DE102016219952A1 - Solenoid valve and hydraulic brake system for a vehicle - Google Patents

Abstract

The invention relates to a solenoid valve (10) for a hydraulic brake system, comprising a magnet assembly, a pole core (11), a guide sleeve (13) connected to the pole core (11), a valve armature (20) guided axially movably within the guide sleeve (13). which is drivable by a magnetic force generated by the magnetic assembly against the force of a return spring (16) or by the force of the return spring (16) and axially moves a plunger (30) with a closing element (34), and with the guide sleeve (13 ) connected valve body (15) having a valve seat (15.1) which is arranged between at least a first flow opening (15.2) and at least a second flow opening (15.3), and a hydraulic brake system with such a solenoid valve (10). Here, the plunger (30) is rotatably connected to the valve armature (20) and the valve body (15) has a receiving area (15.4), which at least partially accommodates a guide assembly (40), wherein the plunger (30) in at least one through hole (15). 41.1, 44.1) of the guide assembly (40) is axially guided, wherein between the guide assembly (40) and the plunger (30) a mechanical latching device (18) is formed, which releases the plunger (30) in an energized closed position, so that the Return spring (16) drives the valve armature (20) with the plunger (30) and sealingly presses the closing element (34) in the valve seat (15.1) to perform a sealing function, and the valve armature (20) with the plunger (30) in a de-energized Open position against the force of the return spring (16) in an axial detent position so determines that the closing element (34) from the valve seat (15.1) is lifted.

Description

The invention relates to a solenoid valve for a hydraulic brake system according to the preamble of independent claim 1. The present invention is also a hydraulic brake system for a vehicle with such a solenoid valve.

Hydraulic brake systems for vehicles having a master cylinder, a hydraulic unit and a plurality of wheel brakes, which include various safety systems, such as an anti-lock brake system (ABS), electronic stability program (ESP), etc., and various safety functions, such as an anti-lock function, are known in the prior art , a traction control system (ASR) and so on. Control and / or regulating operations in the antilock braking system (ABS) or in the traction control system (ASR system) or in the electronic stability program system (ESP system) for the pressure build-up or pressure reduction in the corresponding wheel brakes can be carried out via the hydraulic unit. To carry out the control and / or regulating operations, the hydraulic unit comprises solenoid valves, which are usually held in unambiguous positions due to the counteracting forces "magnetic force", "spring force" and "hydraulic force". Accordingly, there are the valve types "normally open" and "normally closed". These solenoid valves each comprise a magnet assembly and a valve cartridge having a pole core, a guide sleeve connected to the pole core, an axially guided within the guide sleeve against the force of a return spring between a closed position and an open position armature with a plunger and a closing element and one with the Guide sleeve connected valve sleeve with a valve seat comprises. By the energization of the magnet assembly, a magnetic force is generated, which moves the armature with the plunger and the closing element in a de-energized open solenoid valve from the open position to the closed position until the closing element meets the corresponding valve seat and seals it. In the de-energized state, the return spring moves the armature with the plunger and the closing element and the closing element lifts off from the valve seat and releases it. When the solenoid valve is not energized, the armature with the plunger and the closing element is moved from the closed position to the open position by the energization of the magnet assembly, and the closing element lifts out of the valve seat and releases it. If the power is turned off, then the return spring moves the armature with the closing element in the direction of the valve seat until the closing element meets the valve seat and seals it. This energization is accompanied by energy consumption, which is undesirable. In addition, the functional reliability or functional availability is not given to the desired extent if the function is only achieved by active current supply.

In the published patent application DE 10 2007 051 557 A1 For example, a normally closed solenoid valve for a slip-controlled, hydraulic vehicle brake system is described. The solenoid valve comprises a hydraulic part, also referred to as a valve cartridge, which is arranged partially in a stepped bore of a valve block, and an electrical part, which is essentially formed by a magnet assembly which is plugged onto the part of the valve cartridge protruding from the valve block. The magnet assembly comprises a bobbin with an electrical winding, a magnet flux-conducting coil shell and a magnetic flux-conducting annular disc. The hydraulic part has a guide sleeve, which is closed at its end facing the electrical part with a pressed-in and fluid-tight welded pole core. In the guide sleeve, a longitudinally displaceable armature is accommodated, which is supported by a return spring on the pole core. Polkernabgewandt, the armature has a spherical closure member arranged in a recess. At Polkernabgewandten end a cup-shaped valve sleeve with a cylindrical shell and a bottom is pressed into the guide sleeve. The valve sleeve has at the bottom of a passage and a hollow cone-shaped valve seat, which forms a seat valve with the closing body. With the seat valve, a fluid connection between the passage at the bottom of the valve sleeve and at least one passage in the shell of the valve sleeve is designed to be switchable. In addition, a radial filter is arranged outside on the jacket of the valve sleeve in order to filter dirt particles from the fluid flow. The guide sleeve can be caulked by means of a fastening bush in the stepped bore of the valve block.

From the EP 0 073 886 B1 is a hydraulic control device with an axially displaceable in a plurality of switching positions and automatically by means of a return spring in one of its switching positions control spool known which outside this switch position can be fixed by engaging in detents spring-loaded detent, which further guided by a piston in a housing bore and on an adjacent annular space can be actuated hydraulically actuated by hydraulic fluid. The annulus is connected via a pilot valve with the leading to the consumer pump pressure line in connection, which is depressurized at shutdown of the consumer or. Here, the hydraulic travel of the catch relative to its possible against spring force travel is limited and the rest stops on Spool for engaging or engaging behind the catch are radially dimensioned so that a hydraulic release of the catch is possible regardless of the possible against spring force adjustment only at the designated detent positions.

Disclosure of the invention

The solenoid valve for a hydraulic brake system with the features of independent claim 1 has the advantage that in a solenoid valve with a de-energized first operating state, another currentless second operating state can be implemented. This means that embodiments of the present invention provide a bistable solenoid valve, which can be switched by applying a switching signal between the two operating states, wherein the solenoid valve remains permanently in the respective operating state until the next switching signal. Here, the first operating state of a closed position of the solenoid valve and the second operating state may correspond to an open position of the solenoid valve. The change between the two operating states can be performed, for example, by short energization of the active actuator of the magnet assembly or by applying a switching signal or current pulse to the magnet assembly. With such a short energization of energy consumption can be reduced in comparison with a conventional solenoid valve with two operating states in an advantageous manner, which has only a de-energized first operating state and must be energized to implement the energized second operating state for the duration of the second operating state. In addition, in contrast to embodiments of the present invention, the functional reliability or functional availability is not given to the desired extent if the function can only be achieved via active current supply.

Embodiments of the present invention provide a solenoid valve for a hydraulic brake system, comprising a magnet assembly, a pole core, a guide sleeve connected to the pole core, an axially within the guide sleeve guided valve armature, which of a magnetic force generated by the magnet assembly against the force of a return spring or by the force of the return spring is drivable and axially moves a plunger with a closing element, and a valve body connected to the guide sleeve with a valve seat available, which is arranged between at least a first flow opening and at least one second flow opening. Here, the plunger is rotatably connected to the valve armature and the valve body has a receiving area, which at least partially receives a guide assembly. The plunger is axially guided in at least one passage opening of the guide assembly, wherein between the guide assembly and the plunger, a mechanical latching device is formed, which releases the plunger in a de-energized closed position, so that the return spring drives the valve armature with the plunger and the closing element for executing a Sealing function sealingly presses in the valve seat, and the valve armature with the plunger in a de-energized open position against the force of the return spring in an axial detent position so determines that the closing element is lifted from the valve seat. In the de-energized closed position, the fluid flow between the at least one first flow opening and the at least one second flow opening is interrupted, and in the de-energized open position, the fluid flow between the at least one first flow opening and the at least one second flow opening is made possible.

Embodiments of the solenoid valve according to the invention advantageously have a very low leakage in the closed position and low energy consumption in the open position.

The hydraulic brake system for a vehicle having the features of independent claim 18 has the advantage that with little additional effort to a mostly existing hydraulic unit with ESP functionality an additional function can be realized, which include a current brake pressure in the corresponding wheel brake electro-hydraulic and at low energy demand over a longer period of time. This means that the existing pressure supply, the piping from the hydraulic unit to the wheel brakes as well as sensor and communication signals not only for the ESP function and / or ABS function and / or ASR function but also for an electro-hydraulic pressure maintenance function in the wheel brakes can be used. As a result, costs, installation space, weight and wiring can advantageously be saved with the positive effect that the complexity of the brake system is reduced.

The measures and refinements recited in the dependent claims advantageous improvements of the independent claim 1 solenoid valve for a hydraulic brake system are possible.

It is particularly advantageous that the mechanical locking device is designed as a rotary cam mechanism which uses a peripheral force component to a rotational position between the plunger with closing element and the To change guide assembly and the plunger with closing element axially into the locking position in and out again, so that the plunger with the closing element by applying a switching signal or current pulse to the magnet assembly can easily switch between the two de-energized positions. Starting from the currentless closed position, the plunger with the closing element by applying a switching signal from the de-energized closed position in the de-energized open position change. Upon application of a subsequent switching signal, the plunger changes with the closing element back from the de-energized open position to the de-energized closed position. Starting from the currentless open position, the plunger with the closing element by applying a switching signal from the de-energized open position to the de-energized closed position change. When applying a subsequent switching signal, the plunger changes with the closing element back from the de-energized closed position into the de-energized open position. In embodiments of the invention, the control of the armature stroke by means of positioning of the valve armature rotatably connected plunger takes place in a stationary backdrop. The axial movement of the valve armature in this case initiates through the link contour a rotational movement of the plunger in defined steps, which means that after each switching alternately sets an electroless open position or an electroless closed position of the solenoid valve and so the desired bistable behavior is achieved. The valve anchor itself only performs an axial movement. This is an advantage over solutions with rotating valve anchors in which magnetic transverse forces could hinder the rotational movement.

In an advantageous embodiment of the solenoid valve, the guide assembly can be rotatably or non-rotatably mounted in the receiving area of the valve body. For example, the guide assembly can be guided between a support and a retaining ring or in an undercut, which can define an axial position of the guide assembly.

In a further advantageous embodiment of the solenoid valve, the guide assembly may comprise a control cage, which may have a first passage opening, a first guide geometry, a second guide geometry and a third guide geometry, and a control ring, which may have a second passage opening and a fourth guide geometry. The control cage and the control ring, for example, each be executed as a single part. These items can be made for example as plastic parts in an injection molding process. Alternatively, the plastic parts can be made by powder injection molding (PIM) or ceramic injection molding (CIM) or metal injection molding (MIM), etc., or by 3D printing. In addition, the control ring can be produced as a sheet metal part in a stamping bending process. Due to the multi-part design of the guide assembly as plastic parts, the complex guide geometries can be easily and inexpensively mass produced as parts and then joined together. The control cage and the control ring can be rotatably connected to each other, wherein the control ring inserted into the control cage and at least one formed on the control ring positioning nose can be joined in a corresponding formed on the control cage positioning recess. Alternatively, the guide assembly with control cage and control ring can be made in one piece, for example as a two-component plastic injection molded part.

In a further advantageous embodiment of the solenoid valve of the control cage can be designed as a hollow cylinder. In this case, the first guide geometry may comprise first guide straps and cage recesses, which may be formed in uniform angular pitch on a pole core facing the end of the hollow cylinder designed as a control cage, wherein the cage recesses are arranged between the first guide plates. In addition, the second guide geometry may comprise bearing areas, which can be arranged on the first guide plates.

In a further advantageous embodiment of the solenoid valve, the third guide geometry may have a first circumferential slotted guide with formed on a wall of the first passage opening in uniform angular pitch first recesses, which are separated by first dividers, to each of which a one-sided chamfer can be formed. The fourth guide geometry may have a second circumferential slotted guide with second recesses formed at a wall of the second passage opening in a uniform angular pitch, which are separated from each other by second partitions, on each of which a one-sided chamfer can be formed. In this case, the first separating webs can be arranged offset from the second separating webs.

In a further advantageous embodiment of the solenoid valve, at least one locking lugs can be arranged on the outer circumference of the control cage, which engage in an opening formed on the receiving region of the valve body undercut and can rest on a support. This allows the guide assembly with the control ring and the control cage stationary and rotationally fixed in the valve body can be mounted. Thus, the at least one arranged on the outer diameter of the control cage locking lug can engage in the undercut in the valve body. Of the Undercut can be easily and inexpensively manufactured in a valve body made of steel, for example, by turning or pressing a ring or snapping a C-shaped clamping ring in a corresponding groove.

In a further advantageous embodiment of the solenoid valve, the valve anchor may have a stepped cylindrical base body with different outer diameters. Here, a valve seat facing the end of the main body of the valve armature can be formed as a first receiving portion whose outer diameter can be adapted to an inner diameter of a recess in the main body of the plunger, that the plunger can be rotated on the valve armature about a common longitudinal axis. In this case, the inner diameter of the plunger with the smaller outer diameter of the valve armature forms a bearing point, which can prevent its terminals by a jamming or tilting of the plunger on the valve arm in an advantageous manner.

In a further advantageous embodiment of the solenoid valve, a hollow cylindrical body of a pull ring rotatably connected to a second receiving portion of the main body of the valve armature, which is arranged in the direction of pole core after the first receiving portion and may have a larger outer diameter than the first receiving portion. Here, a fifth guide geometry, which cooperate with the first guide geometry of the control cage and guide the valve armature during its axial movement and can prevent a rotational movement of the valve armature, and a sixth guide geometry can be formed on the main body of the pull ring, which cooperate with a formed on the tappet seventh guide geometry and allow a rotational movement of the plunger. The fifth guide geometry can comprise second guide straps connected to the hollow cylindrical main body of the pull ring, which can be toothed with the first guide straps of the first guide geometry. The sixth guide geometry may comprise tensile claws, which may be formed at the free ends of the second guide tabs. Furthermore, the seventh guide geometry of the plunger may comprise a circumferential groove, which can be introduced into the base body at an end facing the pole core. Here, the tensile claws of the sixth guide geometry can engage in the circumferential groove. Due to the tensile claws of the valve armature can take the plunger with an axial movement in the direction of the pole core, at the same time a rotational movement of the plunger is made possible around the common longitudinal axis.

In a further advantageous embodiment of the solenoid valve at an at least one through hole of the guide assembly guided portion of the main body of the plunger an eighth guide geometry, which in an axial movement in the direction of the pole core with the third guide geometry of the control cage and an axial movement in the direction of the valve seat with the fourth guide geometry of the control ring can cooperate, and a ninth guide geometry can be formed, which can cooperate in the de-energized open position with the control cage formed on the second guide geometry.

In a further advantageous embodiment of the solenoid valve, the eighth guide geometry may comprise at least one positioning element, which may be arranged on the base body of the plunger and projecting radially. In a rounded embodiment of the at least one positioning element, the initiation of a rotational movement of the plunger can advantageously take place via a tangential contact of the rounded positioning element on an inclined surface. As a result, in the expected in the vehicle high number of switching operations in contrast to other solutions, which rotate for the function of the rotary indexing axially biased acute contours against each other contact, a wear on the functionally important parts avoided or at least reduced. In addition, the switching can be implemented in comparison to other solutions with a relatively small axial actuating stroke, which can have a positive effect on the achievable axial force in the solenoid valve on the reduced air gap. Alternatively, the at least one positioning element may have an angular, preferably triangular cross-section. Furthermore, the ninth guide geometry may include heels which can be arranged in a uniform angular pitch on the main body of the plunger.

In a further advantageous embodiment of the solenoid valve, the valve armature can take the plunger and its closing element in an axial movement in the direction of pole core caused by the magnetic force of the magnet assembly, wherein the at least one positioning element, starting from a position in a second recess meets a corresponding bevel of the control cage, whereby a circumferential force acting on the plunger and the plunger can rotate about a corresponding longitudinal axis until the at least one positioning element at the end of the chamfer can slide in a corresponding first recess. When caused by the spring force of the return spring axial movement of the valve armature in the direction of the valve seat, the at least one positioning element from the first recess meets a corresponding bevel of the control ring, whereby a circumferential force acting on the plunger and the plunger can continue to rotate about the corresponding longitudinal axis until the at least one positioning element at the end of the chamfer can slide in a corresponding second recess. In the currentless open position, the at least one positioning element can be guided in a corresponding second recess of the fourth guide geometry, and at least one shoulder of the ninth guide geometry can rest on a corresponding contact area of the second guide geometry. In this position, the resting of the at least one ram paragraph on a corresponding bearing area of the control cage prevents the closing element from approaching the valve seat. The spring force of the return spring, which acts on the valve armature is supported by the Zugkrallen and the ram paragraphs through the bearing areas of the control cage. The at least one positioning element of the plunger is located between the chamfers of the control ring and in the axial direction below the chamfers of the control cage. In the de-energized closed position, the at least one positioning element can be guided in a corresponding first recess of the third guide geometry and all paragraphs of the ninth guide geometry are guided in cage recesses and the closing element is sealingly in the valve seat. The maximum working stroke of the valve armature can be predetermined for example by an air gap between the pole core and the valve armature or by the stop of the valve armature on the pole core.

The valve anchor can be radially guided by an arranged outside the guide assembly portion of the body on an inner wall of the guide sleeve. Due to the requirement of the magnetic conductivity of the valve armature is made of a magnetically conductive material, for example in the cold impact method or by machining. The pole core is also made of a magnetically conductive material. The plunger can be produced for example as a plastic component in an injection molding process. Alternatively, the ram can be made by powder injection molding (PIM) or ceramic injection molding (CIM) or metal injection molding (MIM), etc., or by 3D printing. In addition, the plunger can be made in one piece at its tip as a closing element for the valve seat. Alternatively, the plunger can be made in several parts and, for example, an additional sealing element, such as an O-ring seal, which is arranged in the region of the closing element and improves the sealing effect in the closed position. The plunger can for example be pressed into a corresponding receptacle in the main body of the valve anchor. The pull ring can be manufactured as a stamped and bent part from magnetically conductive sheet steel.

Embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description. In the drawing, like reference numerals designate components that perform the same or analog functions.

list of figures

• 1 shows a schematic perspective sectional view of an embodiment of a solenoid valve according to the invention in its de-energized open position.
• 2 shows a schematic perspective view of an embodiment of a control cage for the solenoid valve 1 ,
• 3 shows a schematic perspective view of an embodiment of a control ring for the solenoid valve 1 ,
• 4 shows a schematic perspective partial sectional view of a valve body of the solenoid valve 1 joined guide assembly, which the control cage off 2 and the control ring 3 includes.
• 5 shows a schematic partial sectional view of an embodiment of a pull ring for the solenoid valve 1 ,
• 6 shows a schematic partial sectional view of an embodiment of a plunger for the solenoid valve 1 ,
• 7 shows a schematic perspective view of the with the pull ring 5 fitted ram 6 ,
• 8th shows a schematic sectional view of the valve anchor with the joined pull ring 5 and the attached pestle 6 ,
• 9 to 13 each show a schematic perspective view of an embodiment of a mechanical locking device for the solenoid valve 1 in different positions.
• 14 shows a schematic perspective sectional view of the solenoid valve according to the invention 1 in its de-energized closed position.
• 15 shows a schematic hydraulic circuit diagram of an embodiment of a hydraulic brake system according to the invention for a vehicle.

Embodiments of the invention

How out 1 to 15 it can be seen, the illustrated embodiment comprises a solenoid valve according to the invention 10 for a hydraulic brake system 1 a magnetic assembly, not shown, a pole core 11 , one with the pole core 11 connected guide sleeve 13 , one inside the guide sleeve 13 axially movably guided valve anchor 20 which depends on a magnetic force generated by the magnet assembly against the force of a return spring 16 or by the force of the return spring 16 is drivable and a pestle 30 with a closing element 34 moved axially, and one with the guide sleeve 13 connected valve body 15 with a valve seat 15.1 , which between at least a first flow opening 15.2 and at least one second flow opening 15.3 is arranged. Here is the plunger 30 rotatable with the valve anchor 20 connected and the valve body 15 has a recording area 15.4 on which a guide assembly 40 at least partially absorbs. The pestle 30 is in at least one passage opening 41.1 . 44.1 the guide assembly 40 axially guided, being between the guide assembly 40 and the pestle 30 a mechanical locking device 18 is formed, which the plunger 30 in an in 14 illustrated energized closed position releases, so that the return spring 16 the valve anchor 20 with the pestle 30 drives and the closing element 34 to perform a sealing function sealing in the valve seat 15.1 presses and a fluid flow between the at least one first flow opening 15.2 and the at least one second flow opening 15.3 interrupts, and the valve anchor 20 with the pestle 30 in an in 1 shown powerless open position against the force of the return spring 16 in an axial detent position so determines that the closing element 34 from the valve seat 15.1 lifted and the fluid flow between the at least one first flow opening 15.2 and the at least one second flow opening 15.3 is possible. This will be a bistable solenoid valve 10 implemented, which can be switched by applying a switching signal between the two positions, wherein the solenoid valve 10 remains permanently in the respective operating state until the next switching signal.

Such a bistable solenoid valve 10 For example, in a hydraulic brake system 1 be used for a vehicle.

How out 15 it can be seen comprises the illustrated embodiment of a hydraulic brake system according to the invention 1 for a vehicle with which various safety functions can be performed, a master cylinder 5 , a hydraulic unit 9 and several wheel brakes RR, FL, FR, RL. The hydraulic unit 9 comprises at least two brake circuits BC1, BC2 for brake pressure modulation in the wheel brakes RR, FL, FR, RL. In this case, the at least two brake circuits BC1, BC2 each have a bistable solenoid valve 10 on, which has an electroless closed position and a currentless open position and is switchable between the two positions, wherein the bistable solenoid valve 10 in the de-energized open position releases the brake pressure modulation in at least one associated wheel brake RR, FL, FR, RL and includes a current brake pressure in the at least one associated wheel brake RR, FL, FR, RL in the de-energized closed position.

How out 15 can be further seen, includes the illustrated embodiment of the hydraulic brake system 1 two brake circuits BC1, BC2, which in each case two of the four wheel brakes RR, FL, FR, RL are assigned. Thus, a first wheel brake FR, which is arranged for example on a vehicle front axle on the right side, and a second wheel brake RL, which is arranged for example on a vehicle rear axle on the left side, associated with a first brake circuit BC1. A third wheel brake RR, which is arranged, for example, on a vehicle rear axle on the right side, and a fourth wheel brake FL, which is arranged for example on the vehicle front axle on the left side, are associated with a second brake circuit BC2. Each wheel brake RR, FL, FR, RL is an intake valve EV11, EV21, EV12, EV22 and an exhaust valve AV11, AV21, AV12, AV22 assigned, via the inlet valves EV11, EV21, EV12, EV22 respectively pressure in the corresponding wheel brake RR, FL, FR, RL can be constructed, and wherein via the exhaust valves AV11, AV21, AV12, AV22 respectively pressure in the corresponding wheel brake RR, FL, FR, RL can be reduced. For pressure build-up in the respective wheel brake RR, FL, FR, RL, the corresponding inlet valve EV11, EV12, EV21, EV22 is opened and the corresponding outlet valve AV11, AV12, AV21, AV22 closed. For depressurization in the respective wheel brake RR, FL, FR, RL, the corresponding inlet valve EV11, EV21, EV12, EV22 is closed and the corresponding outlet valve AV11, AV21, AV12, AV22 opened.

How out 15 2, the second wheel brake RL is associated with a second intake valve EV21 and a second exhaust valve AV21, the third wheel brake RR is a third intake valve EV12 and a third exhaust valve AV12 and the fourth wheel brake FL are associated with a fourth intake valve EV22 and a fourth exhaust valve AV22. The intake valves EV11, EV21, EV12, EV22 and the exhaust valves AV11, AV21, AV12, AV22 can be used to perform control and / or regulating operations to implement an ABS function.

In addition, the first brake circuit BC1 has a first intake valve HSV1, a first system pressure control valve USV1, a first compensation reservoir A1 with a first check valve RSV1 and a first fluid pump PE1. The second brake circuit BC2 has a second intake valve HSV2, a second system pressure control valve USV2, a second surge tank A2 with a second check valve RSV2 and a second fluid pump PE2, the first and second fluid pumps PE1, PE2 being driven by a common electric motor M. Furthermore, the hydraulic unit includes 9 to determine the current system pressure or brake pressure, a sensor unit 9.1 , The hydraulic unit 9 used for brake pressure modulation and to implement an ASR function and / or an ESP function in the first brake circuit BC1, the first system pressure control valve USV1, the first intake valve HSV1 and the first return pump PE1 and second brake circuit BC2, the second system pressure control valve USV2, the second intake valve HSV2 and the second return pump PE2. How out 15 It can also be seen that each brake circuit BC1, BC2 is connected to the master brake cylinder 5 connected, which via a brake pedal 3 can be operated. In addition, a fluid container 7 with the master cylinder 5 connected. The intake valves HSV1, HSV2 allow intervention in the brake system without the need for a driver. For this purpose, the respective suction path for the corresponding fluid pump PE1, PE2 to the master cylinder via the intake valves HSV1, HSV2 5 open, so that this can provide the required pressure for the control instead of the driver. The system pressure control valves USV1, USV2 are between the master cylinder 5 and at least one associated wheel brake RR, FL, FR, RL arranged and adjust the system pressure or brake pressure in the associated brake circuit BC1, BC2. How out 15 Further, a first system pressure control valve USV1 sets the system pressure or brake pressure in the first brake circuit BC1, and a second system pressure control valve USV2 sets the system pressure or brake pressure in the second brake circuit BC2.

How out 15 can be further seen, the bistable solenoid valves 10 be looped at different positions P1, P2, P3, P4, P5 in the respective brake circuit BC1, BC2. In the illustrated embodiments, the various positions P1, P2, P3, P4, P5 are respectively designated in the second brake circuit BC2. How out 15 It can also be seen that the bistable solenoid valves 10 each at a first position P1 between the corresponding system pressure control valve USV1, USV2 and the inlet valves EV11, EV12, EV21, EV22 in front of an outlet channel of the corresponding fluid pump PE1, PE2 looped into the respective brake circuit BC1, BC2. Alternatively, the bistable solenoid valves 10 each at a second position P2 between the master cylinder 5 and the corresponding system pressure control valve USV1, USV2 are connected directly in front of the corresponding system pressure control valve USV1, USV2 in the respective brake circuit BC1, BC2. As a further alternative arrangement, the bistable solenoid valves 10 in each case at a third position P3 between the corresponding system pressure control valve USV1, USV2 and the inlet valves EV11, EV12, EV21, EV22 are looped to the outlet channel of the fluid pump PE1, PE2 in the respective brake circuit BC1, BC2. In addition, the bistable solenoid valves 10 in a further alternative arrangement, in each case at a fourth position P4 between the master brake cylinder 5 and the corresponding system pressure control valve USV1, USV2 in the common fluid branch immediately after the master cylinder 5 be looped into the respective brake circuit BC1, BC2. In addition, the bistable solenoid valves 10 in each case at a fifth position P5 are looped directly in front of an associated wheel brake RR, FL, FR, RL in the respective brake circuit BC1, BC2.

How out 15 is further apparent is in the illustrated embodiment of the hydraulic brake system 1 an electrical energy store in the form of a vehicle electrical system used to the in the at least one associated wheel brake RR, FL, FR, RL in the de-energized closed position of the bistable solenoid valve 10 enclosed brake pressure by Nachfördern brake fluid via the fluid pump PE1, PE2 to keep constant. Since electrical energy is required only for valve switching and for the short Nachförderfunktion, there is only a small additional electrical energy requirement for the brake pressure maintenance function. Alternatively, in an embodiment, not shown, hydraulic storage devices may be used to control the in the at least one associated wheel brake RR, FL, FR, RL in the de-energized closed position of the bistable solenoid valve 10 enclosed brake pressure by Nachfördern of brake fluid to keep constant. Since electrical energy is required only for valve switching, but virtually no electrical energy is required for the Nachförderfunktion, results from the hydraulic storage devices even lower electrical energy requirements for the brake pressure maintenance function.

By means of the measures described, it is advantageously possible to compensate for any internal leakage and volume expansions which may be present, for example due to Temperature response can occur. In addition, the described measures can be combined. That is, the hydraulic storage device may be combined with the electrical storage device to operate in the de-energized closed position of the bistable solenoid 10 in the at least one associated wheel brake RR, FL, FR, RL trapped brake pressure to be kept constant by Nachförden brake fluid over a longer period.

How out 1 to 14 can be further seen, is the mechanical locking device 18 designed as a rotary cam mechanism which uses a peripheral force component to a rotational position between the plunger 30 with closing element 34 and the guide assembly 40 to change and the plunger 30 with closing element 34 axially into the detent position and out again to move, so that the plunger 30 with the closing element 34 can switch by applying a switching signal to the magnet assembly between the two de-energized positions. The guide assembly 40 is rotatably in the illustrated embodiment in the receiving area 19 of the valve body 15 stored.

In the illustrated embodiment, the guide assembly includes 40 a Steuerkä 41 which has a first passage opening 41.1 , a first guide geometry 47 , a second guide geometry 48 and a third guide geometry 42, and a control ring 44 , which has a second passage opening 44.1 and a fourth guide geometry 45 having. The tax kä 41 and the tax ring 44 are executed in the illustrated embodiment, each as a plastic part and rotatably connected to each other. Here is the tax ring 44 in the tax kä 41 introduced and three on the tax ring 44 trained positioning tabs 44.2 are in corresponding at the Steuerkä 41 trained positioning recesses 41.2 together. Of course, fewer or more than three positioning noses can 44.2 and positioning recesses 41.2 used to control the control ring 44 rotatably with the Steuerkä 41 connect to. In addition, the tax ring 44 be executed in an alternative embodiment, not shown as a stamped and bent sheet metal part. Alternatively, the guide assembly 40 with tax kä 41 and tax ring 44 be made in one piece as a two-component plastic injection molded part.

The tax kä 41 is executed in the illustrated embodiment as a hollow cylinder. Here, the first guide geometry includes 47 first guide tabs 47.1 and cage recesses 47.2 , which in uniform angular pitch at one of the pole core 11 facing the end of the hollow cylinder designed as a control cage 41 are formed. In the illustrated embodiment, nine first guide plates 47.1 with an angular pitch of 9 x 40 ° and a width of 20 ° each at the control box 41 educated. That means nine cage recesses 47.2 between the first guide tabs 47.1 also have a width of 20 °. The second guide geometry 48 covers nine areas of support 48.1 , which in each case at one of the first passage opening 41.1 facing side of the first guide tabs 47.1 are arranged. The mentioned number of nine first guide tabs 47.1 and nine cage recesses 47.2 is just like the angular pitch of 40 ° and the width of 20 ° only by way of example and is for ease of explanation. A different distribution over the 360 ° circumference is of course possible.

As in particular from 2 and 4 can be seen further, the third guide geometry 42 a first circumferential slide guide 43 with on a wall of the first passage opening 41.1 of the control cage 41 formed in a uniform angular pitch first recesses 43.1 on, which by first dividers 43.2 are separated from each other. At the first dividers 43.2 is each a one-sided bevel 43.3 educated. In the illustrated embodiment, eighteen first recesses 43.1 with an angular pitch of 18 x 20 ° and a width of 10 ° on the wall of the first through hole 41.1 educated. That means the first dividers 43.2 between the first recesses 43.1 also have a width of 10 °. The first recesses 43.1 and the first dividers 43.2 are arranged so that in each case a first recess 43.1 and a first divider 43.2 in the axial direction under a first guide tab 47.1 and a cage recess 47.2 are arranged.

As in particular from 3 and 4 can be seen, has the second guide geometry 45 a second circumferential slotted guide 46 with at a wall of the second passage opening 44.1 the control ring 44 formed in a uniform angular pitch second recesses 46.1 on, which by second dividers 46.2 are separated from each other. At the second dividers 46.2 is each a one-sided bevel 46.3 educated. In the illustrated embodiment, eighteen second recesses 46.1 with an angular pitch of 18 x 20 ° and a width of 10 ° on the wall of the second through hole 44.1 educated. That means the second dividers 46.2 between the second recesses 46.1 also have a width of 10 °. How out 3 can be further seen, are the first dividers 43.2 offset to the second dividers 46.2 arranged. In the illustrated embodiment, the offset between the first dividers 43.2 and the second dividers 46.2 each 10 °. This causes the chamfers 43.3 the first dividers 43.2 opposite the second recesses 46.1 and the bevels 46.3 the second dividers 46.2 are opposite the first recesses 43.1 arranged. The mentioned number of eighteen first recesses each 43.1 and second recesses 46.1 is just like the angular pitch of 20 ° and the width of 10 ° only by way of example and is for ease of explanation. A different distribution over the 360 ° circumference is of course possible.

As in particular from 2 and 4 is further apparent, are on the outer circumference of the control cage 41 several locking lugs 41.4 arranged, which in one at the receiving area 15.4 of the valve body 15 trained undercut 19 intervene and on a pad 17 rest. This is the guide assembly 40 rotationally fixed and stationary with the valve body 15 connected.

The valve anchor 20 has in the illustrated embodiment, a stepped cylindrical body 22 with different outside diameters, with one the valve seat 15.1 facing end of the body 22 of the valve anchor 20 as the first recording section 24 is formed, the outer diameter so to an inner diameter of a recess 33 in the main body 32 of the plunger 30 adapted is that the plunger 32 on the valve anchor 20 is rotatable about a common longitudinal axis. A hollow cylindrical body 52 a pull ring 50 is rotationally fixed with a second receiving portion 25 of the basic body 22 of the valve anchor 20 connected, which in the direction of Polkern 11 after the first recording section 24 is arranged and a larger outer diameter than the first receiving portion 24 having. The valve anchor 20 is through one outside the guide assembly 40 arranged portion of the body 22 whose outer diameter is larger than the outer diameter of the second receiving portion 25 is, on an inner wall of the guide sleeve 13 guided radially. In addition, the basic body 22 of the valve anchor 20 equalization 28 on. At its the pole core 11 facing end, the body 22 of the valve anchor 20 a spring receiver 26 on which the return spring 16 at least partially absorbs. The return spring 16 rests on one end on a valve anchor 20 facing pole surface of the pole core 11 and at the other end on a support in the spring retainer 26 from. In an alternative embodiment not shown, the spring receptacle 26 also in the pole core 11 be introduced so that the return spring 16 at the pole core 11 facing end face of the valve anchor 20 and in the spring receptacle 26 supported. One between the pole face of the pole core 11 and a pole face of the valve anchor 20 Trained air gap 12 specifies a maximum possible armature stroke.

As in particular from 5 and 7 is apparent, is at the base body 52 of the pull ring 50 a fifth guide geometry 54 , which with the first guide geometry 47 of the control cage 41 interacts and the valve anchor 20 during its axial movement and a rotational movement of the valve armature 20 prevented.

The fifth guide geometry 54 includes nine on the hollow cylindrical body 52 of the pull ring 50 Tethered second guide plates 54.1 , which with the first guide tabs 47.1 the first guide geometry 47 interlocked. That means the second guide tabs 54.1 each have a width of 20 ° in the illustrated embodiment and in the cage recesses 47.2 are guided. Furthermore, it is on the main body 52 of the pull ring 50 a sixth guide geometry 55 formed, which with a on the plunger 30 trained seventh leadership geometry 36 cooperates and a rotational movement of the plunger 30 allows. The sixth guide geometry 55 includes nine tensile claws 54.1 , which at the free ends of the second guide tabs 54.1 are formed. The seventh guide geometry 36 of the plunger 30 includes a circumferential groove 36.1 , which at one the Polkern 11 facing end into the body 32 is brought in, with the Zugkrallen 54.1 the sixth guide geometry 54 in the circumferential groove 36.1 intervention. This allows the valve anchor 20 during an axial movement in the direction of the pole core 11 the pestle 30 take along, at the same time a rotational movement of the plunger 30 around the common longitudinal axis is made possible.

As in particular from 6 and 7 is further apparent, are at one in the at least one through hole 41.1 . 44.1 the guide assembly 40 guided section of the body 32 of the plunger 30 an eighth guide geometry 39 which in the case of an axial movement in the direction of the pole core 11 with the third guide geometry 42 of the control cage 40 and with an axial movement in the direction of the valve seat 15.1 with the fourth guide geometry 45 the control ring 44 interacts, and a ninth leadership geometry 38 formed, which in the de-energized open position with the tax kä 41 trained second guide geometry 48 interacts. The eighth guide geometry 39 in the illustrated embodiment, at least one rounded positioning element 39.1 on, which at the base body 32 of the plunger 30 is arranged and protrudes radially. Alternatively, the positioning element 39.1 be executed with an angular, preferably with a triangular cross section, so that surfaces of the positioning element 39.1 parallel to the corresponding chamfers 43.3 or bevels 46.3 are aligned. In addition, the at least one positioning element 39.1 alternative for integral with the ram 30 in a radial bore of the body 32 of the plunger 30 be pressed in. The positioning element 39.1 can have one in the Steuerkä 41 arranged insertion recess 41.3 inside the guide assembly 40 be introduced and with the first and second slide guide 43 . 46 interact. The ninth guide geometry 38 includes nine paragraphs 38.1 , which in uniform angular pitch on the body 32 of the plunger 30 are arranged. In the illustrated embodiment are analogous to the nine bearing areas 48.1 the second guide geometry 48 nine paragraphs 39.1 with an angular pitch of 9 x 40 ° and a width of 20 ° on the ram 30 educated. As in particular from 6 and 7 is further apparent, is on a valve seat 15.1 facing end of the main body 32 the closing element 34 formed, which is the tip of the plunger 30 forms and to exercise the sealing function with the valve seat 15.1 interacts. In the illustrated embodiment, the plunger 30 designed as a plastic injection molded part. Alternatively, the plunger 40 in a PIM, CIM or MIM process or as a 3D printing part. In addition, on the closing element 34 a sealing element are arranged to the sealing effect in the valve seat 15.1 to improve. The sealing element can be performed for example as an O-ring seal.

The following is with reference to 9 to 13 the movement of the valve anchor 20 with pestle 30 and closing element 34 starting from the in 1 illustrated currentless open position in the in 14 illustrated electroless closed position described.

How out 1 and 9 is further apparent, is the positioning element 39.1 of the plunger 30 in the illustrated de-energized open position of the solenoid valve 10 between two bevels 46.3 the control ring 44 in a second recess 46.1 arranged and is located on a second divider 46.2 at. In addition, there are the nine paragraphs 38.1 of the plunger 30 each on a support area 48.1 of the control cage 41 on and the closing element 34 is from the valve seat 15.1 lifted and allows the fluid flow between the at least one first flow opening 15.2 and the at least one second flow opening 15.3 , In this position prevents the rests of the plunger heels 38.1 on the support areas 48.1 of the control cage 41 an approximation of the closing element 34 to the valve seat 15.1 , The spring force of the return spring 16 , which acts on the valve anchor 20, is over the Zugkrallen 55.1 of the pull ring 50 and the ram heels 38.1 through the support areas 48.1 of the control cage 41 supported. In the illustrated embodiment, only one positioning element 39.1 used. However, it can also be several positioning elements 39.1 over the circumference of the plunger 30 distributed to improve the leadership.

How out 10 can be seen further, takes the valve anchor 20 at a caused by magnetic force of the magnet assembly axial movement in the direction of the pole core 11 the pestle 30 and its closing element 34 over the train claws 55.1 of the pull ring 50 with, which in the circumferential groove 36.1 of the plunger 30 intervention. This will lift the ram heels 38.1 from the bearing areas 48.1 of the control cage 41 from. In addition, the rounded positioning element meets 39.1 of the plunger 30 starting from the position in the second recess 46.1 tangential to a corresponding chamfer 43.3 of the control cage 41 , In 10 is the moment during the upward movement of the valve anchor 20 shown in which the rounded positioning element 39.1 Contact with the chamfer 43.3 of the control cage 41 gets. As a result, a circumferential force acts on the plunger 30 and the plunger turns on the valve anchor 20 around the common longitudinal axis to the rounded positioning element 28.1 at the end of the chamfer 43.3 in a corresponding first recess 43.1 slides out, like out 11 is apparent. Here, a predetermined maximum axial stroke is achieved and the rounded positioning 39.1 is between two chamfers 43.3 of the control cage 41 in a first recess 43.1 arranged and is located on a first divider 43.2 at. In the illustrated embodiment, the plunger rotates 30 until the maximum axial stroke is reached by 10 ° to the left. The maximum axial stroke is achieved when the valve armature 20 with pull ring 50 and pestles 30 abuts an upper stop, which, for example, by a pole face of the pole core 11 is formed. In this position, the ram heels cover 38.1 each half a corresponding first guide tab 47.1 and a corresponding cage recess 47.2 ,

After switching off the magnetic force, the spring force causes the return spring 16 the axial movement of the valve anchor 20 with pull ring 50 , Pestle 30 and closing element 34 in the direction of the valve seat 15.1 , The rounded positioning element moves 39.1 from the first recess 43.1 and tangentially hits a corresponding chamfer 46.3 the control ring 44 , As a result, a circumferential force acts on the plunger 30 and turn the pestle 30 on the valve anchor 20 continue around the common longitudinal axis until the rounded positioning element 39.1 at the end of the chamfer 46.3 in a corresponding second recess 46.2 slides out, like out 13 is apparent. In 12 is the moment during the downward movement of the valve anchor 20 shown in which the rotational movement of the plunger 30 is completed. In the illustrated embodiment, the plunger rotates 30 until the completion of the rotation of another 10 ° to the left. In the downward movement towards the valve seat, the plunger has 30 so further turned that the ram paragraphs 38.1 in the cage recesses 47.2 lie. This allows the valve anchor 20 with the pestle 30 by the spring force of the return spring 16 until the stop of the closing element 34 in the valve seat 15.1 can be pushed further in the direction of the valve seat, so that the closing element sealingly rests in the valve seat and the solenoid valve 10 in its de-energized closed position and the fluid flow between the at least one first flow opening 15.2 and the at least one second flow opening 15.3 is interrupted. How out 13 is further apparent, is the rounded positioning element 39.1 in the now achieved currentless closed position between two bevels 46.3 the control ring 44 in a second recess 46.1 arranged and is located on a second divider 46.2 at. From the in 13 shown de-energized closed position, the principle described is repeated with half a partial rotation in the energized upward movement and half a partial rotation in the de-energized downward movement during the next energizing the magnet assembly, so that then adjusts the de-energized open position. The ram heels 38.1 lie after each shift alternately either on or between the support areas 48.1 of the control cage 41 , In the de-energized open position, the spring force of the return spring 16 , which on the valve anchor 20 acts, over the Zugkrallen 55.1 and the ram heels 38.1 through the support areas 48.1 of the control cage 41 supported.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102007051557 A1 [0003]
• EP 0073886 B1 [0004]

Claims (18)

Solenoid valve (10) for a hydraulic brake system (1), comprising a magnet assembly, a pole core (11), a guide sleeve (13) connected to the pole core (11), a valve armature (20) guided axially movably within the guide sleeve (13), which is drivable by a magnetic force generated by the magnetic assembly against the force of a return spring (16) or by the force of the return spring (16) and axially moves a plunger (30) with a closing element (34), and one with the guide sleeve (13) connected valve body (15) having a valve seat (15.1) which is arranged between at least a first flow opening (15.2) and at least one second flow opening (15.3), characterized in that the plunger (30) is rotatably connected to the valve armature (20) and the valve body (15) has a receiving region (15.4) which at least partially accommodates a guide assembly (40), wherein the plunger (30) in at least a passage opening (41.1, 44.1) of the guide assembly (40) is guided axially, wherein between the guide assembly (40) and the plunger (30) a mechanical latching device (18) is formed, which releases the plunger (30) in an energized closed position, such that the return spring (16) drives the valve armature (20) with the plunger (30) and presses the closing element (34) sealingly into the valve seat (15.1) to perform a sealing function, and the valve armature (20) with the plunger (30). in an electroless open position against the force of the return spring (16) in an axial detent position so determines that the closing element (34) from the valve seat (15.1) is lifted. Solenoid valve after Claim 1 characterized in that the mechanical detent device (18) is a rotary cam mechanism which utilizes a peripheral force component to change a rotational position between the tappet (30) with closure member (34) and the guide assembly (40) and engages the tappet (30) Closing element (34) axially into the locking position in and out again to move, so that the plunger (30) to the closing element (34) by applying a switching signal to the magnet assembly between the two de-energized positions changes. Solenoid valve after Claim 1 or 2 , characterized in that the guide assembly (40) rotatably or non-rotatably in the receiving area (15.4) of the valve body (15) is mounted. Solenoid valve according to one of the Claims 1 to 3 characterized in that the guide assembly (40) comprises a control cage (41) having a first passage opening (41.1), a first guide geometry (47), a second guide geometry (48) and a third guide geometry (42), and a control ring (41). 44), which has a second passage opening (44.1) and a fourth guide geometry (45). Solenoid valve after Claim 4 , characterized in that the control cage (41) and the control ring (44) are each designed as a single part or the guide assembly (40) with control cage (41) and control ring (44) is made in one piece. Solenoid valve after Claim 5 , characterized in that the control cage (41) and the control ring (44) are rotatably connected to each other, wherein the control ring (44) is inserted into the control cage (41) and at least one positioning nose (44.2) formed on the control ring (44) in one corresponding formed on the control cage positioning recess (41.2) is joined. Solenoid valve according to one of the Claims 4 to 6 , characterized in that the control cage (41) is designed as a hollow cylinder, wherein the first guide geometry (47) comprises first guide plates (47.1) and cage recesses (47.2) which in uniform angular pitch at one of the pole core (11) facing the end of the hollow cylinder the cage recesses (47.2) between the first guide plates (47.1) are arranged, and wherein the second guide geometry (48) bearing areas (48.1), which are arranged on the first guide plates (47.1). Solenoid valve after Claim 7 , characterized in that the third guide geometry (42) has a first circumferential slotted guide (43) with first recesses (43.1) formed at a wall of the first passage opening (41.1) in uniform angular pitch, which are separated from each other by first separating webs (43.2), on each of which a one-sided chamfer (43.3) is formed, and wherein the fourth guide geometry (45) has a second circumferential slotted guide (46) formed on a wall of the second passage opening (44.1) in a uniform angular pitch second recesses (46.1), which by second separating webs (46.2) are separated from each other, on each of which a one-sided chamfer (46.3) is formed, wherein the first separating webs (43.2) offset from the second separating webs (46.2) are arranged. Solenoid valve after Claim 7 or 8th , characterized in that on the outer circumference of the control cage (41) at least one latching lug (41.4) is arranged, which engages in a receiving area (15.4) of the valve body (15) formed undercut (19) and rests on a support (17). Solenoid valve according to one of the Claims 1 to 9 , characterized in that the valve anchor (20) has a stepped cylindrical base body (22) with different outer diameters, wherein an end of the base body (22) of the valve anchor (20) facing the valve seat (15.1) is designed as a first receiving portion (24), whose outer diameter is adapted to an inner diameter of a recess (33) in the base body (32) of the plunger (30), that the plunger (32) on the valve armature (20) is rotatable about a common longitudinal axis. Solenoid valve after Claim 10 , characterized in that a hollow-cylindrical main body (52) of a pull ring (50) rotatably connected to a second receiving portion (25) of the base body (22) of the valve armature (20), which in the direction of the pole core (11) after the first receiving portion (24 ) and having a larger outer diameter than the first receiving portion (24), wherein the base body (52) of the pull ring (50) has a fifth guide geometry (54) which cooperates with the first guide geometry (47) of the control cage (41) and the Valve armature (20) during its axial movement and prevents a rotational movement of the valve armature (20), and a sixth guide geometry (55) are formed, which cooperates with a on the plunger (30) formed seventh guide geometry (36) and a rotational movement of the plunger (30 ). Solenoid valve after Claim 11 , characterized in that the fifth guide geometry (54) on the hollow cylindrical base body (52) of the pull ring (50) connected second guide plates (54.1) which are toothed with the first guide tabs (47.1) of the first guide geometry (47), wherein the sixth Guide geometry (55) tensile claws (54.1), which are formed at the free ends of the second guide plates (54.1). Solenoid valve after Claim 12 , characterized in that the seventh guide geometry (36) of the plunger (30) comprises a circumferential groove (36.1), which is introduced at an end facing the pole core (11) in the base body (32), wherein the Zugkrallen (54.1) of sixth guide geometry (54) engage in the circumferential groove (36.1). Solenoid valve according to one of the Claims 10 to 13 , characterized in that at an in the at least one passage opening (41.1, 44.1) of the guide assembly (40) guided portion of the main body (32) of the plunger (30) an eighth guide geometry (39), which in an axial movement in the direction Polkern ( 11) with the third guide geometry (42) of the control cage (40) and with an axial movement in the direction of the valve seat (15.1) with the fourth guide geometry (45) of the control ring (44) cooperates, and a ninth guide geometry (38) are formed, which in the de-energized open position with the control cage (41) formed second guide geometry (48) cooperates. Solenoid valve after Claim 14 , characterized in that the eighth guide geometry (39) has at least one radially projecting positioning element (39.1) which is arranged on the main body (32) of the tappet (30), wherein the ninth guide geometry (38) comprises shoulders (38.1) which in uniform angular pitch on the base body (32) of the plunger (30) are arranged. Solenoid valve after Claim 15 , characterized in that the valve armature (20) at a caused by the magnetic force of the magnet assembly axial movement in the direction of pole core (11) the plunger (30) and its closing element (34) entrains, wherein the at least one positioning element (39.1) starting from a position in a second recess (46.1) meets a corresponding chamfer (43.3) of the control cage (41), whereby a circumferential force acts on the plunger (30) and rotates the plunger (20) about a corresponding longitudinal axis until the at least one positioning element (39.1) slides at the end of the chamfer (43.3) in a corresponding first recess (43.1), wherein in the axial movement of the valve armature (20) in the direction of the valve seat (15.1) caused by the spring force of the return spring (16) the at least one positioning element (39.1) first recess (43.1) meets a corresponding chamfer (46.3) of the control ring (44), whereby a circumferential force acting on the plunger (30) and further rotates the plunger (30) about the corresponding longitudinal axis until the at least one positioning element (39.1) slides at the end of the chamfer (46.3) into a corresponding second recess (46.1). Solenoid valve after Claim 16 , characterized in that in the de-energized open position the at least one positioning element (39.1) is guided in a corresponding second recess (46.1) of the fourth guide geometry (46) and at least one shoulder (38.1) of the ninth guide geometry (38) on a corresponding support region (38). 48.1) of the second guide geometry (48) rests, wherein in the de-energized closed position the at least one positioning element (39.1) is guided in a corresponding first recess (43.1) of the third guide geometry (43) and all paragraphs (38.1) of the ninth guide geometry (38) in cage recesses (47.2) are guided and the closing element (34) sealingly in the valve seat (15.1) is applied. Hydraulic brake system (1) for a vehicle, with a master cylinder (5), a hydraulic unit (9) and a plurality of wheel brakes (RR, FL, FR, RL), wherein the hydraulic unit (9) at least two brake circuits (BC1, BC2) for brake pressure modulation in the wheel brakes (RR, FL, FR, RL), characterized in that the at least two brake circuits (BC1, BC2) each have at least one bistable solenoid valve (10), which according to at least one of Claims 1 to 17 is executed and in the de-energized open position, the brake pressure modulation in at least one associated wheel brake (RR, FL, FR, RL) releases and in the de-energized closed position includes a current brake pressure in the at least one associated wheel brake (RR, FL, FR, RL).

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