen Abschnitt auf. Hierdurch ist zwischen dem hülsenfδrmigen Abschnitt 57 und dem kreiszylindrischen Abschnitt 52 ein Spaltraum 59 gebildet, welcher gegen die Ventilkammer 40 offen ist. Außerdem weist der hülsenförmige Abschnitt 57 einen axialen Rückstand gegenüber dem Kugelsegment 54 auf. Dieser ist derart bemessen, daß eine im Randbereich des Kugelsegments 54 angelegte, die Längsachse 37 des Ventils 10 unter einem Winkel von ca. 45° schneidende Tangente 60 auf die rechtwinklig zur Ventillängsachse 37 verlaufende Stirnseite 61 des hülsenfδrmigen Abschnitts 57 trifft, wie dies in den Figuren 2 und 3 dargestellt ist. Abweichend hiervon kann der axiale Rückstand oder der Außendurchmesser des hülsenfδrmigenn Abschnitts 57 derart bemessen sein, daß die Tangente 60 außerhalb des Abschnitts an der Stirnseite 61 vorbeiläuft. Wie Figur 2 außerdem erkennen läßt, läuft in der Offenstellung des Sitzventils 35 die Tangente 60 an der stirnseitigen Kante 45 der Eintiefung 44 im Ventilkörper 34 vorbei. Die Eintiefung 44 hat einen Durchmesser, der gleich oder kleiner als der Innendurchmesser des hülsenförmigen Abschnitts 57 ist, beim dargestellten Ausführungsbeispiel etwa mittig zwischen diesem und dem Abschnitt 52 des inneren Ventilstoßelteils 26 liegt. In der in Figur 3 dargestellten Teiloffenstellung des Sitzventils 35 trifft die Tangente 60 dagegen auf die Mantelwand 62 der Eintiefung 44. In der Teiloffenstellung nimmt der hülsenförmige Abschnitt 57 einen erheblich geringeren axialen Abstand zur Stirnseite 46 des Ventilkδrpers 34 ein als in der Offenstellung.The section 52 of the inner valve lifter part 26 is encompassed by a sleeve-shaped section 57 of the outer valve lifter part 25. The sleeve-shaped section 57 extends at a radial distance from the circular-cylindrical section 52, ie the inner lateral surface 58 of the sleeve-shaped section has one even distance from the circular cylindrical section. As a result, a gap 59 is formed between the sleeve-shaped section 57 and the circular-cylindrical section 52, which is open towards the valve chamber 40. In addition, the sleeve-shaped section 57 has an axial residue with respect to the ball segment 54. This is dimensioned such that a tangent 60 which is applied in the edge region of the spherical segment 54 and which intersects the longitudinal axis 37 of the valve 10 at an angle of approximately 45 ° meets the end face 61 of the sleeve-shaped section 57 which extends at right angles to the longitudinal axis 37 of the valve, as shown in FIGS Figures 2 and 3 is shown. Deviating from this, the axial residue or the outer diameter of the sleeve-shaped section 57 can be dimensioned such that the tangent 60 runs past the end face 61 outside the section. As can also be seen in FIG. 2, in the open position of the seat valve 35, the tangent 60 runs past the end edge 45 of the recess 44 in the valve body 34. The recess 44 has a diameter which is equal to or smaller than the inner diameter of the sleeve-shaped section 57, in the exemplary embodiment shown approximately between the latter and the section 52 of the inner valve lifter part 26. In contrast, in the partially open position of the seat valve 35 shown in FIG. 3, the tangent 60 strikes the jacket wall 62 of the recess 44. In the partially open position, the sleeve-shaped section 57 has a considerably smaller axial distance from the end face 46 of the valve body 34 than in the open position.
Vom Spaltraum 59 geht ein im wesentlichen in der Ventillängsachse 37 verlaufender Druckmittelkanal 65 aus. Lediglich am inneren Ventilstδßelteil 26 ist der Druckmittelkanal 65 als wenigstens eine auf den kreiszylindrischen Abschnitt 52 folgende Ausnehmung 66 in der Form einer längslaufenden Kerbe oder Nut ausgebildet. Auf die Ausnehmung 66 folgend verläuft der Druckmittelkanal 65 im Innenraum des äußeren Ventilstoßelteils 25 sowie der Einpreßhülse 27 und geht nach dem Dichtsitz 24 in eine Längsbohrung 67 des Magnetankers 22 über. In der Kappe 15 des Ventildomes 14 mündet der Druckmittelkanal 65 in eine Steuerkammer 68, welche einerseits durch die Kappe 15 und andererseits durch die sitzventilferne Stirnseite 69 des Magnetankers 22 begrenzt ist. Die Steuerkammer 68 ist umfangsseitig des Magnetankers 22 gegen den Ventildom 14 abgedichtet. Hierzu ist am Magnetanker eine DichtmanschetteA pressure medium channel 65 extending essentially in the longitudinal valve axis 37 extends from the gap space 59. Only on the inner valve tappet part 26 is the pressure medium channel 65 formed as at least one recess 66 following the circular cylindrical section 52 in the form of a longitudinal notch or groove. Following the recess 66, the pressure medium channel runs 65 in the interior of the outer valve lifter part 25 and the press-in sleeve 27 and, after the sealing seat 24, merges into a longitudinal bore 67 of the armature 22. In the cap 15 of the valve dome 14, the pressure medium channel 65 opens into a control chamber 68 which is delimited on the one hand by the cap 15 and on the other hand by the end face 69 of the magnet armature 22 remote from the seat valve. The control chamber 68 is sealed on the circumferential side of the armature 22 against the valve dome 14. For this purpose there is a sealing sleeve on the magnet armature
70 aufgenommen, deren am Ventildom 14 angreifende Dichtlippe70 added, the sealing lip acting on the valve dome 14
71 gegen die Steuerkammer 68 gerichtet ist. Anstelle der Dichtmanschette 70 kann der Magnetanker 22 auch mit einer Spaltdichtung 72 gegen den Ventildom abgedichtet sein.71 is directed against the control chamber 68. Instead of the sealing sleeve 70, the armature 22 can also be sealed with a gap seal 72 against the valve dome.
Das Magnetventil 10 hat folgende Wirkungsweise:The solenoid valve 10 has the following mode of operation:
Bei einer Bremsung ohne Schlupfregelung wird das seine Offenstellung einnehmende Sitzventil 35 bei Druckaufbau in den RadbremsZylindern vom Druckmitteleinlaß 47 zum Druckmittelauslaß 48, bei Druckabbau in umgekehrter Richtung vom Druckmittel durchströmt.When braking without slip control, the seat valve 35, which assumes its open position, is flowed through from the pressure medium inlet 47 to the pressure medium outlet 48 when pressure builds up in the wheel brake cylinders, and pressure medium flows in the opposite direction when the pressure is reduced.
Bei Bremsdruckabbau nimmt das Druckmittel einen Weg durch das Sitzventil 35 in die Ventilkammer 40, wie dies in Figur 2 durch Stromlinien angedeutet ist. Das von der VentHoffnung 42 her den Ventilsitz 43 durchströmende Druckmittel wird vom Kugelsegment 54 des Schließglieds 51 etwa tangential umgelenkt, wobei die Strömung an der scharfen Kante 53 des Schließgliedes 51 abreißt. Das Druckmittel verläßt die Eintiefung 44 in Richtung der Tangente 60 und trifft teilweise auf die Stirnseite 61 des hülsenfδrmigen Abschnitts 57 des äußeren Ventilstoßelteils 25. Dort erfährt das Druckmittel eine radiale Ablenkung in die Ventilkammer 40, aus der es zum Druckmitteleinlaß 47 abströmt. Bei einer der Antriebschlupfregelung dienenden Bremsung wird durch Bestromen der Magnetspule 18 ein Magnetfeld erzeugt, welches eine Kraft auf den Magnetanker 22 ausübt und diesen in Richtung auf den Ventilkδrper 34 verschiebt. Der am Magnetanker 22 abgestützte Ventilstδßel 23 wird entgegen der Kraft der Rückstellfeder 36 mitbewegt. Im Verlauf der Bewegung des Magnetankers 22 trifft das Schließglied 51 des inneren Ventilstoßelteils 26 auf den Ventilsitz 43 des Ventilkδrpers 34. Hierdurch wird die Bewegung des inneren Ventilstoßelteils 26 beendet. Das Sitzventil 35 nimmt seine Schließstellung ein. Da der Magnetanker 22 noch nicht seinen vollen Hub ausgeführt hat (die Hübe des Sitzventils 35 und des Magnetankers 22 sind in Figur 1 der Zeichnung unmaßstäblich wiedergegeben) und sich daher weiter gegen den Ventilkδrper 34 bewegt, wird der Bund 29 des inneren Ventilstoßelteils 27 unter Überwindung der Vorspannkraf der Druckbegrenzungsfeder 28 von dem Absatz 30 des äußeren Ventilstoßelteils 25 abgehoben. Während bisher der Kraftfluß der Druckbegrenzungsfeder 28 über den Bund 29 des inneren Ventilstoßelteils 26, den äußeren Ventilstößelteil 25 sowie die Einpreßhülse 27 geschlossen war, übt am Ende des Ankerhubes die Druckbegrenzungsfeder 28 eine Axialkraft auf den inneren Ventilstδßelteil 26 aus, mit der dieser mittels seines Schließgliedes 51 am Ventilsitz 43 des Ventilkδrpers 34 angreift. Die Kraft der Druckbegrenzungsfeder 28 wirkt jetzt als den Öffnungsdruck des Magnetventils 10 bestimmende Schließkraft des Sitzventils 35.When the brake pressure is reduced, the pressure medium takes a path through the seat valve 35 into the valve chamber 40, as is indicated by streamlines in FIG. The pressure medium flowing through the valve seat 43 from the valve hope 42 is deflected approximately tangentially by the ball segment 54 of the closing element 51, the flow tearing off at the sharp edge 53 of the closing element 51. The pressure medium leaves the recess 44 in the direction of the tangent 60 and partially meets the end face 61 of the sleeve-shaped section 57 of the outer valve lifter part 25. There, the pressure medium undergoes a radial deflection into the valve chamber 40, from which it flows out to the pressure medium inlet 47. In the case of braking which serves to control the traction slip, energizing the magnet coil 18 generates a magnetic field which exerts a force on the magnet armature 22 and displaces it in the direction of the valve body 34. The valve tappet 23 supported on the armature 22 is also moved against the force of the return spring 36. In the course of the movement of the magnet armature 22, the closing member 51 of the inner valve lifter part 26 hits the valve seat 43 of the valve body 34. The movement of the inner valve lifter part 26 is hereby terminated. The seat valve 35 assumes its closed position. Since the armature 22 has not yet reached its full stroke (the strokes of the seat valve 35 and the armature 22 are shown to scale in FIG. 1 of the drawing) and therefore continues to move against the valve body 34, the collar 29 of the inner valve stem part 27 is overcome the biasing force of the pressure limiting spring 28 is raised from the shoulder 30 of the outer valve lifter part 25. While the force flow of the pressure limiting spring 28 was previously closed via the collar 29 of the inner valve tappet part 26, the outer valve tappet part 25 and the press-in sleeve 27, at the end of the armature stroke, the pressure limiting spring 28 exerts an axial force on the inner valve tappet part 26, with which this means by means of its closing member 51 engages the valve seat 43 of the valve body 34. The force of the pressure limiting spring 28 now acts as the closing force of the seat valve 35 which determines the opening pressure of the solenoid valve 10.
Bei am Ventilsitz 43 angreifendem Schließglied 51 übt das Magnetventil 10 somit die Funktion eines Absperrventils mit druckbegrenzender Wirkung seitens des radbremszylinderseitigen Teils der Bremsanlage aus. Wird von der Rückfδrderpumpe der Öffnungsdruck des Magnetventils 10 überschritten, so wird die Druckbegrenzungsfunktion wirksam. Das Schließglied 51 hebt entgegen der Kraft der Druckbegrenzungsfeder 28 vom Ventilsitz 43 ab und nimmt die in Figur 3 dargestellte Teiloffenstellung des Sitzventils 35 ein.When the closing member 51 engages the valve seat 43, the solenoid valve 10 thus functions as a shut-off valve with a pressure-limiting effect on the part of the brake system on the side of the brake cylinder. If the opening pressure of the solenoid valve 10 is exceeded by the return pump, the pressure limiting function becomes effective. The closing member 51 lifts against the force of the pressure limiting spring 28 from the valve seat 43 and takes it A partially open position of the seat valve 35 shown in FIG. 3.
In dieser Stellung nehmen die Stromlinien beim Durchdringen des engen Spaltes zwischen dem Ventilsitz 43 und dem Kugelsegment 54 einen Verlauf entsprechend der Tangente 60 und treffen beim Verlassen des Ventilsitzes auf die Mantelwand 62 der Eintiefung 44. Hier erfahren die Stromlinien eine axiale Ablenkung, so daß sie zum Teil beim Verlassen der Eintiefung 44 bis in den Spaltraum 59 zwischen dem Schließglied 51 und dem hülsenfδrmigen Abschnitt 57 eindringen und dort einen Staudruck erzeugen, der auch umfangsseitig auf den kreiszylindrischen Abschnitt 52 des Schließgliedes 51 wirkt. Diese definierte Strömungsführung unterdrückt mögliche Instabilitäten der vorliegenden StrahlStrömung, so daß das Schließglied 31 nicht mit wechselnden Impulskräften beaufschlagt und daher nicht zu Schwingungen angeregt wird. Der Staudruck wird ferner durch den Druckmittelkanal 65 in die Steuerkammer 68 übertragen, wo er eine gegen das Sitzventil 35 gerichtete hydraulische Kraft auf den Magnetanker 22 hervorruft. Da der Magnetanker 22 jedoch am Polkern 13 abgestützt ist, übt diese Kraft keine Wirkung auf das Sitzventil 35 aus. Durch den Staudruck wird die Druckmittelstrδmung aus dem Spaltraum 59 herausgelenkt, so daß das Druckmittel einen radialen Weg zwischen den beiden Stirnseiten 46 und 61 von Ventilkδrper 34 und hülsenförmigem Abschnitt 57 in Richtung auf den Druckmitteleinlaß 47 nimmt.In this position, the streamlines take a course corresponding to the tangent 60 when penetrating the narrow gap between the valve seat 43 and the ball segment 54 and meet the casing wall 62 of the recess 44 when leaving the valve seat. Here the streamlines experience an axial deflection so that they partly when leaving the recess 44 penetrate into the gap 59 between the closing member 51 and the sleeve-shaped section 57 and generate a dynamic pressure there, which also acts on the circumferential side on the circular cylindrical section 52 of the closing member 51. This defined flow control suppresses possible instabilities of the present jet flow, so that the closing member 31 is not subjected to changing impulse forces and is therefore not excited to vibrate. The dynamic pressure is also transmitted through the pressure medium channel 65 into the control chamber 68, where it causes a hydraulic force directed against the seat valve 35 on the magnet armature 22. However, since the magnet armature 22 is supported on the pole core 13, this force has no effect on the seat valve 35. Due to the dynamic pressure, the pressure medium flow is directed out of the gap space 59, so that the pressure medium takes a radial path between the two end faces 46 and 61 of the valve body 34 and the sleeve-shaped section 57 in the direction of the pressure medium inlet 47.
Beim Beenden der Bestromung der Magnetspule 18 bricht das Magnetfeld zusammen, und der Magnetanker 22 wird durch die Wirkung der Druckbegrenzungsfeder 28 sowie der Rückstellfeder 36 zusammen mit dem Ventilstδßel 23 in Richtung auf die Kappe 15 des Ventildoms 14 bewegt. Bei sich öffnendem Sitzventil 35 durchströmt Druckmittel den Ventilsitz 43 entsprechend der Darstellung nach Figur 3 und erzeugt im Spaltraum 59 einen Staudruck, der sich durch den Druckmittelkanal 65 in die Steuerkammer 68 überträgt. Die dort hervorgerufene hydraulische Kraft wirkt auf den Magnetanker 22 entgegen dessen Bewegungsrichtung und kompensiert teilweise die auf den Ventilstδßel 23 wirkenden Öffnungskräfte. Dies hat eine verlangsamte Öffnungsbewegung des Magnetventils 10 zur Folge, zumindest solange sich das Sitzventil 35 in der Teiloffenstellung befindet. Da in der Teiloffenstellung das Druckmittel das Sitzventil 35 nur gedrosselt durchströmen kann, ist abstrδmseitig das Auftreten eines Druckstoßes weitgehend vermieden. Mit zunehmendem Ventilhub wird die Wirkung des Staudrucks vermindert, so daß das Sitzventil 35 seine Offenstellung einnehmen kann, in welcher der Durchfluß des Druckmittels weitgehend ungedrosselt entsprechend der Darstellung in Figur 2 erfolgt. When the energization of the magnet coil 18 ends, the magnetic field collapses, and the magnet armature 22 is moved in the direction of the cap 15 of the valve dome 14 by the action of the pressure limiting spring 28 and the return spring 36 together with the valve tappet 23. When the seat valve 35 opens, pressure medium flows through the valve seat 43 as shown in FIGS generates a dynamic pressure in the gap 59, which is transmitted through the pressure medium channel 65 into the control chamber 68. The hydraulic force generated there acts on the armature 22 against its direction of movement and partially compensates for the opening forces acting on the valve tappet 23. This results in a slower opening movement of the solenoid valve 10, at least as long as the seat valve 35 is in the partially open position. Since in the partially open position the pressure medium can only flow through the seat valve 35 in a throttled manner, the occurrence of a pressure surge is largely avoided on the downstream side. With increasing valve lift, the effect of the dynamic pressure is reduced so that the seat valve 35 can assume its open position, in which the flow of the pressure medium takes place largely unthrottled, as shown in FIG. 2.

Claims

Ansprüche Expectations
1. Magnetventil (10) mit Druckbegrenzung für schlupfgeregelte Kraftfahrzeug-Bremsanlagen, mit den folgenden Merkmalen:1. Solenoid valve (10) with pressure limitation for slip-controlled motor vehicle brake systems, with the following features:
- in einem Ventildom (14) ist ein Magnetanker (22) längsbewegbar aufgenommen,a magnet armature (22) is accommodated in a longitudinally movable manner in a valve dome (14),
- der Ventildom (14) ist von einer Magnetspule (18) umgriffen,- The valve dome (14) is encompassed by a magnetic coil (18),
- dem Magnetanker (22) ist ein Ventilstδßel (23) zugeordnet,- The solenoid armature (22) is assigned a valve tappet (23),
- es ist ein Sitzventil (35) mit einem eine Ventilδffnung (42) umschließenden Ventilsitz (43) in einem Ventilkδrper (34) und einem mit diesem zusammenwirkenden Schließglied (51) vorgesehen,a seat valve (35) with a valve seat (43) enclosing a valve opening (42) is provided in a valve body (34) and a closing member (51) cooperating with the latter,
- das Sitzventil (35) weist Kegel-Kugel-Konfiguration auf, wobei der Ventilsitz (43) kegelförmig und das Schließglied (51) stirnseitig kugelförmig ausgebildet sind,the seat valve (35) has a cone-and-ball configuration, the valve seat (43) being conical and the closing member (51) being spherical at the end face,
- das Schließglied (51) ist am inneren Teil (26) des aus zwei koaxial ineinandergreifenden Teilen (25, 26) gebildeten Ventilstößels (23) angeordnet,the closing member (51) is arranged on the inner part (26) of the valve tappet (23) formed from two coaxially interlocking parts (25, 26),
- der Ventilstδßel (23) ist durch Magnetkraft in die Schließstellung und durch die Kraft einer Rückstellfeder (36) in die Offenstellung des Sitzventils (35) axial bewegbar,- The valve stem (23) is by magnetic force in the closed position and by the force of a return spring (36) axially movable into the open position of the seat valve (35),
- zwischen dem inneren Teil (26) und dem äußeren Teil (25) des Ventilstδßels (23) ist eine sich axial an diesen abstützende Druckbegrenzungsfeder (28) angeordnet, gegen deren Kraft der innere Ventilstδßelteil (26) aus der Schließstellung in eine Teiloffenstellung des Sitzventils (35) relativ zum äußeren Ventilstδßelteil (25) axial verschiebbar ist, gekennzeichnet durch die weiteren Merkmale:- Between the inner part (26) and the outer part (25) of the valve tappet (23) an axially supported on this pressure limiting spring (28) is arranged, against the force of the inner valve tappet part (26) from the closed position to a partially open position of the seat valve (35) is axially displaceable relative to the outer valve tappet part (25), characterized by the further features:
- der Ventilsitz (43) liegt in einer wenigstens annähernd geraden, kreisförmigen Eintiefung (44) des Ventilkörpers (34) , die stδßelseitig scharfkantig durch eine wenigstens annähernd radial verlaufende Stirnseite (46) des Ventilkδrpers begrenzt ist,- The valve seat (43) lies in an at least approximately straight, circular recess (44) in the valve body (34), which is sharply delimited on the ram side by an at least approximately radially extending end face (46) of the valve body,
- das Schließglied (51) geht nach einem stirnseitigen Kugelsegment (54) unter Bildung einer scharfen Kante (53) in einen geraden kreiszylindrischen Abschnitt (52) des inneren Ventilstoßelteils (26) über,- The closing member (51) merges into a straight circular cylindrical section (52) of the inner valve stem part (26) after an end spherical segment (54), forming a sharp edge (53),
- der Abschnitt (52) des inneren Ventilstoßelteils (26) ist von einem hülsenfδrmigen Abschnitt (57) des äußeren Ventilstoßelteils (25) unter Bildung eines Spaltraumes (59) mit radialem Abstand sowie mit axialem Rückstand gegenüber dem Kugelsegment (54) umgriffen,- The section (52) of the inner valve lifter part (26) is encompassed by a sleeve-shaped section (57) of the outer valve lifter part (25) to form a gap space (59) with a radial distance and with an axial residue relative to the ball segment (54),
- der axiale Rückstand des hülsenfδrmigen Abschnitts (57) ist derart bemessen, daß eine im Randbereich des Kugelsegments (54) angelegte, die Längsachse (37) des Ventils schneidende Tangente (60) auf die Stirnseite (61) des hülsenfδrmigen Abschnitts (57) trifft oder außerhalb dieses Abschnitts an der Stirnseite vorbeiläuft,- The axial residue of the sleeve-shaped section (57) is dimensioned such that a tangent (60), which cuts in the edge region of the ball segment (54) and intersects the longitudinal axis (37) of the valve, meets the end face (61) of the sleeve-shaped section (57) or runs past the end of this section,
- in der Offenstellung des Sitzventils (35) liegt das Kugelsegment (54) des Schließgliedes (51) wenigstens annähernd im Bereich der Ventilkörperstirnseite (46) , so daß die Tangente (60) an der stirnseitigen Kante (45) der Eintiefung (44) des Ventilkörpers (34) vorbeiläuft, - in der Teiloffenstellung des Sitzventils (35) , in der das Schließglied (51) entgegen der Kraft der Druckbegrenzungsfeder (28) vom Ventilsitz (43) abgehoben ist, trifft die Tangente (60) auf die Mantelwand (62) der Eintiefung (44) ,- In the open position of the seat valve (35), the ball segment (54) of the closing member (51) is at least approximately in the region of the valve body end face (46), so that the tangent (60) on the front edge (45) of the recess (44) of the Valve body (34) passes by, - In the partially open position of the seat valve (35), in which the closing member (51) is raised against the force of the pressure-limiting spring (28) from the valve seat (43), the tangent (60) hits the jacket wall (62) of the recess (44) ,
- von dem Spaltraum (59) geht ein Druckmittelkanal (65) zu einer Steuerkammer (68) aus, die zwischen der sitzventilfernen Stirnseite (69) des Magnetankers (22) und dem Ventildom (14) gelegen ist,a pressure medium channel (65) extends from the gap space (59) to a control chamber (68) which is located between the end face (69) of the magnet armature (22) remote from the seat valve and the valve dome (14),
- die Steuerkammer (68) ist umfangsseitig des Magnetankers (22) abgedichtet.- The control chamber (68) is sealed on the circumferential side of the armature (22).
2. Magnetventil nach Anspruch 1, dadurch gekennzeichnet, daß die Tangente (60) einen Winkel zwischen 30° und 60°, vorzugsweise 45°, zur Ventillängsachse (37) einschließt.2. Solenoid valve according to claim 1, characterized in that the tangent (60) includes an angle between 30 ° and 60 °, preferably 45 °, to the valve longitudinal axis (37).
3. Magnetventil nach Anspruch 1, dadurch gekennzeichnet, daß die Eintiefung (44) des Ventilkδrpers (34) einen Durchmesser hat, der gleich oder kleiner ist als der Innendurchmesser des hülsenfδrmigen Abschnitts (57) des äußeren Ventilstoßelteils (25) .3. Solenoid valve according to claim 1, characterized in that the recess (44) of the Ventilkδrpers (34) has a diameter which is equal to or smaller than the inner diameter of the sleeve-shaped portion (57) of the outer valve lifter part (25).
4. Magnetventil nach Anspruch 3, dadurch gekennzeichnet, daß der Durchmesser der Eintief ng (44) wenigstens annähernd mittig zwischen dem Durchmesser des Abschnitts (52) des inneren Ventilstoßelteils (26) und dem Innendurchmesser des hülsenfδrmigen Abschnitts (57) des äußeren Ventilstoßelteils (25) liegt.4. Solenoid valve according to claim 3, characterized in that the diameter of the recess (44) at least approximately centrally between the diameter of the section (52) of the inner valve lifter part (26) and the inner diameter of the sleeve-shaped section (57) of the outer valve lifter part (25 ) lies.
5. Magnetventil nach Anspruch 1, dadurch gekennzeichnet, daß die Eintiefung (44) des Ventilkδrpers (34) , der Abschnitt (52) des inneren Ventilstoßelteils (26) und die innere5. Solenoid valve according to claim 1, characterized in that the recess (44) of the Ventilkδrpers (34), the section (52) of the inner valve lifter part (26) and the inner
Mantelfläche (58) des hülsenförmigen Abschnitts (57) des äußeren Ventilstoßelteils (25) achsparallel begrenzt sind, während die Stirnseiten (46, 61) des Ventilkδrpers (34) und des hülsenfδrmigen Abschnitts (57) in rechtwinklig zur Ventillängsachse (37) verlaufenden Ebenen liegen.The lateral surface (58) of the sleeve-shaped section (57) of the outer valve lifter part (25) is axially parallel, while the end faces (46, 61) of the valve body (34) and of the sleeve-shaped section (57) lie in planes running at right angles to the longitudinal valve axis (37).
6. Magnetventil nach Anspruch 1, dadurch gekennzeichnet, daß der Druckmittelkanal (65) von einer Längsbohrung (67) des Magnetankers (22) , von dem Innenraum des äußeren Ventilstoßelteils (25) und einer Ausnehmung (66) des inneren Ventilstoßelteils (26) gebildet ist.6. Solenoid valve according to claim 1, characterized in that the pressure medium channel (65) from a longitudinal bore (67) of the magnet armature (22), from the interior of the outer valve lifter part (25) and a recess (66) of the inner valve lifter part (26) is formed is.
7. Magnetventil nach Anspruch 6, dadurch gekennzeichnet, daß der Magnetanker (22) und der Ventilstδßel (23) als getrennte Bauteile ausgebildet sind, die unter der Wirkung der Rückstellfeder (36) in einem den Druckmittelkanal (65) umfassenden Dichtsitz (24) aneinander angreifen.7. Solenoid valve according to claim 6, characterized in that the magnet armature (22) and the Ventilstδßel (23) are designed as separate components which under the action of the return spring (36) in a pressure medium channel (65) comprising sealing seat (24) to each other attack.
8. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Magnetanker (22) eine Dichtmanschette (70) trägt, deren am Ventildom (14) angreifende Dichtlippe (71) gegen die Steuerkammer (68) gerichtet ist.8. Valve according to claim 1, characterized in that the magnet armature (22) carries a sealing collar (70), the sealing lip (71) acting on the valve dome (14) is directed against the control chamber (68).
9. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß der Magnetanker (22) durch eine Spaltdichtung (72) gegen den Ventildom (14) abgedichtet ist. 9. Valve according to claim 1, characterized in that the magnet armature (22) is sealed by a gap seal (72) against the valve dome (14).
EP95934045A 1994-10-27 1995-10-10 Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems Ceased EP0785885A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4438336 1994-10-27
DE4438336A DE4438336A1 (en) 1994-10-27 1994-10-27 Solenoid valve with pressure limitation for slip-controlled motor vehicle braking systems
PCT/DE1995/001386 WO1996013414A1 (en) 1994-10-27 1995-10-10 Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems

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EP0785885A1 true EP0785885A1 (en) 1997-07-30

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EP95934045A Ceased EP0785885A1 (en) 1994-10-27 1995-10-10 Magnetic valve with pressure limitation for controlled-slip motor vehicle braking systems

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US (1) US6086164A (en)
EP (1) EP0785885A1 (en)
JP (1) JPH10507813A (en)
KR (1) KR970706997A (en)
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WO (1) WO1996013414A1 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19805404A1 (en) * 1998-02-11 1999-08-12 Itt Mfg Enterprises Inc Pressure control valve
DE19815778A1 (en) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Shut-off valve with pressure limiting function, in particular for slip-controlled hydraulic brake systems in motor vehicles
US6412884B1 (en) * 1998-09-30 2002-07-02 Tokico Ltd. Solenoid-controlled valve
DE19956821A1 (en) * 1998-11-30 2000-05-31 Denso Corp Electromagnetic valve for controlling motor vehicle brake hydraulic pressure has three states; fully open, with both connecting paths open; half open, with choked path open; fully closed
JP2000309259A (en) * 1999-04-26 2000-11-07 Nisshinbo Ind Inc Solenoid valve device
US6431207B1 (en) * 2000-03-16 2002-08-13 Ross Operating Valve Company High-pressure ball-poppet control valve
DE60037967T2 (en) * 2000-07-01 2009-03-26 Robert Bosch Gmbh Method and apparatus for calculating the control of a hydraulic FDR / ESP subassembly to reduce hydraulic noise
US6634722B1 (en) * 2001-07-31 2003-10-21 Kelsey-Hayes Company Vehicle braking system with proportional poppet valve pressure control strategy
DE10253769B4 (en) * 2002-11-19 2014-05-15 Robert Bosch Gmbh Electromagnetically actuated valve, in particular for hydraulic brake systems of motor vehicles
KR100721363B1 (en) * 2003-01-13 2007-05-23 주식회사 만도 Traction Control Valve with Integrated Relief Function
KR100721383B1 (en) * 2003-01-13 2007-05-23 주식회사 만도 Traction Control Valve with Integrated Relief Function
DE10321413B4 (en) * 2003-05-13 2014-06-26 Robert Bosch Gmbh Electromagnetically actuated valve
JP4010982B2 (en) * 2003-06-03 2007-11-21 日信工業株式会社 solenoid valve
DE102004001565A1 (en) * 2004-01-10 2005-08-04 Robert Bosch Gmbh Electromagnetic valve, in particular for a brake system of a motor vehicle
DE102005022693A1 (en) 2005-05-18 2006-11-23 Hydac Fluidtechnik Gmbh Valve, in particular proportional pressure relief valve
KR20060132379A (en) * 2005-06-18 2006-12-21 주식회사 만도 Anti-lock brake system
DE102005057674B4 (en) * 2005-12-01 2008-05-08 Alstom Technology Ltd. waste heat boiler
DE102007032950A1 (en) * 2007-07-14 2009-01-15 Continental Teves Ag & Co. Ohg Method for measuring the admission pressure on an analogized, electromagnetically controlled hydraulic valve
DE102008014192B4 (en) * 2008-03-14 2014-04-10 Hilite Germany Gmbh Powertrain with a vehicle dynamics system and electrohydraulic valve
CN102741600B (en) 2010-02-03 2016-03-16 凯尔西-海耶斯公司 Solenoid valve
DE102010002602A1 (en) * 2010-03-05 2011-09-08 Robert Bosch Gmbh Solenoid valve for controlling a fluid
DE102014101437A1 (en) 2014-02-05 2015-08-06 Eto Magnetic Gmbh Solenoid valve and internal combustion engine cooling system with solenoid valve
DE102014225323A1 (en) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Shift or pressure control valve for a fuel injection system

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2262247A1 (en) * 1972-12-20 1974-06-27 Teves Gmbh Alfred ELECTROMAGNETIC VALVE
DE2442372A1 (en) * 1974-09-04 1976-03-18 Bosch Gmbh Robert ELECTROMAGNETIC 3-WAY VALVE ARRANGEMENT
DE3529134A1 (en) * 1985-08-14 1987-02-26 Teves Gmbh Alfred Solenoid valve
DE3725810A1 (en) * 1987-08-04 1989-02-16 Bosch Gmbh Robert SOLENOID VALVE WITH SWITCHABLE FLOW RATES
DE3802648A1 (en) * 1988-01-29 1989-08-10 Mainz Gmbh Feinmech Werke Electromagnetically actuated hydraulic quick-action switching valve
DE3934771C1 (en) * 1989-10-18 1991-03-28 Lucas Industries P.L.C., Birmingham, West Midlands, Gb
EP0551256B1 (en) * 1990-05-25 1994-07-27 ITT Automotive Europe GmbH Brake pressure regulator
DE4035817A1 (en) * 1990-11-10 1992-05-14 Bosch Gmbh Robert Electromagnetically actuated valve for vehicle hydraulic braking - permits release of fluid from enlarged bore of shaft guide in only one direction of travel
DE4041506C2 (en) * 1990-12-22 1995-01-19 Bosch Gmbh Robert Shut-off valve in a hydraulic brake system, in particular for motor vehicles
DE4234749A1 (en) * 1992-10-15 1994-04-21 Bosch Gmbh Robert Magnetic valve
JP3294382B2 (en) * 1992-10-30 2002-06-24 株式会社デンソー Flow control valve
DE4332368A1 (en) * 1993-09-23 1995-03-30 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE4332371A1 (en) * 1993-09-23 1995-03-30 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE4332372A1 (en) * 1993-09-23 1995-03-30 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE4339694A1 (en) * 1993-11-22 1995-05-24 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE4344440A1 (en) * 1993-12-24 1995-06-29 Teves Gmbh Alfred Solenoid valve, in particular for slip-controlled motor vehicle brake systems
DE4429211A1 (en) * 1994-08-18 1996-02-22 Bosch Gmbh Robert Solenoid valve for vehicle hydraulic ABS brakes
DE4433364A1 (en) * 1994-09-20 1996-03-21 Bosch Gmbh Robert Electromagnetically actuated valve, in particular for slip-controlled hydraulic brake systems in motor vehicles
DE19504077A1 (en) * 1995-02-08 1996-08-14 Bosch Gmbh Robert Electromagnetically operated valve for anti-wheel-lock braking system for automobiles

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9613414A1 *

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KR970706997A (en) 1997-12-01
DE4438336A1 (en) 1996-05-02
WO1996013414A1 (en) 1996-05-09
US6086164A (en) 2000-07-11
JPH10507813A (en) 1998-07-28

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