DE102014115206B3 - Tilting tank valve for a pressure control module of a vehicle and method for operating a tipping armature valve - Google Patents

Abstract

The present invention relates to a tilting-armature valve (118) for a pressure-regulating module (102) of a vehicle (100), comprising at least one coil element (340) comprising at least one coil core (350) and a coil (352) arranged radially around the coil core (350), an armature (342) mounted on an end face of the armature (342) by means of a bearing (354), the armature (342) being activated by activating the spool (352) from a first position (356) in a second position (342). 358) is movable, a spring (344) for moving the armature (342), wherein a first portion (360) of the spring (344) on a coil element (340) facing side of the armature (342) is arranged and a force the armature (342) is exerted to move the armature (342) towards the first position (356), and a second portion (362) of the spring (344) is located on a side of the armature (342) facing away from the coil element (340) is arranged, a sealing element (346), which at the the coil element (340) abgegewa a half-shell (348) in which a valve seat (364) is formed with an outlet (366) and an inlet (368) for a fluid, the outlet (366) in the first Position (356) of the armature (342) by means of the sealing element (346) is fluid-tightly closed.

Description

The present invention relates to a dump tank valve for a pressure control module of a vehicle and a method for operating a dump tank valve.

Braking systems for a vehicle having an electronic service brake system include, for example, at least one control valve for pressure control. Control valves with a cylindrical basic structure may comprise a valve element comprising a movable cylindrical piston with a sealing element and separate stopper rubber. The valve seats and the connection area are manufactured in plastic injection molding.

The publication DE 10 2006 030 468 B3 shows a solenoid valve.

The publication DE 33 46 290 A1 also shows a solenoid valve.

It is the object of the present invention to provide an improved control valve for a pressure control module of a vehicle.

This object is achieved by a tilting-armature valve for a pressure-regulating module of a vehicle and a method for operating a tilting-armature valve according to the independent claims. Advantageous embodiments emerge from the respective subclaims and the following description.

By a Kippankerprinzip with a lateral anchor bearing the moving mass of Kippankerventils can be kept very low. Furthermore, a largely homogeneously distributed magnetic field can be generated by means of a coil which acts on the armature via a coil core. A spring generates a counterforce or a valve closing force.

A dump tank valve for a pressure control module of a vehicle comprises at least:
a coil element comprising at least one coil core and a coil arranged radially around the coil core;
an armature supported on an end face of the armature by means of a bearing, the armature being movable from a first position to a second position by activating the spool;
a spring for moving the armature, wherein a first portion of the spring is disposed on a side facing the coil element of the armature and exerts a force on the armature to move the armature in the direction of the first position, and a second portion of the spring on a The coil element facing away from the armature is arranged;
a sealing element which is arranged on the side facing away from the coil element of the armature; and
a half-shell, in which a valve seat with an outlet and an inlet for a fluid are formed, wherein the outlet in the first position of the armature by means of the sealing element is fluid-tightly closed.

A vehicle may be understood to mean a vehicle having an electronic or pneumatic service brake system. Under the vehicle, a truck or a rail vehicle can be understood. In this case, the vehicle may have a pressure control module. In this case, the pressure control module may be part of the electronic service brake system. The coil element may have an interface for receiving a control signal. The control element may be configured to generate a magnetic field upon application of a control signal or in response to the control signal. The tipping armature valve may be configured to direct an input fluid to the outlet. In this case, a fluid flow can be controlled by the position of the armature. It is advantageous to use the Kippankerventils as normally open or inlet / outlet valve, as a normally closed, for example, for a backup application or a universal use as a changeover or change-over valve possible.

Furthermore, the bearing may be formed as a sliding bearing. It is also favorable if the bearing is designed as a needle bearing or the bearing comprises a needle roller. Thus, advantageously, a low-friction armature suspension (for example, <0.1 N) can be created with a low-wear armature bearing. A needle bearing can offer a precise anchor guide. The needle roller may have a diameter of less than three millimeters. The needle roller may have a diameter within a tolerance range of two and a half millimeters. In this case, the needle roller made of a hardened metal, such as steel, be made.

It is also favorable if the needle roller is connected rotationally fixed to the coil element. Furthermore, the needle roller can be connected in a rotationally fixed manner to a further half shell which at least partially surrounds the coil element. In this case, the needle roller can be connected to the coil element or to the further half shell, in particular by laser welding. The needle roller can essentially comprise a magnetically non-conductive material. The armature, with a bearing half shell formed in the armature, in which the needle roller can be guided, can essentially comprise a magnetically conductive material. The additional half shell may also have at least one magnetically conductive material.

The spring may be formed as a wire bending part. Thus, the spring can be produced inexpensively and take only a small amount of space. Advantageously, the spring can be easily adapted to the available space.

The Kippankerventil may have a damper element which is arranged on the side facing the coil element of the armature. In this case, the damper element can be designed to damp a mechanical oscillation of the armature, in particular a vibration and / or a vibration and / or a shock, during a movement of the armature into the second position. The damper element can be arranged centrally on the armature. So the damper element can act on the spool core. The damper element can be arranged on the armature in such a way that it acts on a movement of the armature into the second position on the coil, an end face of the coil or a perforated disk arranged on an end side of the coil. Thus, the damper element may be arranged on a side facing away from the bearing end on a coil facing the main surface of the armature.

The damper element and the sealing element may be formed integrally or from two (preferably the same) individual parts. Thus, the damper element and the sealing element can be mounted in one step. Also manufacturing advantages are achievable, for example, a cost-effective production.

Furthermore, the damper element and the sealing element may be at least partially formed from an elastomer. Thus, the damper element and the sealing element may be at least partially formed from a rubber. Thus, advantageous sealing and damping properties can be achieved.

Furthermore, the coil element can be arranged in a further half-shell. In this case, the half-shell and the further half-shell can be fluid-tightly interconnected. The half-shell and the further half-shell can advantageously provide a housing for the tilting-armature valve. In the further half-shell, a connection or an interface for the coil can be provided.

It is also favorable if the half-shell is not magnetically conductive. Furthermore, the additional half-shell and additionally or alternatively the armature can be magnetically conductive. Thus, a magnetic field emanating from the coil can be passed favorably. If the half-shell is magnetically non-conductive, so unfavorable forces can be avoided by an unwanted magnetic force in an unwanted direction to the anchor.

The half shell and the further half shell may at least partially comprise steel. Thus, a plurality of elements of the tilting tank valve can be made of a robust, low-wear material.

In the coil element or the further half-shell, a bearing half-shell may be formed as a bearing element of the bearing for receiving the armature or the needle roller. The bearing half-shell may be formed as a groove so that the needle roller or a corresponding bulge of the anchor can be accommodated therein. Thus, a bearing element can be created inexpensively.

The anchor may be at least partially made or formed from a stamped sheet. Furthermore, the anchor may at least partially comprise steel. Thus, a robust element of the tilting tank valve can be manufactured inexpensively.

The armature may be formed as a bearing element of the bearing. Thus, the anchor for receiving the needle roller may be formed. For example, the armature may have a bearing half shell configured to receive the needle roller. Thus, in a favorable embodiment, the needle roller can be guided between two bearing half-shells, wherein the two bearing shells are formed in the armature and the coil element or the other half-shell. Alternatively, the armature can have a bearing element which can engage directly in a bearing half-shell formed in the coil element or the further half-shell and can form a bearing.

The spring may be configured to exert a closing force on the armature in a direction away from the coil element. Thus, the spring can exert a force on the armature in the direction of the first position. The force acting on the armature from the activated coil on the armature in the direction of the second position may be greater than the force exerted by the spring in the direction of the first position. Thus, with the bobbin deactivated, the armature can be moved in the direction of the first position and, with the bobbin activated, in the direction of the second position. When the coil is activated, the armature can be held in the second position.

The spring may have at least one side wing that is configured to guide the bearing, the armature or the needle roller vertically. In particular, the at least one side wing can be designed to guide the bearing, the armature or the needle roller vertically by means of an end-side spring support. The side wing may advantageously be designed to guide a plurality of elements vertically. In In a favorable embodiment, the spring may have at least two side wings.

Further, the spring may comprise at least one support portion which is configured to compress the bearing, wherein a supporting force is exerted by the half-shell on the support portion. Thus, the spring may be formed to compress bearing elements of the bearing such as bearing shells and needle roller.

In this case, the spring may be at least partially formed mirror-symmetrical. So a sturdy tipping anchor valve can be created. So all functions of the spring can be performed redundantly. A breakage of the spring can thus be compensated by the redundant spring section. Advantageously, a robust and fail-safe Kippankerventil is created.

An opening can be formed in the armature for the passage of a fluid channel or a fluid channel tube. This makes it easy to adapt a valve function of the tilting-armature valve. For example, the fluid channel for a valve can be used as an opener. A common part concept can enable larger production lots. In the anchor, a second opening for the passage of fluid can be created. For example, this opening can be used to allow passage of the fluid from the inlet to the valve interior located above the armature in the case of a valve used as an opener. The opening for passage of the fluid and the fluid channel may also be provided when the valve is designed as an inlet / outlet valve.

In the Kippankerventil can be arranged radially around the spool at a side facing the armature end of the coil, a perforated disc. The lock washer may be formed as a spacer ring or a spacer disk or perform the function of a spacer ring or a spacer disk. Thus, advantageously, a common part concept can be implemented.

The perforated disc can have a fluid channel. In this case, the perforated disc can be formed from at least a first perforated disc and a second perforated disc. In this case, the first perforated disk and additionally or alternatively the second perforated disk can be manufactured as a deep-drawn part. The first perforated disc and the second perforated disc can be connected to each other, for example by means of laser welding. The first perforated disc and the second perforated disc may be made of steel. The perforated disc can be connected, for example, by means of laser welding to the further half shell and, in addition or alternatively, to the coil core. In this case, a fluid-tight connection can be created. This can also be achieved a fluid-tight delimitation of the coil relative to the fluid-loaded valve interior.

The fluid channel may have a valve opening as a fluid connection, which can be closed by the damper element. When positioning the armature in the second position, the valve opening of the fluid channel can be closed fluid-tight by the damper element. Thus, the Kippankerventil can be designed as an opener, a change-over or shuttle valve.

Furthermore, the fluid channel can have a valve opening as an outlet for a backup valve, wherein at the outlet a fluid channel tube is arranged, which connects the outlet of the fluid channel with an outlet in the half shell. The fluid channel tube may have a diameter of less than 5 millimeters. In particular, the fluid channel tube may have a diameter of 3 millimeters plus a tolerance range. For example, the wall thickness of the fluid channel tube may be less than 0.6 millimeters. For example, the wall thickness of the fluid channel tube may be substantially 0.3 millimeters. In this case, the fluid channel pipe can be made of steel.

It is also favorable if a fine sieve is arranged at the inlet for the fluid. So dirt particles can be filtered out before they penetrate into the tipping armature valve.

It is also favorable if the armature has two legs connected to the front side. Thus, the armature may have a first leg and a second leg. The two legs can be separated by a slot. In this case, the legs can be connected to each other in the area of the bearing, so that the anchor can be considered as split by the two legs. The anchor with the two legs can be made in one piece. The split anchor, for example, manufactured as a split anchor plate, creates a height tolerance compensation different high valve seats. The armature may have a pitch in at least two legs, so that a first leg of the armature is connected via a narrow elastic connecting web with a second leg of the armature. A leg can be understood as a segment. Thus, the armature may have a division into two or more segments, so that a part of the armature is connected only via a narrow elastic connecting web with the adjacent other part.

Further, the Kippankerventil next to the first sealing element may have a second sealing element. The first sealing element can be attached to the side of the armature facing away from the coil element a first leg of the two legs may be arranged. The second sealing element may be arranged on the side of the armature facing away from the coil element on a second leg of the two legs. So simply a double switching valve can be created. The dump tank valve may be used with at least two pressure circuits for safety applications requiring redundancy, for example. Thus, in one embodiment of a tilting anchor valve described here, which is used for example in a two-channel pressure control module, a second backup valve can be saved.

In the half-shell, a first valve seat with a first outlet for a fluid, a first input for the fluid, a second valve seat with a second outlet for the fluid or another fluid and a second inlet for the fluid or the further fluid may be formed. In the first position of the armature, the first outlet by means of the first sealing element and the second outlet by means of the second sealing element can be closed in a fluid-tight manner.

The perforated disc can have two fluid channels. The first fluid channel of the two fluid channels can have a first valve opening as the first fluid port, which can be closed by the damper element. The second fluid channel of the two fluid channels can have a second valve opening as a second fluid port, which can be closed by the second damper element. When positioning the armature in the second position, the first valve opening of the fluid channel can be closed in a fluid-tight manner by the damper element and the second valve opening of the fluid channel by the second damper element. Thus, the Kippankerventil can be designed as an opener, a change-over or shuttle valve. The first valve opening may be arranged on a first fluid channel of the two fluid channels, the second valve opening may be arranged on a second fluid channel of the two fluid channels.

Furthermore, the fluid channel may have a first valve opening as a first outlet for a first backup valve and a second valve opening as a second outlet for a second backup valve, wherein a first fluid channel tube is arranged at the first outlet and a second fluid tube at the second outlet. In particular, the first fluid channel may have a first valve opening as a first outlet for a first backup valve and the second fluid channel a second valve opening as a second outlet for a second backup valve. The first fluid channel tube may connect the first outlet to a first outlet in the half shell. The second fluid channel tube may connect the second outlet to a second outlet in the half shell. It is also possible to provide two valve openings, which open into a shared fluid channel and discharge the fluid flowing through a shared fluid channel tube.

In an unloaded rest position of the armature, a first distance between the first valve seat and the first sealing element may be less than a second distance between the second valve seat and the second sealing element. Thus, the anchor may have a height-related slight displacement of the two anchor halves. Thus, a height-related displacement of the first leg of the armature can be formed to the second leg of the armature. With a weak activation, only one side can open. With a full control, a large switching cross section can be achieved. This means that both valves can be open when fully activated. Thus, a drive can provide more than two positions of the armature. For example, in a coarse / fine solenoid valve, as in a clutch plate, a halving of the number of valves can be achieved.

In an unloaded rest position of the armature, the first leg on a side facing away from the end side may have a smaller distance from the coil element than the second leg. In the unloaded rest position of the armature, the first valve seat may have a smaller distance to the coil element than the second valve seat to the coil element. Thus, a height offset can be formed between the first valve seat and the second valve seat. Alternatively or additionally, a height offset can be formed between the first leg and the second leg. The height offset may be less than 2 mm, in particular, the height offset may be less than 1 mm.

In addition to or instead of a height offset between the first leg and the second leg, a first valve seat may have a passage opening which is smaller in cross-section than the second valve seat. Alternatively or additionally, the spring of the first anchor leg, which has a smaller valve seat opening cross-section, have a lower closing force than the spring on the side of the armature leg with the valve seat having a larger cross section. As a result, when a magnetic field is applied through the coil, the leg of the armature having the smaller spring force opens earlier than the side with the stronger spring force. It is the same at the end of a current through the coil, which causes a reduction of the magnetic holding force. The side-related different spring force in the first portion causes a later fall of the armature on the armature side with the lower spring force. If the later-opening sealing element is reduced in its valve opening cross-section, a better fine gradation of the pressure reduction can be achieved.

A method for operating a tilting-armature valve according to a variant of a tilt-armature valve presented here is presented, wherein a signal for actuating the coil is provided to an interface of the tilting-armature valve in order to set a valve position. Also by this embodiment of the invention in the form of a method, the object underlying the invention can be solved quickly and efficiently.

Preferred embodiments of the present invention will be explained in more detail below with reference to the accompanying drawings. Show it:

1 a schematic representation of a vehicle with a pressure control module according to an embodiment of the present invention;

2 a schematic representation of a valve element for a pressure control module of a vehicle;

3 a schematic representation of a tilting tank valve according to an embodiment of the present invention

4 a schematic cross-sectional view of a Kippankerventils according to an embodiment of the present invention;

5 a schematic cross-sectional view of an energized Kippankerventils with marked magnetic flux according to an embodiment of the present invention;

6 a schematic representation in a view from below of a Kippankerventils according to an embodiment of the present invention;

7 a schematic sectional view of a Kippankerventils according to an embodiment of the present invention;

8th a schematic representation in a view from below of an energized Kippankerventils with marked magnetic flux according to an embodiment of the present invention;

9 a schematic representation of an energized Kippankerventils with perforated disc according to an embodiment of the present invention;

10 a schematic detail of a needle bearing of a Kippankerventils according to an embodiment of the present invention;

11 a schematic representation in a view from below of a Kippankerventils according to an embodiment of the present invention;

12 a schematic representation of a de-energized Kippankerventil with perforated disc according to an embodiment of the present invention;

13 a schematic representation in a view from below of a powered Kippankerventils according to an embodiment of the present invention;

14 a schematic representation of a de-energized Kippankerventils with a formed in a perforated disc fluid channel according to an embodiment of the present invention;

15 a schematic representation of a perforated disc of a Kippankerventils in a view from below according to an embodiment of the present invention;

16 a schematic sectional view of a perforated disc according to an embodiment of the present invention;

17 a schematic sectional view of a perforated disc according to an embodiment of the present invention;

18 a schematic sectional view of a perforated disc according to an embodiment of the present invention;

19 a schematic representation of a spring of a Kippankerventils according to an embodiment of the present invention;

20 a flowchart of a method for operating a tilting tank valve according to an embodiment of the present invention;

21 a simplified 3D representation of another half-shell of a tilting tank valve according to an embodiment of the present invention;

22 a simplified schematic sectional view through a further half-shell of a tilting tank valve according to an embodiment of the present invention;

23 a schematic representation in a view from below of a Kippankerventils as Doppelumschaltventil according to an embodiment of the present invention;

24 a schematic representation of a Kippankerventils as double switching valve according to an embodiment of the present invention;

25 a schematic representation of a perforated disc of a Kippankerventils as Doppelumschaltventil in a view from below according to an embodiment of the present invention;

26 a schematic detail of a needle bearing of a Kippankerventils according to an embodiment of the present invention; and

27 a schematic detail of a needle bearing a Kippankerventils according to an embodiment of the present invention.

In the following description of the preferred embodiments of the present invention, the same or similar reference numerals are used for the elements shown in the various drawings and similar, and a repeated description of these elements will be omitted.

1 shows a schematic representation of a vehicle 100 with a pressure control module 102 according to an embodiment of the present invention. In the embodiment shown, it is the vehicle 100 around a truck 100 , The pressure control module 102 is part of an electronic service brake system 104 with at least one brake cylinder 106 and the brake cylinder 106 associated pressure control module 102 , The pressure control module 102 , also as DRM 102 or control valve 102 denotes, has a working chamber 108 and a control chamber 110 on. Furthermore, the pressure control module comprises 102 an inlet solenoid valve 112 , an outlet solenoid valve 114 as well as a backup valve 116 , The inlet solenoid valve 112 , the outlet solenoid valve 114 as well as the backup valve 116 are as variants of a dump tank valve 118 executed.

The control chamber 110 is via the inlet solenoid valve 112 with a storage air tank 120 connected. Further, the working chamber 108 to the storage air tank 120 connected. For pressure reduction is the control chamber 110 via the outlet solenoid valve 114 and optionally a muffler, not shown, with the atmosphere 122 connected. By operation of inlet solenoid valve 112 or outlet solenoid valve 114 During braking, a predetermined by the electronic brake control pressure in the control chamber 110 adjusted. The pressure in the control chamber 110 regulates via a valve 124 the pressure in the working chamber 108 , At the valve 124 it can be a relay valve. The control chamber 110 The pressure control module is also via a backup line and the backup solenoid valve 116 with a conventional backup system 126 connected, in which a pressure applied via a pneumatic foot brake valve during braking. This is used in case of failure of the electrical pressure control still braking the vehicle 100 to enable. These are the inlet solenoid valve 112 and the outlet solenoid valve 114 closed in the de-energized state, the backup solenoid valve 116 is open when de-energized. Corresponding embodiments of the tilting tank valve 118 are shown and described in the following figures.

2 shows a schematic representation of a valve element 230 for a pressure control module of a vehicle. The pressure control module may be a variant of an in 1 shown pressure control module 102 act. The valve element 230 has a predominantly cylindrical basic structure. In this case, the valve element comprises 230 a movable cylindrical piston 231 with a sealing element 232 and a separate stop rubber 233 , On a housing 234 of the valve element 230 are at least a valve seat 235 as well as a connection area 236 educated. The at least one valve seat 235 as well as the connection area 236 are made of plastic injection molding.

3 shows a schematic representation of a Kippankerventils 118 according to an embodiment of the present invention. At the tipper tank valve 118 it may be an embodiment of an in 1 shown tilting tank valve 118 act. The dump tank valve 118 has a coil element 340 , an anchor 342 , a feather 344 , a sealing element 346 as well as a half shell 348 on. In this case, the coil element comprises 340 at least one spool core 350 and a coil disposed radially around the spool core 352 , An end face of the anchor 342 is by means of a warehouse 354 stored. The anchor 342 is between a first position 356 and a second position 358 movable. Here is the anchor 342 formed when activating the coil 352 from the first position 356 in the second position 358 to be moved. When the coil is activated 352 can the anchor 342 in the second position 356 being held. Here is the spring 344 trained, a force in the direction of the first position 356 on the anchor 342 exercise. So can the anchor 342 with the coil deactivated 352 in the first position 356 being held. A first subarea 360 the feather 344 is on one of the coil element 340 facing side of the anchor 342 arranged. A second subarea 362 the feather 344 is on one of the coil element 340 opposite side of the anchor 342 arranged. On the coil element 340 opposite side of the anchor 342 is still the sealing element 346 arranged.

In the half shell 348 is a valve seat 364 with an exit 366 and an entrance 368 formed for a fluid. This is the output 366 by means of the sealing element 346 fluid-tight lockable when the anchor 342 in the first position 356 is arranged.

4 shows a simplified cross-sectional view of a Kippankerventils 118 according to an embodiment of the present invention. At the tipper tank valve 118 it may be an embodiment of an in 1 or 3 shown tilting tank valve 118 act. It may be in a variant to a in 1 with the reference number 112 provided inlet solenoid valve act.

The dump tank valve 118 indicates one of the half shell 348 and another half shell 470 formed housing on. In one embodiment, the half shell 348 and the other half shell 470 connected fluid-tight to each other by laser welding. In the other half shell 470 is a coil element 340 arranged. The coil element 340 includes a spool core 350 and a coil disposed annularly around the spool core 352 , The other half shell 470 is through the coil element 340 almost completely filled. The coil element 340 has a connection 472 for receiving a control signal 474 on. Depending on the status of the control signal 474 becomes the coil 352 switched off or energized. In the other half shell 470 is on one side a first bearing half shell 476 for a needle roller 478 educated. At an end face of the coil element 340 or the coil 352 is adjacent to the first bearing half shell 476 an anchor 342 arranged. In the anchor 342 is a second bearing half shell 480 educated. The first bearing half shell 476 , the needle roller 478 as well as the second bearing half shell 480 make up a camp together 354 ,

At the anchor 342 is a spring 344 arranged. A first subarea 360 the feather 344 is on the coil element 340 facing side of the anchor 342 arranged. A second subarea 362 the feather 344 is on the coil element 340 opposite side of the anchor 342 arranged. In the embodiment shown here is at the spring 344 around a wire bending element.

In the half shell 348 is an entrance 368 and in a valve seat 364 an exit 366 educated. It is at the exit 366 a fine sieve 482 arranged. For example, the fine sieve 482 with the half shell 348 connected by a process using resistance welding.

At the anchor 342 is a sealing element 346 and a damper element 484 arranged. The sealing element 346 is on the coil element 340 opposite side of the anchor 342 arranged. Furthermore, the damper element 484 on the coil element 340 facing side of the anchor 342 arranged. In the illustrated embodiment, the sealing element 346 and the damper element 484 integrally formed. Both the sealing element 346 as well as the damper element 484 are made in one embodiment of an elastomer such as rubber.

The anchor 342 is in a first position 356 shown. In the first position 356 is the sealing element 346 the kind to the valve seat 364 arranged that this is sealed fluid-tight. In this case, in the illustrated embodiment, the anchor 342 an angle of 2 ° to the half shell 348 or to the end face of the coil element 340 on. A surface of the valve seat 364 at which the sealing element 346 abuts when the anchor 342 in the first position 356 is arranged, has an angle of 2 ° to the main extension plane of the half-shell 348 on.

In the in 4 illustrated embodiment is on the end face of the coil element 340 a perforated disc 486 arranged. In this case, the perforated disc 486 a breakthrough in the diameter of the spool core 350 on. The perforated disc 486 is with the other half shell 470 as with the spool core 350 connected. Here, in a favorable embodiment, the perforated disc 486 the kind with the further half shell 470 and the spool core 350 connected to that coil 352 fluid-tight of one of the half-shell 348 created space in which the anchor 342 is arranged, is separated. The perforated disc 486 consists of a magnetically non-conductive material. Also the half shell 348 preferably consists of a magnetically non-conductive material.

This in 4 shown tilting tank valve 118 is based on a basic principle of an electrical relay. Except the coil 352 In one embodiment, the elements of the tilting tank valve 118 made of steel. Advantageously, these are thus high temperature resistant and have a high surface quality. An anchor bearing is a needle roller 478 similar to how it is used in classic needle roller bearings. The spring manufactured in one embodiment from a form bending wire 344 fixes both the anchor 342 as well as generates the spring 344 a valve closing force of the tilting tank valve 118 , Both from the half shell 348 and the other half shell 470 formed housing as well as the anchor 342 are punched or deep-drawn sheets. Advantageously, the items of Kippankerventils 118 connected by laser welding.

By arranging a round coil 340 in a largely round further half shell 470 Magnetic circuit optimization is carried out by a largely homogeneously distributed magnetic field. So follows the arrangement of the coil 340 in the other half shell 470 together with the anchor 342 a pot-lid principle and leads to a coil and cost minimization. In addition to the in 4 illustrated basic principle of Kippankerventils 118 as a closer or an inlet / outlet valve is shown as examples in the following figures, also a configuration of the tilting tank valve 118 as an opener, for example, for a backup application or as a changer for universal use easily feasible.

The tilting tank valve shown here 118 creates an affordable overall solution through optimal utilization of magnetic force with minimum coil and housing size. The robust basic concept is characterized by a high resistance to shaking due to the half-shell bearing as well as the possible high number of cycles. The high switching numbers are, for example, due to the large bearing contact surface with a small distance to be covered by the anchor 342 created.

In one embodiment, the spring 344 formed mirror-symmetrically. That's the way the pen points 344 a symmetrical spring contour. This can advantageously be achieved by redundant suspension high reliability. As in the 14 to 19 can represented by two additional punched deep-drawn parts and a fluid channel tube, the Kippankerventil 118 configured and used for a backup solution.

The tilting tank valve described here 118 is characterized by a simple assembly, a low moving anchor mass, a low-friction armature suspension and a low-wear armature bearing. As explained in more detail in subsequent figures, is formed by the combination of a needle bearing and a spring designed as a spring shape 344 achieved a precise anchor guide. Both the armature stroke and the valve seat 364 are easy to adapt. The executed as a wire bending part spring 344 provides both a valve closing force and a guide for accurate anchor positioning.

5 shows a schematic cross-sectional view of a powered Kippankerventils 118 with marked magnetic flux 590 according to an embodiment of the present invention. The illustration of the tilting tank valve 118 in 5 corresponds to the representation of the tilting tank valve 118 in 4 , with the difference that the anchor 342 in the second position 358 is positioned since the coil 352 is in an energized state. A dashed line shows the magnetic flux 590 around the coil 352 , The magnetic flux 590 is essentially over the bobbin 350 and the other half shell 470 directed. A magnetic force acts on the armature 342 and moves it to the second position 358 or alternatively, the magnetic force holds the armature 342 in the second position 358 , The coil core 350 , the other housing shell 470 and the anchor 342 consist of a magnetically conductive material.

If the anchor 342 in the second position 358 is positioned, so is the output 366 released and the tipper armature valve 118 switched to passage or flow.

6 shows a schematic representation in a view from below of a Kippankerventils 118 according to an embodiment of the present invention. At the tipper tank valve 118 it can be a in 4 or 5 shown tilting tank valve 118 act. The anchor 342 is from the half shell 348 edged. In the embodiment shown, the anchor is made as a punched embossing sheet. The anchor 342 has two notches in mirror symmetry 692 on, through which the mirror-symmetric spring 344 is led for a page change. The needle roller 478 gets into one in the anchor 342 trained bearing half shell out. A length of the needle roller 478 corresponds largely to a diameter or extension of the armature 342 , The formed as a wire bending part spring 344 is shaped such that the anchor 342 is fixed in the storage area. A vertical guide of the anchor 342 is achieved by a frontal spring support.

To increase the robustness of the bearing, the needle roller because of the limited enclosure in the housing shell z. B. be fixed by laser welding. The movement of the warehouse 354 thus finds itself only in the optimally enclosed storage area between anchors 342 and needle roller 478 instead of.

The sealing element 346 sometimes referred to as a valve element or valve rubber, and the damper element 484 are in the embodiment shown in one piece designed as a laterally plug-in unit. The unit of sealing element 346 and damper element 484 is in one in the anchor 342 formed blind hole arranged.

The sealing element 346 and damper element 484 may alternatively be inserted as a single similar plug-in elements in a respective hole of the anchor. The rubber can be vulcanized into a kind of pans made of deep-drawn sheet metal.

In the illustration in 6 are shown two cutting axes. A first cutting axis A runs horizontally in the middle. A corresponding to 6 Corresponding sectional view is in 7 shown. A second section axis B runs parallel to the first section axis A and shows a plan view of the bearing 354 , wherein the vertical guide by the spring 344 is better to recognize. A corresponding sectional image on the second cutting axis B is in 10 shown.

7 shows a schematic sectional view of a Kippankerventils 118 according to an embodiment of the present invention. The representation in 7 shows a section along the first section axis A of an in 6 illustrated Kippankerventils 118 , The anchor 342 is arranged in the first position. This is the illustrated tilting tank valve 118 in a powerless state. The valve seat 364 has a slope in a tolerance range of 2 °. The valve seat 364 is in the half shell 348 educated. The half shell 348 creates a housing bottom for the tilting tank valve 118 , The half shell 348 is not magnetically conductive. The straight running anchor 342 is formed as a punch-embossed part. At the entrance 368 is a fine sieve 482 arranged. The sealing element 346 and the damper element 484 are made in one piece.

8th shows a schematic representation in a view from below of a powered Kippankerventils 118 with marked magnetic flux 590 according to an embodiment of the present invention. The dump tank valve 118 corresponds to the in 6 illustrated tilting tank valve 118 , with the difference that the spring 344 has a different shape, the notches 692 at a different position in the anchor 342 are formed and the anchor 342 an opening 894 for performing a fluid channel. Behind the anchor 342 is a perforated disc 486 arranged.

The damper element 484 , the sealing element 346 and the entrance 368 are arranged along the first section line A. The first section line A corresponds to a mirror axis for the spring 344 , In the in 8th illustrated embodiment is the spring 344 formed mirror-symmetrically.

The perforated disc 486 has a support area 693 on. In the support area 693 is supported in a mounted state in a Kippankerventil, as described in the preceding figures, a spring of the Kippankerventils to exert a corresponding force on the armature of the Kippankerventils can.

The feather 344 has two side wings 896 on. The side wings 896 are trained, the camp 354 and the anchor 342 to lead vertically. The vertical guidance of the bearing 354 and the anchor 342 is by a frontal spring support of the side wings 896 achieved. Furthermore, the spring 344 two support sections 898 on. The support sections 898 are trained, the camp 354 compress. This is a supporting force of the half shell 348 on the support section 898 exercised.

8th shows the dump tank valve 118 in an energized state, the magnetic flux 590 symbolized by arrows. The magnetic flux runs in the armature towards the middle.

9 shows a schematic representation of an energized Kippankerventils 118 with perforated disc 486 according to an embodiment of the present invention. The representation in 9 shows a section along the first section axis A of an in 8th illustrated Kippankerventils 118 , The anchor 342 is in the second position 358 arranged. This is the illustrated tilting tank valve 118 in an energized state.

The perforated disc 486 differs from the illustrations in 4 to 7 a profile on. So takes the perforated disc 486 in comparison to the aforementioned embodiments, a larger space. The perforated disc 486 creates a stop for the damper element 484 if the anchor 342 in the second position 358 is arranged, or is moved into this. Such a trained perforated disk 486 offers the advantage that a common part concept can be easily implemented. This is how a tilting tank valve configured as a backup valve differs 118 essentially through another perforated disc and an additional connection. Corresponding embodiments are from 14 shown.

10 shows a schematic detail of a needle bearing a Kippankerventils 118 according to an embodiment of the present invention. The representation in 10 shows a section along the second section axis B of an in 9 illustrated Kippankerventils 118 , The warehouse 354 is from the first bearing half shell 476 , the needle roller 478 and the second half bearing 480 educated. The anchor 342 includes the second half bearing 480 , The first bearing half shell 476 is in the other half shell 470 formed. The feather 344 has a side wing 896 and a support section 898 on. The side wing 896 is at the front of the needle roller 478 arranged. A point of contact 1001 the spring support on the side wall of the half-shell 348 is preferably formed directly in a line to the pivot point of the armature in the camp. So the touch point 1001 as a fulcrum 1001 be designated. The support section 898 is at one of the needle roller 478 opposite side of the second half bearing 480 arranged. Both the side wing 896 as well as the support section 898 make curved sections of the spring 344 dar. The perforated disc 486 is over a weld 1000 with the other half shell 470 connected. In the specific embodiment, it is the weld 1000 around a laser weld 1000 , The other half shell 470 is over a weld 1000 with the half shell 348 connected.

There is a transition of the magnetic flux 590 from the anchor 342 on the right side of the needle roller 478 over in the other half shell 470 instead of. The needle roller 478 itself consists of magnetically non-conductive material. In particular, the transition of the magnetic flux 590 in the area of the first bearing half shell 476 and the second half bearing 480 clear.

11 shows a schematic representation in a view from below of a Kippankerventils 118 according to an embodiment of the present invention. The presentation largely corresponds to the representation in 8th , with the difference that a representation of the magnetic flux is dispensed with.

12 shows a schematic representation of a de-energized Kippankerventils 118 with perforated disc 486 according to an embodiment of the present invention. The illustration of the tilting tank valve 118 corresponds to the representation of the tilting tank valve 118 in 9 , with the difference that the anchor 342 in the first position 356 is positioned since the coil 352 is not energized. Thus, from the coil 352 no force on the anchor 342 exercised and the pen 344 pushes the anchor 342 in the direction of the first position 356 ,

13 shows a schematic representation in a view from below of a powered Kippankerventils 118 according to an embodiment of the present invention. The illustration of the tilting tank valve 118 in 13 corresponds to the representation of the tilting tank valve in 8th with the difference that the position of the entrance 368 from a position on the first cutting axis A to a mirror-symmetrical arrangement with respect to the first cutting axis A with respect to the opening 894 is changed.

At the same position in plan view here is another opening 1394 in the anchor 342 intended. This opening is used to pass through the entrance 368 incoming air to the top of the anchor 342 towards the in 14 illustrated valve 1404 ,

14 shows a schematic representation of a de-energized Kippankerventils 118 with one in a perforated disc 486 trained fluid channel 1402 according to an embodiment of the present invention. The dump tank valve 118 is largely the same as in 12 illustrated tilting tank valve 118 , with the difference that in the perforated disc 486 a fluid channel 1402 is trained. The fluid channel 1402 has a valve opening 1404 on, passing through the damper element 484 is closable. The one in the perforated disc 486 trained fluid channel 1402 is through a first perforated disc 1406 and a second perforated disc 1408 formed, wherein at least one of the two perforated discs 1406 . 1408 has a profile or contour between the first perforated disc 1406 and the second perforated disc 1408 the fluid channel 1402 shaped. In the in 14 illustrated embodiment, the second perforated disc 1408 such a profile. So it is at the second perforated disc 1408 for example, a punched deep-drawn part or a punched embossing sheet. In the embodiment shown, the first perforated disc 1406 and the second perforated disc 1408 to the perforated disc 486 welded.

In 14 is the anchor 342 in the first position 356 positioned. The anchor 342 closes the exit 366 , If the anchor 342 in the second position 358 is positioned, so in the perforated disc 486 shaped valve opening 1404 locked.

The feather 344 has in a rotational axis of the bearing or the needle roller on a portion with a large bend, which is directed away from the needle roller. This creates together with a side wall of the half shell 348 a point of contact 1001 the spring support.

15 shows a schematic representation of a perforated disc 486 a tipping armature valve in a view from below according to an embodiment of the present invention. The tilting tank valve may be an embodiment of an in 14 shown tilting tank valve 118 act. The perforated disc 486 is between the outer shell acting as a housing outer wall 470 and the spool core 350 the tilting tank valve can be arranged, or arranged. In a favorable embodiment, the perforated disc 486 with the other half shell 470 and the spool core 350 about one in 15 not shown weld, in particular fluid-tight, connected. The perforated disc 486 has a fluid channel 1402 on, with a valve opening 1404 , Furthermore, the fluid channel 1402 with a fluid channel tube 1510 connected. The fluid channel 1402 and the fluid channel tube 1510 are interconnected so that one through the valve opening 1404 in the fluid channel 1402 inflowing fluid through the fluid channel tube 1510 flows. The fluid channel pipe 1510 is also referred to as a tube or fluid channel. In a favorable embodiment, the fluid channel is 1510 essentially made of steel. Advantageously, this is a magnetically non-conductive steel.

The perforated disc 486 has a support area 693 on. In the support area 693 is supported in a mounted state in a Kippankerventil, as described in the preceding figures, a spring of the Kippankerventils to exert a corresponding force on the armature of the Kippankerventils can.

A round, dashed line around the valve opening 1404 shows a valve seat for the backup valve. Using the perforated disc shown here 486 can be described in the preceding figures Kippankerventil 118 as an opener valve for a backup application or a changeover valve, as in 14 shown to be configured.

The representation in 15 shows three section lines A, B, C. Corresponding detailed representations of the perforated disc 486 are in the following three figures 16 . 17 such as 18 shown. The first section line A passes through the valve opening 1404 , The second section line B passes through a not further changed region of the fluid channel 1402 , The third cutting line C passes through the connection of the fluid channel 1402 to the fluid channel tube 1510 ,

16 shows a schematic sectional view of a perforated disc 486 according to an embodiment of the present invention. At the perforated disc 486 it may be an embodiment of an example in 15 illustrated perforated disk 486 act. The representation of the perforated disc 486 in 16 corresponds to a section along the first section line A in FIG 15 , The perforated disc 486 forming first perforated disc 1406 and second perforated disc 1408 are between a half-shell forming a side wall 470 as well as the spool core 350 arranged. In the second perforated disc 1408 is a valve opening 1404 formed. Between the first perforated disc 1406 and the second perforated disc 1408 is a fluid channel 1402 formed.

In a favorable embodiment of an in 16 illustrated perforated disk 486 has the first perforated disc 1406 in a tolerance range of 10%, a thickness of 1 mm. At the second perforated disc 1408 it is a deep-drawn part. The second perforated disc 1408 has a thickness of 0.5 mm in a tolerance range of 10%. The valve opening 1404 is formed as a substantially round hole with a diameter of in a tolerance range of 10% 1.5 mm. The fluid channel 1402 points in the area of the valve opening 1404 within a tolerance range of 10% a height of 2 mm.

17 shows a schematic sectional view of a perforated disc 486 according to an embodiment of the present invention. At the perforated disc 486 it may be an embodiment of an example in 15 illustrated perforated disk 486 act. The representation of the perforated disc 486 in 17 corresponds to a section along the second section line B in FIG 15 , The perforated disc 486 forming first perforated disc 1406 and second perforated disc 1408 are between a half-shell forming a side wall 470 as well as the spool core 350 arranged. The first perforated disc 1406 , the second perforated disc 1408 as well as the half shell 470 are over a weld 1000 connected with each other. Comparable are the first perforated disc 1406 , the second perforated disc 1408 as well as the spool core 350 over a weld 1000 connected with each other. In a favorable embodiment, the weld creates 1000 a fluid-tight connection between the elements.

Analogous to the perforated disk described in the two preceding figures 486 has the fluid channel 1402 in the area of the second section line B in a tolerance range of 10%, a height of 1 mm.

18 shows a schematic sectional view of a perforated disc 486 according to an embodiment of the present invention. At the perforated disc 486 it may be an embodiment of an example in 15 illustrated perforated disk 486 act. The representation of the perforated disc 486 in 18 corresponds to a section along the third section line C in FIG 15 , The perforated disc 486 forming first perforated disc 1406 and second perforated disc 1408 are between a half-shell forming a side wall 470 as well as the spool core 350 arranged. The second perforated disc 1408 is with a fluid channel tube 1510 connected. In a favorable embodiment, it is in the fluid channel tube 1510 around a thin stainless steel tube, with a diameter of substantially 3 mm with a wall thickness of in a tolerance range of 10% 0.3 mm. The fluid channel pipe 1510 is about welds 1000 with the half shell 348 connected. Likewise, the fluid channel pipe 1510 over welds 1000 with the second perforated disc 1408 connected. As shown in the two preceding figures, the first perforated disc 1406 and the second perforated disc 1408 each with welds 1000 connected to each other, at the same time a fluid-tight connection with the spool core 350 or of a housing for the Kippankerventil forming half shell 470 is created.

19 shows a schematic representation of a spring 344 a dump tank valve according to an embodiment of the present invention. At the spring 344 it can be a Embodiment of a spring described in the preceding figures 344 for a dump tank valve 118 act. With the spring shown here 344 it is a wire bending part. In a preferred embodiment, the spring 344 integrally formed and mirror-symmetrical. The spring is preferred 344 at least partially made of steel. Further, the spring 344 made according to one embodiment of a magnetically non-conductive material.

In the in 19 illustrated embodiment, the spring 344 at least three sub-areas, each of the three sub-areas is performed twice. A first subarea 360 the feather 344 can be arranged on a side facing a coil element of an armature of a Kippankerventils. A second subarea 362 can be arranged on a side facing away from the coil element of the armature. The first section 360 is configured to exert a force or closing force on the armature in order in an assembled state of the armature 342 and the spring 344 to move the armature in the direction of a first position, or to move in the direction of the opposite side of the armature. Between the first section 360 and the second subsection 362 There is a (strongly) curved section that passes through a notch 692 in the anchor 342 is feasible to the paging of the subareas 360 . 362 the feather 344 to enable. The first two sections 360 the feather 344 collide with each other and are interconnected. To the second section 362 then follows a side wing 896 , In the area of the side wing 896 is the spring 344 curved. The side wing 896 is formed, the bearing or the anchor 342 to lead the Kippankerventils by a frontal spring support. The point of contact 1001 the spring support on the side wall of the half-shell 348 is preferably directly in line with the pivot point of the armature in the bearing. To the side wing 896 This is followed by a support section 898 , The support section 898 is formed of a first straight section, a curved section and a second straight section. The first straight section closes to the side wing 896 at. The first straight portion of the support portion is locatable on the bearing of the tilting anchor valve to compress the elements of the bearing. The second straight section of the support section 898 is on the housing or the half-shell of Kippankerventils be arranged lying. In this case, a supporting force of the half-shell on the support portion 898 exercised.

20 shows a flowchart of a method 2000 for operating a dump tank valve according to an embodiment of the present invention. The tilting-armature valve may be a variant of a tilt-armature valve described in the preceding figures. The procedure 2000 provides a signal to drive the spool to an interface of the dump tank valve to adjust a valve position. The signal may be a current signal. Thus, the coil of the tipping armature valve can be energized or de-energized. Thus, in response to the signal, a position of the armature of the tilting armature valve can be adjusted. In response to the signal, the valve position can be adjusted. For example, the method 2000 one step 2020 of the driving, wherein in step 2020 the drive, a signal for driving the coil is provided to an interface of the tilting tank valve to adjust the valve position.

21 shows a simplified 3D representation of another half-shell 470 a dump tank valve according to an embodiment of the present invention. The tilting tank valve may be an embodiment of an example in 3 4 or 14 act shown tilting tank valve. In the other half shell 470 are a perforated disc 486 and a coil core 350 arranged. In the perforated disc 486 is a fluid channel 1402 educated. The fluid channel 1402 has an opening 1404 on. Furthermore, the fluid channel 1404 with a fluid channel tube 1510 connected. In the other half shell 470 is a first bearing half shell 476 designed to receive a needle roller.

At the spool core 350 it is a circular cylindrical body. The perforated disc 486 closes to the outer surface of the spool core 350 at. The fluid channel 1402 has an annular shape. The in the fluid channel 1402 trained opening 1404 is at the first bearing half shell 476 most remote area of the fluid channel formed. At the opening 1404 it can be a hole. A length of the first bearing half shell 476 corresponds to a tolerance of 10% an outer diameter of the perforated disc 486 ,

A section line D symbolizes a sectional plane that leads through the middle of the other half shell. A corresponding sectional view is in the following figure 22 shown.

22 shows a simplified schematic sectional view through another half-shell 470 a dump tank valve according to an embodiment of the present invention. At the other half shell 470 can it be in the 22 shown additional half shell 470 act.

To a coil core 350 is a coil 352 arranged. The sink 352 includes a bobbin 2232 and a coil carrier 2234 , Furthermore, around the spool core is a perforated disc 486 arranged. The perforated disc 486 is at one end of the coil 352 arranged. Both the coil 350 as well as the perforated disc 486 are with the outer surface of the spool core 350 connected. Furthermore, at least the perforated disc 486 with the other half shell 470 connected. In this case, the perforated disc includes 486 a first perforated disc 1406 and a second perforated disc 1408 , Between the first perforated disc 1406 and the second perforated disc 1408 is a fluid channel 1402 educated. In the second perforated disc 1408 is an opening 1404 formed.

The other half shell 470 has a first bearing half shell 476 on. This is formed as a groove in the other half-shell. The first bearing half shell 476 is adapted to receive a needle roller or a correspondingly shaped anchor and to provide a bearing.

23 shows a schematic representation in a view from below of a Kippankerventils as a double switching valve according to an embodiment of the present invention. The dump tank valve 118 corresponds to the in 8th illustrated tilting tank valve 118 , with the difference that the anchor 342 two through a slot 2314 separate thighs 2316 having. The two thighs 2316 are in the area of the camp 354 connected with each other. This connection is designed so elastic that the two mirror-symmetrical sides of the armature are easily displaced in their vertical movement. This compensates for a tolerance-related height compensation of the two valve seat positions. The sealing element 346 is on a first leg 2316 the two legs arranged, a second sealing element 2346 is on a second leg 2316 the two legs arranged. The damper element 484 is on the first leg 2316 arranged, a second damper element 2384 is on the second leg 2316 arranged. The sealing element 346 and the damper element 484 are on two opposite sides of the first thigh 2316 staggered to each other. The second sealing element 2346 and the second damper element 2384 are on two opposite sides of the second leg 2316 staggered to each other. In this case, in the embodiment shown, the sealing element 346 and the damper element 484 made in one piece as a plug-in unit. The unit of sealing element 346 and damper element 484 is in one in the anchor 342 in the first leg 2316 formed blind hole arranged. Furthermore, the second sealing element 2346 and the second damper element 2384 made in one piece as a plug-in unit. The unit of second sealing element 2346 and second damper element 2384 is in one in the anchor 342 in the second leg 2316 formed blind hole arranged.

The slot 2314 between the two thighs 2316 points in the in 23 shown embodiment on a T-shape. Such a remaining connecting web between the two legs creates an elastic connection, so that the two legs create a height compensation.

A first cutting axis A runs horizontally in the middle. A corresponding to 23 Corresponding sectional view along the first cutting axis A centered by the sealing element 346 and the damper element 484 is in 24 shown. A second section axis B runs parallel to the first section axis A and shows a plan view of the bearing 354 , wherein the vertical guide by the spring 344 is better to recognize. A corresponding sectional image on the second cutting axis B is in 10 shown.

The anchor 342 is from the half shell 348 edged. In the embodiment shown, the anchor is made as a punched embossing sheet. The anchor 342 is along a mirror axis, which corresponds to the sectional axis A, through the slot 2314 in two mutually symmetrical legs 2316 divided, which are connected to each other at the front. Furthermore, the anchor points 342 mirror-symmetrical two notches 692 on, through which the mirror-symmetric spring 344 is led for a page change. In the area of the front is in the anchor 342 a bearing half shell formed in which a needle roller 478 to be led. This corresponds to a length of the needle roller 478 largely a diameter of the anchor 342 ,

The feather 344 has two side wings 896 on. The side wings 896 are trained, the camp 354 and the anchor 342 to lead vertically. The vertical guidance of the bearing 354 and the anchor 342 is by a frontal spring support of the side wings 896 im, the side wall of the half shell 348 touching bearing pivot point 1001 achieved. Furthermore, the spring 344 two support sections 898 on. The support sections 898 are trained, the camp 354 compress. This is a supporting force of the half shell 348 on the support section 898 exercised.

The anchor 342 points in the first leg 2316 an opening 894 for performing a fluid channel. Mirror symmetrical to the first axis A of the second leg 2316 a second opening 2394 for performing a fluid channel. Behind the anchor 342 is a perforated disc 486 arranged.

The perforated disc 486 has a support area 693 on. In the support area 693 rests in a mounted state of the tilting tank valve 118 like this in the previous figures is described, the spring 344 of the tipping armature valve 118 to apply an appropriate force to the anchor 342 of the tipping armature valve 118 to be able to exercise.

24 shows a schematic representation of a Kippankerventils 118 as a double switching valve according to an embodiment of the present invention. The representation in 24 shows a section along the first section axis A of an in 23 illustrated Kippankerventils 118 , The anchor 342 is in the first position 356 arranged. This is the illustrated tilting tank valve 118 in a powerless state. The dump tank valve 118 points in the in 24 embodiment shown a perforated disc 486 on. The perforated disc 486 has a profile. This is in the perforated disc 486 at least one fluid channel 1402 with at least one valve opening 1404 educated. In the following 25 will be apparent that the perforated disc 486 two separate fluid channels 1402 each with a valve opening 1404 having, wherein the fluid channels 1402 each with a tube 1510 are connected. It is also possible, on the one hand two valve openings 1404 . 2504 as in 23 provided on the other hand, however, as in 25 not visible, only one shared fluid channel 1402 to accomplish. Here, on the second fluid channel pipe 2510 be waived. Analogously, it is also possible to have two outputs 366 to create and to choose an anchor, which two sealing elements 346 . 2346 having.

The perforated disc 486 creates a stop for the damper element 484 , In the sectional picture in 24 is not shown directly that the perforated disc 486 also a stop for the second damper element 2384 creates. As described in the preceding figures, the perforated disc 486 a support area 693 on.

The dump tank valve 118 includes in 24 at least one coil element 340 , an anchor 342 , a feather 344 , a sealing element 346 , a damper element 484 as well as a half shell 348 , The coil element 340 includes at least one coil core 350 and a coil disposed radially around the spool core 352 , At the anchor 342 is the sealing element 346 and the damper element 484 arranged. The sealing element 346 is on the coil element 340 opposite side of the anchor 342 arranged. Furthermore, the damper element 484 on the coil element 340 facing side of the anchor 342 arranged. In the illustrated embodiment, the sealing element 346 and the damper element 484 integrally formed. Both the sealing element 346 as well as the damper element 484 are made in one embodiment of an elastomer such as rubber. The rubber of the sealing and damping element may be surrounded by a sheet-metal deep-drawn part, wherein only the end-side support or sealing surface is free from the sheet metal cover. This allows a more rational and thus cheaper production by means of multiple vulcanization can be achieved. At the same time the rubber element has a stable side wall, whereby a better dimensional stability of the sealing and damping element is achieved with frequent valve actuation.

An end face of the anchor 342 is by means of a warehouse 354 stored. The anchor 342 is between a first position 356 and a second position 358 movable. Here is the anchor 342 formed when activating the coil 352 from the first position 356 in the second position 358 to be moved. When the coil is activated 352 can the anchor 342 in the second position 356 being held. Here is the spring 344 trained, a force in the direction of the first position 356 on the anchor 342 exercise. So can the anchor 342 with the coil deactivated 352 in the first position 356 being held. A first subarea 360 the feather 344 is on one of the coil element 340 facing side of the anchor 342 arranged. A second subarea 362 the feather 344 is on one of the coil element 340 opposite side of the anchor 342 arranged.

In the half shell 348 is at least a valve seat 364 and an entrance 368 formed for a fluid. In the sectional picture in 24 not visible is that in the half shell 348 a second valve seat and a second inlet for the fluid is formed. An exit 366 in the valve seat 364 is by means of the sealing element 346 fluid-tight lockable when the anchor 342 in the first position 356 is arranged. The entrance 368 is over the pipe 1510 with the fluid channel 1402 connected. Not shown is that the second input is connected via a second tube to the second fluid channel.

In an optional, not shown embodiment is in an unloaded rest position of the armature 342 a first distance between the first valve seat 364 and the first sealing element 346 is less than a second distance between the second valve seat and the second sealing element. Alternatively, the first leg in an unloaded rest position of the anchor 342 a smaller distance to the coil element 340 as the second leg up. Optionally, the first valve seat 364 a smaller distance to the coil element 340 as the second valve seat to the coil element 340 ,

In addition to or instead of this height offset between the first leg and the second leg, a first valve seat 366 have a smaller cross-sectional passage opening than the second valve seat. Alternatively or additionally, the spring 344 of the first anchor leg 2316 , which has a smaller valve seat opening cross section has a lower closing force than the spring on the side of the armature leg 2316 with the cross-sectionally larger valve seat. This opens when applying a magnetic field through the coil 352 the leg of the armature with the lower spring force earlier than the side with the stronger spring force 360 , The same applies to the valve seat 486 at the end of a current supply through the coil 352 , which causes a degradation of the magnetic holding force. The page-related different spring force in the first section 360 causes a later fall of the anchor 342 in the direction of position 356 on the side of the armature with the lower spring force 360 , This later opening valve 484 can have a larger opening cross section. This improves the accuracy of a fine control for an exhaust valve.

25 shows a schematic representation of a perforated disc 486 a tipping armature valve as a double switching valve in a view from below according to an embodiment of the present invention. The tilting tank valve may be an embodiment of an in 23 or 24 shown tilting tank valve 118 act. The perforated disc 486 is between the outer shell acting as a housing outer wall 470 and the spool core 350 the tilting tank valve can be arranged, or arranged. In a favorable embodiment, the perforated disc 486 with the other half shell 470 and the spool core 350 about one in 25 not shown weld, in particular fluid-tight, connected and the perforated disc 486 has a first fluid channel 1402 with a first valve opening 1404 and a second fluid channel 2502 with a second valve opening 2504 on. Furthermore, the first fluid channel 1402 with a first fluid channel 1510 connected. The second fluid channel 2502 is with a second fluid channel 2510 connected. The first fluid channel 1402 and the first fluid channel tube 1510 are interconnected such that one through the first valve opening 1404 in the first fluid channel 1402 inflowing fluid through the first fluid channel tube 1510 flows. The same applies to the mirror-symmetrical second fluid channel tube 2502 , the second fluid channel pipe 2510 and the second valve opening 2504 , So are the second fluid channel 2502 and the second fluid channel tube 2510 connected to each other such that a through the second valve opening 2504 in the second fluid channel 2502 inflowing fluid through the second fluid channel tube 2510 flows. The fluid channel pipes 1510 . 2510 are also referred to as pipe or fluid channel. In a favorable embodiment, the fluid channel tubes 1510 . 2510 essentially made of steel. It is advantageous both in the perforated disc 486 as well as the pipe 1510 . 2510 around a magnetically non-conductive steel.

The perforated disc 486 has a support area 693 on. In the support area 693 is supported in a mounted state in a Kippankerventil, as described in the preceding figures, a spring of the Kippankerventils to exert a corresponding force on the armature of the Kippankerventils can.

The representation in 25 shows three section line A, B, C. Corresponding detailed representations of the perforated disc 486 are in previous figures 16 . 17 such as 18 shown. The first section line A passes through the valve opening 1404 . 2504 , The second section line B passes through a not further changed region of the fluid channel 1402 . 2502 , The third cutting line C passes through the connection of the fluid channel 1402 . 2502 to the fluid channel tube 1510 . 2510 ,

26 shows a schematic detail of a needle bearing a Kippankerventils according to an embodiment of the present invention. The representation in 26 corresponds largely to the representation in 10 , with the difference that the needle roller 478 with the first bearing half shell 476 over two welds or points 1000 is rotationally connected. In the specific embodiment, it is the weld 1000 around a laser weld 1000 , The needle bearing corresponds to a detailed view along the second section line B of a tilting tank valve 118 like these in previous figures such as 6 . 8th . 11 or 13 is drawn. The warehouse 354 is from the first bearing half shell 476 , the needle roller 478 and the second half bearing 480 educated. The anchor 342 includes the second half bearing 480 , The first bearing half shell 476 is in the other half shell 470 formed. A side wing of the spring 344 is at the front of the needle roller 478 arranged. A point of contact 1001 the spring support on the side wall of the half-shell 348 is preferably formed directly in a line to the pivot point of the armature in the camp. So the touch point 1001 as a fulcrum 1001 be designated.

There is a transition of the magnetic flux 590 from the anchor 342 at the anchor 344 substantially opposite side of the needle roller 478 over in the other half shell 470 instead of. The needle roller 478 itself consists of magnetically non-conductive material. In particular, the transition of the magnetic flux 590 in the area of the first bearing half shell 476 and the second half bearing 480 clear. The first bearing half shell touches each other 476 and the second bearing half shell 480 if the anchor 344 , as in 26 shown in the first position 356 located. Alternatively, in an embodiment, not shown, between the first half bearing shell 476 and the second bearing half shell 480 a small gap formed when the anchor 344 is in the first position. The gap gets bigger when the anchor 344 from the first position 356 in the second position 358 emotional.

27 shows a schematic detail of a needle bearing a Kippankerventils according to an embodiment of the present invention. The representation in 27 corresponds to the illustration in 26 , with the difference that the anchor 344 in 27 in the second position 358 is arranged, whereas in 26 the anchor 344 in the first position 356 is arranged. Clearly visible, and highlighted by an arrow, is a gap between the first bearing half shell 476 and the second half bearing 480 at the anchor 344 substantially opposite side of the needle roller 478 ,

At the needle roller 478 In the exemplary embodiment, this is a hardened needle roller 478 with a high surface quality. The needle roller 478 is in the thermoformed housing 470 welded, for example by means of three welding points. Thus, it is advantageously achieved that no bearing wear in the thermoforming housing 470 arises and optimum robustness is achieved by an unrestricted half shell-shaped bearing surface on the anchor side. In the in 27 illustrated embodiment is a horizontal armature guide through the form of spring 344 in the bearing pivot 1001 achieved, wherein the shape spring 344 at the half shell 348 formed outer wall is applied.

If the anchor 344 is in the first position, an anchor end is connected to the housing top, that is, the Kippankerventil has a flatter over the Zustuweg force / displacement characteristic as in cylindrical solenoid valves. It acts a larger tightening force at the beginning of the closing process and a closing force reduction in the closed state, that is a stroke force reduction. There is the possibility of a force / displacement characteristic determination.

The non-magnetic property of the needle roller 478 also causes a displacement of the magnetic force away from the area of the bearing 354 towards an increase of the magnetic force laterally and opposite the bearing 354 , This also increases the initial closing force at the beginning of the energization of the valve.

The described embodiments are chosen only by way of example and can be combined with each other.

LIST OF REFERENCE NUMBERS

100

vehicle

102

Pressure control module

104

electronic service brake system

106

brake cylinder

108

working chamber

110

control chamber

112

Inlet solenoid valve

114

Outlet solenoid valve

116

Backup valve

118

Kippankerventil

120

Air reservoir

122

the atmosphere

124

Valve

126

Backup system

230

valve element

231

cylindrical piston

232

sealing element

233

rubber stop

234

casing

235

valve seat

236

terminal area

340

coil element

342

anchor

344

feather

346

sealing element

348

half shell

350

Plunger

352

Kitchen sink

354

camp

356

first position

358

second position

360

first subarea

362

second subarea

364

valve seat

366

output

368

entrance

470

another half shell

472

connection

474

control signal

476

first bearing half shell

478

needle roller

480

second bearing half shell

482

fine screen

484

damper element

486

perforated disc

590

magnetic flux

692

score

693

support area

A

first cut line

B

second cut line

894

opening

896

wing

898

support section

1000

Weld

1001

Touch point, fulcrum

1394

Opening, hole in anchor for fluid passage

1402

fluid channel

1404

valve opening

1406

first perforated disc

Claims (15)

Tilting tank valve ( 118 ) for a pressure control module ( 102 ) of a vehicle ( 100 ), having at least the following features: a coil element ( 340 ) comprising at least one coil core ( 350 ) and one radially around the spool core ( 350 ) arranged coil ( 352 ); an anchor ( 342 ), which at one end face of the anchor ( 342 ) by means of a warehouse ( 354 ), wherein the armature ( 342 ) by activating the coil ( 352 ) from a first position ( 356 ) into a second position ( 358 ) is movable; a spring ( 344 ) for moving the anchor ( 342 ), with a first subregion ( 360 ) the feather ( 344 ) on a coil element ( 340 ) facing side of the anchor ( 342 ) and a force on the armature ( 342 ) exercises the anchor ( 342 ) in the direction of the first position ( 356 ) and a second subsection ( 362 ) the feather ( 344 ) on a coil element ( 340 ) facing away from the armature ( 342 ) is arranged; a sealing element ( 346 ), which at the the coil element ( 340 ) facing away from the armature ( 342 ) is arranged; and a half-shell ( 348 ), in which a valve seat ( 364 ) with an output ( 366 ) and an entrance ( 368 ) is designed for a fluid, wherein the output ( 366 ) in the first position ( 356 ) of the anchor ( 342 ) by means of the sealing element ( 346 ) is closed fluid-tight. Tilting tank valve ( 118 ) according to claim 1, wherein the bearing ( 354 ) is designed as a plain bearing, and / or wherein the spring ( 344 ) is designed as a wire bending part. Tilting tank valve ( 118 ) according to claim 1, wherein a needle roller ( 478 ) with the coil element ( 340 ) and / or with a coil element ( 340 ) at least partially enclosing further half shell ( 470 is rotationally connected. Tilting tank valve ( 118 ) according to one of the preceding claims, with at least one damper element ( 484 ), which at the the coil element ( 340 ) facing side of the anchor ( 342 ) is arranged, wherein the damper element ( 484 ) is formed during a movement of the armature ( 342 ) to the second position ( 358 ) a mechanical oscillation of the armature ( 342 ) to dampen. Tilting tank valve ( 118 ) according to claim 4, wherein the at least one damper element ( 484 ) and in which the at least one sealing element ( 346 ) are at least partially formed of an elastomer. Tilting tank valve ( 118 ) according to one of the preceding claims 3-5, wherein the coil element ( 340 ) in another half-shell ( 470 ) is arranged, wherein the half-shell ( 348 ) and the further half shell ( 470 ) are fluid-tightly interconnected. Tilting tank valve ( 118 ) according to one of the preceding claims 3-6, wherein the half-shell ( 348 ) and / or the further half shell ( 470 ) at least partially comprises steel. Tilting tank valve ( 118 ) according to one of the preceding claims 3-7, wherein the spring ( 344 ) is formed, a closing force in one of the coil element ( 340 ) leading away from the anchor ( 342 ) and / or where the spring ( 344 ) at least one side wing ( 896 ), which is designed, the bearing ( 354 ) and / or the anchor ( 342 ) and / or the needle roller ( 478 ) to lead vertically. Tilting tank valve ( 118 ) according to one of the preceding claims, wherein in the anchor ( 342 ) at least one opening ( 894 ) for carrying out a fluid channel ( 1402 ) and / or fluid channel tube ( 1510 ) is trained. Tilting tank valve ( 118 ) according to one of the preceding claims, in which radially around the coil core ( 350 ) at an anchor ( 342 ) facing end side of the coil ( 352 ) a perforated disc ( 486 ) is arranged. Tilting tank valve ( 118 ) according to claim 10, wherein the perforated disc ( 486 ) a fluid channel ( 1402 ), wherein at the output ( 366 ) a fluid channel tube ( 1510 ) is arranged, which the output of the fluid channel ( 1402 ) with an outlet in the half-shell ( 348 ) connects. Tilting tank valve ( 118 ) according to one of the preceding claims, in which the armature ( 342 ) two legs connected at the front side ( 2316 ), and / or a second sealing element ( 2346 ) at the coil element ( 340 ) facing away from the armature ( 342 ) on a second leg ( 2316 ) of the two legs ( 2316 ) is arranged. Tilting tank valve ( 118 ) according to claim 12, wherein in an unloaded rest position of the anchor ( 342 ) a first distance between the valve seat ( 364 ) and the first sealing element ( 346 ) is less than a second distance between a second valve seat and the second sealing element ( 2346 ) and / or wherein the first leg ( 2316 ) in an unloaded rest position of the anchor ( 342 ) a smaller distance to the coil element ( 340 ), as the second leg ( 2316 ) and / or the valve seat ( 364 ) a smaller distance to the Coil element ( 340 ) than the second valve seat to the coil element ( 340 ). Tilting tank valve ( 118 ) according to one of the preceding claims, in which a first valve seat ( 364 ) has a smaller cross-sectional passage opening than a second valve seat. Procedure ( 2000 ) for operating a tilting tank valve ( 118 ) according to one of the preceding claims, wherein a signal for driving the coil ( 352 ) to an interface of the tilting tank valve ( 118 ) is provided to adjust a valve position.

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