WO2007082816A1

WO2007082816A1 - Solenoid valve

Info

Publication number: WO2007082816A1
Application number: PCT/EP2007/050171
Authority: WO
Inventors: Christoph Voss; Christian Courth
Original assignee: Continental Teves Ag & Co. Ohg
Priority date: 2006-01-11
Filing date: 2007-01-09
Publication date: 2007-07-26
Also published as: DE102006013660A1

Abstract

The invention relates to a solenoid valve having a main valve stage and a pilot control stage, and having a magnet coil (1) and a magnet armature (3), wherein, in order to reduce the overall size and the electrical energy requirement, the magnet coil (1) is configured within the valve housing (6) as a plunger-type coil and the magnet armature (3) is configured as a plate armature which receives the valve closing elements (14, 24) of the pilot control stage and the main stage in a relatively movable manner within a stepped bore (28).

Description

Solenoid valve

The invention relates to a solenoid valve according to the preamble of patent claim 1.

From DE 100 10 734 Al a solenoid valve of the type specified is already known, with an externally mounted on the sleeve-shaped valve housing solenoid and a magnet armature extending between the valve spool in the valve housing to a valve housing closing magnetic core. The valve housing consists of a material which does not conduct the magnetic flux, which results in a large contact resistance in the region of the magnetic disk pushed onto the valve housing for the magnetic flux.

Further, the magnet armature is a rigidly mounted first valve closing member in the function of a pilot stage, which closes in the valve base position arranged in a second valve closing member valve seat. The second valve closure member takes over the function of the valve main stage and is normally held by the first valve closure member to a valve seat which is arranged in the bottom of the valve housing.

The chosen design requires a correspondingly high electrical energy requirement for the magnetic drive in order to fully release the main valve stage, the armature over a relatively large stroke both against the action of a arranged between the armature and the magnetic core compression spring and taking into account the hydraulic see pressure differences on the magnetic core to move.

Another disadvantage of the cited solenoid valve results due to its relatively large length.

Therefore, it is the object of the present invention, a small design of a solenoid valve of the specified type and energetically inexpensive to perform and thus to improve so that the aforementioned disadvantages do not occur.

This object is achieved according to the invention for the solenoid valve of the type indicated by the characterizing features of claim 1.

Other features, advantages and applications of the invention will become apparent in the following from the description of an embodiment with reference to several drawings.

Show it:

1 shows an embodiment of a solenoid valve in longitudinal section in the closed, electromagnetically non-energized switching position,

2 shows the solenoid valve according to FIG. 1 in an electromagnetically excited switching position, which is advanced compared to FIG. 1, in which a magnet armature bears against a step of a first valve closing member after bridging an armature partial stroke;

FIG. 3 shows the electromagnetic valve according to FIG. 1 in an electromagnetic state which is advanced with respect to FIG. table excited switching position in which after Ü- exceeded the Ankerteilhubs the first valve closing member is lifted from its valve seat,

FIG. 4 shows the solenoid valve according to FIG. 1 in an electromagnetically excited switching position, which is advanced with respect to FIG. 3, in which the magnet armature rests against the magnet core and a driver mounted on the magnet armature lifts a second valve closing member from its valve seat;

Figure 5 shows the solenoid valve of Figure 1 in a comparison with Figure 4 advanced electromagnetically excited switching position, in which the second valve closing member occupies its maximum opening stroke after hydraulic pressure compensation under spring force.

1, the structural design of the solenoid valve according to the invention will first be explained. The illustrated in longitudinal section, designed as a two-stage 2/2-way poppet valve solenoid valve has a cartridge designed in the valve housing 6, which has a received by a magnet armature 3 first and second valve closure member 24, 14. Both valve closing members 14, 24 are arranged concentrically on the valve longitudinal axis, wherein the second valve closing member 14 is concentric with a valve seat 8 in the valve housing 6 and the first valve closure member 24 is directed to a provided on the second valve closure member 14 valve seat 12.

In order to make both the magnetic force effect on the armature 3 as effectively as possible and to keep the height of the hydraulic valve as low as possible, the invention Magnet armature 3 disc or plate-shaped and the required for the actuation of the magnet armature 3 solenoid 1 integrated directly in the valve housing 6. The magnetic coil 1 is arranged in a magnetic flux conducting portion 5 of the valve housing 6 and fixedly connected to this section 5. Between the magnetic portion 5 and the corresponding end face of the armature 3, a changeable by the armature stroke axial gap 2 is provided, which is bridged during an electromagnetic excitation of the magnet armature 3 only axially on and axially exiting magnetic field lines.

The magnetic coil 1 is designed as a partially immersed by the pressure medium plunger coil, which is immersed in electromagnetic excitation of the armature 3 in a ringnutförmige recess 31 of the armature 3.

Further, the valve housing 6 has a magnetic flux non-conductive further portion 7, which bears liquid-tight at the periphery of the magnetic portion 5, to which the further portion 7 is formed as a cup-shaped deep-drawn part, which in the lower part of the executed on a press-fit valve seat 8 and a few Pressure medium channels 9, 10 receives.

Both sections 5, 7 of the valve housing 6 are designed as mutually fixed by a press fit cartridge-shaped housing halves, in which advantageously the solenoid coil 1 as a plunger space and magnetic force optimized integrated.

The by means of a self-restraint in the valve block 11 completely sunk fastened, to the atmosphere as a press-fit sealing portion 5 of the valve housing 6 is designed for use in high-pressure hydraulic systems and for receiving the caulking thick-walled and has for partially receiving the magnetic coil 1 adapted to the magnetic coil contour recess in which the solenoid 1 is accurately recorded and securely attached. The protruding from the section 5 in the direction of the axial gap 2 part of the solenoid coil 1 is acted upon directly by the liquid flowing through the valve housing 6, provided that a corresponding pressure supply into the valve housing 6 takes place. The magnetic coil 1 is therefore designed to be pressure-resistant and thus immersed liquid-flushed sections in the recess 31 of the armature 1 a.

The flush in the valve block 11 valve housing 6 thus consists only of two cartridge halves, the upper half of the housing is formed by the provided with the annular recess plug-shaped portion 5 and the lower half of the housing through the cup-shaped portion 7 which carries the valve seat 8.

For the electrical power supply of the solenoid coil 1 of the magnetic coil 1 receiving portion 5 is provided with an atmosphere-directed through hole 13 through which a connected to the magnetic coil 1 electrical contact 23 is passed gas and liquid tight.

Between the end face of the magnetic coil 1 and the end face of the recess 24, a sealing washer 15 is inserted, which advantageously the liquid-tight from the magnetic coil 1 protruding electrical contact 23 in the direction of the passage opening 13 in the valve housing 6 surrounds.

The coil turns and the contact 23 of the magnetic coil 1 connected to the coil turns are liquid on all sides. impermeable sealed by a pressure-resistant housing (eg plastic), which forms the bobbin. The magnetic coil 1 is either fixed in the recess of the section 5 or fixed non-positively or positively via a pressure-resistant plastic sheath of the contact 23 in the through hole 13 of the valve housing 6.

In order to allow for the valve housing 6 as cost-effective production, the recess 24 having portion 5 is formed as a cold impact part, the contour of which can be produced automatically by cold striking a magnetic flux conducting blank from which in a single operation advantageously the outside as well which is formed for receiving the magnetic coil 1 required inner contour.

Likewise, due to the chosen construction, the magnet armature 3 can also be produced in a simplified manner by extrusion or cold striking.

The individual components known from the cited prior art, such as a magnetic core, a non-ferromagnetic annular disc and a yoke ring enclosing the magnetic coil 1, can thus be integrated much more easily in the two-part valve housing 6 as a predominantly homogeneous unit with a reduced number of parts.

Furthermore, the solenoid valve has a cup-shaped portion 7 arranged on the filter element 27, which is designed as a ring filter element and prevents dirt entering via the pressure medium channel 9 in the valve housing 6.

The magnetic core is defined by the area of the magnetic Coil 1 enclosing section 5 formed in the center of the direction of the axial gap 2, a blind bore 16 opens, which receives a compression spring 17 which is clamped between the end face of the armature 3 and the end of the blind bore 16, whereby in the basic valve position of the armature with the valve-closing members 14, 24 in the valve seats 8, 12 closing switch position is held.

For precise centering of the magnet armature 3 in the valve housing 6 is in a centrally piercing the armature 3 penetrating stepped bore 28 sections of a sleeve-shaped guide member 29 is pressed, facing away from the magnet armature 3 sleeve end either on the outer circumference of the valve seat 8 having Einpresshülse or according to the figure along the on Section 7 sleeve-shaped bottom is guided.

In the stepped bore 28, both valve closing members 14, 24 are inserted in sections, wherein the second valve closing member 14 is accommodated in the region of its pipe section telescopically displaceable in the stepped bore 28. The valve closing member 14 extends under the action of a spring used in the stepped bore 28 19 with its pipe section to a bore stage in the stepped bore 28, wherein the spring 19 is clamped between a collar 32 on the pipe section and a stop fixed to the armature 3 stop 33, the Preferably, a component of the fixedly connected to the armature 3 guide member 29 is. This results in a telescope-like interaction of magnetic armature and valve closure member, to be able to cover the largest possible armature stroke with the lowest possible magnetic power requirement. The upper end of the pipe section on the second valve closing member 14 has the valve seat 12, which is closed by the first flap-shaped valve closure member 24. The first valve closure member 24 is guided between a cap 20 and the stepped bore 28 as well as the second valve closure member 14 in the armature 3 telescopically. The cap 20 is therefore fastened in the end region of the stepped bore 28 on the end face of the magnet armature 3 facing the axial gap 2.

The cap 20 is preferably made by deep drawing of thin sheet, provided with a pressure equalization hole and extends due to their height between the spring coils of the compression spring 17 space optimized in the blind bore 16th

Under the action of the compression spring 17 thus arranged in series with the second valve closing member 14 first valve closing member 24 in the electromagnetically non-energized magnet armature position closes the adjacent to the throttle bore 22 of the second valve closure member 14 valve seat 12th

The arranged between the sleeve-shaped driver 18 and the collar 26 spring 19 is dimensioned such that upon electromagnetic excitation of the armature 3, the valve closure member 14 remains on the valve seat 8, as long as the valve closure member 14 is not hydraulically pressure balanced. In order to establish the pressure equalization at the main stage forming the valve closing member 14 for the two-stage valve, the first valve closure member 24 acts as a pilot stage, the positively controlled by the Magnetankerhub the throttle bore 22 releases for pressure equalization.

In summary, the construction of the According to the electromagnetic valve according to the invention:

1. The armature 3 is designed to be relatively movable in the region of a defined anchor stroke relative to the first valve closure member 24, wherein the magnetic coil 1 is designed as a plunger coil.

2. The magnet armature 3 is provided with a recess 31 adapted to the diameter of the magnet coil 1, into which part of the magnet coil 1 protruding inside the valve housing 6 can be immersed.

3. The recess 31 is designed as embedded in the end face of the armature 3 annular groove whose depth is selected to be greater by at least the dimension of the axial gap 2 as the supernatant of the magnetic coil 1 within the valve housing. 6

4. For fluid equalization on both sides of the magnet armature 3 a plurality of symmetrically distributed in the armature 3 pressure compensation openings 32 are arranged, which are preferably inserted directly into the recess 31.

5. The magnet armature 3 is designed to be freely movable relative to the second valve closing member 14 via a defined armature stroke, to which end a driver 18 attached to the second valve closing member 14 with axial play is fastened to the magnet armature 3.

6. The driver 18 is designed as a fixed to the armature 3 sleeve through which the first valve closing member 14 extends in sections within a stepped bore 28 in the direction of the second valve closing body 8.

7. Both valve closing members 14, 24 are at least off taken in sections axially within a stepped bore 28 of the magnet armature 3, in which the driver 18 is attached.

8. On the end face of the magnet armature 3 remote from the driver 18, a cap 20 is secured into which the first valve closing member 24 extends.

9. The driver 18 has a sleeve-shaped guide member 29 formed on the end portion which is guided centrally to the longitudinal axis of the valve housing 6, whereby the armature 3 is centered in the valve housing 6.

10. Within the stepped bore 28 rests against a stop 25 of the driver 18, a spring 19 which is supported with its remote from the stop 25 spring end to a second valve closure member 14 arranged on the collar 26.

Taking into account the structural features of the e- lektromagnetventils according to Figure 1 follows with reference to the further Fig. 2-5, a functional description.

In the illustrated, non-energized solenoid valve position of Figure 1 take due to the closing force of the compression spring 17 whose spring force is larger than the force of the oppositely acting spring 19, both arranged in series connection valve closure members 14, 24 their illustrated valve closing positions. For this purpose, the push-type valve closure member 24 bears against the end wall on the inner wall of the cap 20 and presses the sleeve-shaped valve closure member 14 onto the valve seat 8. When the illustrated solenoid valve is preferably used in a slip-controlled brake system, there are generally no constant hydraulic pressures in the pressure medium inlet (horizon- Valve terminal 21) and pressure medium outlet (vertical valve connection 4), wherein the pressure in the pressure medium inlet generally predominates.

FIG. 2 shows the beginning of the electromagnetic excitation, according to which the armature 3 covers a partial lift until it contacts a step 30 provided on the first valve closing member 24. Both valve closing members 14, 24 initially remain in the closing pitch as a result of the magnetic armature partial stroke.

3 shows the armature 3 after bridging the partial stroke, after which the first valve closure member 24 is lifted from its valve seat 12 due to the positive connection between the step 30 and the stepped bore 28 of the armature 3, whereby in the sense of the pilot stage on the in the pipe section of the second Valve closing member 14 arranged throttle bore 22, a hydraulic pressure equalization takes place while the second valve closure member 14 still remains at its valve seat 8.

4 shows the magnet armature 3 after completion of the maximum possible armature stroke, in which the second valve closing member 14 is lifted slightly from its valve seat 8 due to the abutment of the collar 26 on the driver 18. The spring 19 remains initially ineffective until the hydraulic pressure compensation.

5 shows the second valve closing member 14 after completed hydraulic pressure equalization, whereby the spring 19 forces a lifting of the valve closing member 14 from the valve seat 8, so that in the sense of the main stage of the large passage cross-section between the valve closing member 14 and the valve seat 8 is opened maximum. To set the maximum opening To achieve the stroke of the valve closing member 14, the spring 19 moves via the second valve closing member 14, the first valve closure member 24 except for the upper stop in the cap 20th

The pressure fluid connection between the two valve ports 21, 4 is thus made resistant to resistance for a correspondingly large volume flow rate.

The advantage of the telescopic arrangement of the two valve closing members 14, 24 in the armature 3 is thus that in an electromagnetically initiated lifting movement of the armature 3 is initially covered to the concerns of the armature 3 at the plunger stage of the valve closure member 24 is already a partial lift from the armature 3, the the required to open the valve closing member 14 stroke and thus significantly reduced by the magnetic field to be bridged axial gap 2, so that after the pressure equalization through the throttle bore 22 with a relatively low magnetic force designed for a large volume flow valve closure member 14 via the driver 18 from the valve seat 8 accordingly can be easily lifted off.

With the measures described above, thus using a miniaturized solenoid coil 1 for the main valve stage, a large Ventilöffnungshub and the largest possible valve opening cross-section is guaranteed. LIST OF REFERENCE NUMBERS

1 solenoid

2 axial gap

3 magnetic armature

4 valve connection

5 section

6 valve housing

7 section

8 valve seat

9 pressure medium channel

10 pressure medium channel

11 valve block

12 valve seat

13 passage opening

14 valve closure member

15 sealing washer

16 blind hole

17 compression spring

18 drivers

19 spring

20 cap

21 valve connection

22 throttle bore

23 contact

24 valve closure member

25 stop

26 fret

27 filter element

28 stepped bore

29 guide member

30 level

31 deepening

32 pressure compensation opening

Claims

claims

A solenoid valve having a first and a second valve closure member disposed in a valve housing capable of opening or closing a first and a second valve seat in a coaxial arrangement in the valve housing, comprising a magnet armature forming an assembly with at least one of the two valve closure members with a compression spring, which is arranged between the magnet armature and a magnetic core of the valve housing, wherein the first valve closing member depending on the electromagnetic excitation of a solenoid can open or close a arranged on the second valve closing member valve seat whose passage cross-section is smaller than one of the second valve closing member openable valve seat, characterized in that the magnet armature (3) in the region of a defined armature stroke relative to the first valve closing member (24) is designed to be relatively movable, and that the magnetic coil (1) designed as a plunger coil is.

2. Electromagnetic valve according to claim 1, characterized in that the magnet armature (3) is provided with a to the diameter of the magnetic coil (1) adapted recess (31), in which a within the valve housing (6) projecting part of the magnetic coil (1). is submersible.

3. Electromagnetic valve according to claim 2, characterized in that the recess (31) is preferably designed as in the end face of the magnet armature (3) embedded annular groove whose depth is at least by the dimension of the axial gap (2) greater than the Ü overhang of the magnetic coil (1) within the valve housing (6).

4. Solenoid valve according to one of the preceding claims, characterized in that for liquid equalization on both sides of the armature (3) a plurality of symmetrically in the armature (3) distributed pressure equalization openings (32) are arranged, which are preferably inserted directly into the recess (31).

5. Electromagnetic valve according to one of the preceding claims, characterized in that the magnet armature (3) over a defined armature stroke is freely movable to the second valve closure member (14), including a second valve closure member (14) having axial play entrainment (18) on the armature (3) is attached.

6. Electromagnetic valve according to claim 5, characterized in that the driver (18) is designed as a sleeve on the armature (3) fixed sleeve through which the first valve closing member (14) sections within a stepped bore (28) in the direction of the second valve closing body (8) extends.

7. Electromagnetic valve according to claim 1, characterized in that both valve closing members (14, 24) are at least partially axially within a stepped bore (28) of the armature (3) are received, in which also the driver (18) is fixed.

8. Electromagnetic valve according to claim 7, characterized in that on the driver (18) remote End face of the armature (3) is fixed a cap (20) into which the first valve closing member (24) extends.

9. Electromagnetic valve according to one of the preceding claims, characterized in that the driver (18) has a preferably sleeve-shaped guide member (29) formed end portion which is guided centrally to the longitudinal axis of the valve housing (6), whereby the armature (3) in the valve housing (6) is centered.

10. Electromagnetic valve according to one of the preceding claims, characterized in that within the stepped bore (28) on a stop (25) of the driver (18) a spring (19) rests, with their from the stop (25) facing away from the spring end on the second valve closing member (14) arranged collar (26) is supported.