WO2016004920A2

WO2016004920A2 - Valve, in particular hydraulic valve

Info

Publication number: WO2016004920A2
Application number: PCT/DE2015/100279
Authority: WO
Inventors: Thomas Jacob; Michael BIERKOCH; Jürgen PEILER; Johannes Widmann
Original assignee: Hilite Germany Gmbh
Priority date: 2014-07-11
Filing date: 2015-07-03
Publication date: 2016-01-14
Also published as: WO2016004920A3; DE102015110733A1

Abstract

The invention relates to a valve (10), in particular a hydraulic valve (10) of a device carrying a fluid. Said valve comprises a valve bushing (12) having a passage (14), formed in the longitudinal direction (L) between an inlet opening (32) and an outlet opening (30), and a particulate filter (20), which is arranged on the inlet opening (32) of the passage (14). The outer edge (22) of said particulate filter (20) is connected in a fluid-tight fashion to a collar (34) arranged at an inlet opening (32) of the passage (14).

Description

Valve, in particular hydraulic valve

Technical area

The invention relates to a valve, in particular a hydraulic valve of a fluid-carrying device, in particular the mechatronics of a hydraulic control of a transmission of a motor vehicle, in particular a vent valve or a proportional control valve of mechatronics.

State of the art

From DE 10 2010 025 078 A1 a device for venting a leading from a pressure source to a consumer hydraulic line is known, which contains a between a pressureless and a pressurized state changing fluid. The apparatus includes a vent valve having an inlet opening in fluid communication with the hydraulic line and a conduit portion, a valve member, a first valve seat and a second valve seat, the valve member being movable in the conduit portion between a first position in which it on the first valve seat fluid-impermeable, and a second position in which it rests against the second valve seat. The hydraulic line is part of a transmission or a gear assigned, for example in a motor vehicle. The fluid is, for example, an oil.

From DE 10 2010 023 667 A1 a hydraulic valve with a valve housing is known. In the valve housing, a stepped bore is formed, the wall is finely machined. A stepped piston is arranged displaceably guided in the stepped bore. In the valve housing are two axially spaced apart radially into the stepped bore openings educated. A portion of the stepped piston has compared to the stepped bore on a reduced outer diameter, which forms a control groove, wherein two axially adjacent ports depending on the axial positioning of the stepped piston by the stepped piston shut off from each other and / or over the range reduced outer diameter are connected to each other.

DISCLOSURE OF THE INVENTION An object of the invention is to provide a valve, in particular a hydraulic valve for the mechatronics of a hydraulic control of a transmission of a motor vehicle, which ensures a very reliable mode of operation with a simple and cost-effective design. The above object is achieved according to one aspect of the invention with the features of the independent claims.

Favorable embodiments and advantages of the invention will become apparent from the other claims, the description and the drawings.

A valve, in particular a hydraulic valve, of a fluid-carrying device is proposed, which comprises a valve bushing with a passage formed in a longitudinal direction between an inlet opening and an outlet opening, and a particle filter which is arranged at the inlet opening of the passage. In this case, the particle filter is fluid-tightly connected at its outer edge with a collar arranged at an inlet opening of the passage.

To ensure the function of hydraulic valves, for example in mechatronic transmission control systems, it is necessary to keep dirt away from the valve to ensure the valve functions. Especially big ones Particles can lead to impairment of the valve function or failure due to blocking due to the small work gaps and running clearance. By a corresponding coarse dirt filter in the fluid flow of the valve such a malfunction can be prevented.

Therefore, according to the invention, the valve has a particle filter in order to keep dirt particles or abrasion away by the use, for example, in a transmission application of sensitive components, such as the mechatronics of a hydraulic control of a transmission of a motor vehicle. The fact that the particulate filter is an integral part of the valve, ensures that the valve is operated in any case only with filtered fluid and thus the functioning is not affected by any dirt particles or abrasion contained in the fluid. According to the invention a deep-drawn sieve is pressed as a particle filter in the valve sleeve to stop. By appropriate geometric design of the screen and the installation space in the valve with undercut the screen is fixed in the installation space. The hole size in the etched screen can be adapted to the sizes of particles to be kept from the interior of the valve.

The cost-effective particulate filter can be pressed into the valve bushing via a simple assembly on an existing system without significantly adversely affecting the external geometry of the valve. By appropriate geometric design of the screen and the installation space in the valve with undercut no additional security of the screen is necessary. The hole size in the sieve is variable and adaptable according to customer requirements. Such screens can be adapted to different installation space geometries due to the manufacturing process. Thus, the use is not limited to the use of a valve with a specific function. Advantageous for hydraulic applications are hole sizes of the particulate filter, for example 70 to 200 m. The particle filter thus prevents the passage of particles that are larger in all dimensions. Due to the radial contact of the plate sewer fire on the housing space, a passage of particles is prevented by bypassing the sieve structure. The undercut in the housing prevents falling out of the plate strainer from the installation space during assembly of the screen in the valve sleeve and operation of the valve, for example in the transmission. According to an advantageous embodiment of the particulate filter can be designed as a sieve, in particular as a plate sieve. The particle filter is preferably made of a metallic material such as steel sheet of wall thickness 0, 1 mm and has a plurality of sieve holes are made on and on the order of 70-200 μm diameter. The web width between the sieve holes can be for example 50 to 150 pm.

According to an advantageous embodiment of the particulate filter can be pressed or pressed into the collar. In this way, the particulate filter can be mounted easily and captive in the hydraulic valve.

According to an advantageous embodiment of the federal government may have an undercut for the axial fixation of the particulate filter in the pressed state. This ensures that the particle filter can not fall out when it is mounted.

According to an advantageous embodiment of the particulate filter can be arranged in the collar self-locking. Due to the axial self-locking of the particle filter remains fixed in its mounting position and captive. According to an advantageous embodiment of the particle filter may have on its outer edge a crank for clamping with the federal government. Thereby can the particle filter with a certain bias form, whereby the self-locking assembly behind the undercut of the federal can be carried out low. According to an advantageous embodiment, the particle filter has a multiplicity of sieve holes with an approximate aperture effect, which can be produced, for example, by an etching method. The design of the sieve holes as diaphragms, it is possible to reduce the temperature-dependent influences of the hydraulic fluid in the flow through the screen. The flow resistance is thus more dependent on the viscosity of the medium and less on the temperature. In addition, the pressure losses across the sieve are significantly reduced.

According to an advantageous embodiment, the valve may be formed as a vent valve for venting a device carrying a fluid. In this case, the valve may comprise a valve member arranged in the passage, which is supported by a spring which applies a spring force to a arranged in the passage and connected to the valve sleeve insert and the output port of the passage in a normal operation fluid-tightly closes, if a force exerted on the valve member by a pressure of the fluid at the inlet opening of the passage is greater than the spring force.

The valve member is applied to non-pressurized fluid under pressure at a second valve seat. At the second valve seat, the valve member is in a shut-off, also referred to as Leitungsabsperrlage. The valve member is so acted upon by a force, preferably a spring force, that the valve member in non-pressurized state at the second valve seat in abutment. The valve member is movably guided in the passage to a first valve seat. Also on the first valve seat, the valve member is in a shut-off, also referred to as Atmosphärenabsperrlage. Through this training is the Passage is held closed not only under pressure fluid by conditioning the valve member to the first valve seat, but also in pressureless fluid by conditioning the valve member by means of the force applied by the spring to the second valve seat. If pressure of the fluid builds up after previously pressureless fluid, the valve member lifts from the second valve seat and the gas in front of the valve member can flow around the valve member to flow via the passage at the first valve seat into the space connected to the atmosphere before the first valve seat first valve seat is closed by the valve member. By closed at zero pressure fluid passage of the second valve seat is advantageously prevented that air can be sucked from the outside into the device via the vent valve.

Preferably, a section of the passage lying behind the first valve seat in the direction of the outlet opening is always filled with fluid. This section preferably lies within a valve bushing of the venting valve, which may be partially or even completely filled with fluid. The vent valve acts as a siphon. The fluid flows out of the breather valve at the highest point. The vent valve remains filled with fluid. This ensures tightness at the second valve seat. As a result, fluid is always present on the side of the valve member facing the first valve seat, the second valve seat only has to be tight against fluid when the valve member rests, while gas-tightness is not required. Thus, the vent valve can be formed there with low geometric tolerances and surface requirements, which is associated with corresponding cost advantages.

Preferably, the valve member is spherical, so that the ball can always come to rest on the first valve seat and on the second valve seat regardless of the orientation of the vent valve relative to the horizontal. In another embodiment, the valve member may be a shut-off piston, for example in the form of a double cone, which has sealing surfaces on its sides facing the valve seats. A good Sealing function is achieved in that the first and / or the second valve seat is formed as a conical seat. For this purpose, preferably the sealing surfaces of the shut-off piston are conical. To apply force with little force, the valve member may be acted upon by a prestressed compression spring, for example a helical compression spring, in its line shut-off position.

According to an advantageous embodiment, the passage along its longitudinal direction portions having different diameters, wherein the valve member and the insert are arranged in the portion of the passage and the valve member, the portion against the portion of the passage fluid-tightly closes, if one by a pressure of the fluid The force exerted on the valve member by the input opening of the passage is less than the spring force.

According to an advantageous embodiment, a gap formed by the clearance between the valve member and a wall of the valve sleeve may be gas-permeable and fluid-impermeable. If gas under pressure is present in front of the valve member, it flows around the valve member. The passage has a closely surrounding the valve member wall, so that the gas flows around the valve member in the gap between the wall of the passage and the valve member. As soon as fluid rests against the valve member, it can not flow around the valve member through the gap due to its greater viscosity.

The gas flowing around the valve member leads to a brief drop in pressure in front of the valve member. This short pressure drop is sufficient that the valve member is briefly lifted by the force from the first valve seat and the gas can flow into the space connected to the atmosphere. It can therefore also be done during the pressurized fluid venting.

According to an advantageous embodiment, the insert may have a fluid channel with a transverse bore for guiding the fluid in the longitudinal direction from the inlet opening to the outlet opening of the passage. from Venting valve to the room connected to the atmosphere then performs an overflow, which is arranged above the first valve seat. This overflow can be carried out, for example, as a transverse bore. For example, the space connected to the atmosphere is an oil sump.

If the passage extends vertically with the first valve seat at the top, then in the case of fluid in the outlet-side section of the passage, no intake of air, but only fluid from the device, will take place, even if the leakage is not absolute at the second valve seat. But it is also possible that the line section extends horizontally. In order to ensure the siphon function, it may be advantageous in one embodiment that the overflow, for example, designed as a transverse bore, is aligned vertically upward in the installation position. According to an advantageous embodiment, the valve bushing may have a sealing groove arranged on an outer diameter for receiving a radial seal. With the help of such a radial seal, the vent valve in a bore of a fluid-conducting device can be mounted fluid-tight cheap and safe and, if necessary, remove again to a possible replacement of the vent valve.

According to an advantageous embodiment of the insert can be pressed into the portion of the bore. This ensures a safe and cost-effective installation of the insert in the valve sleeve, as well as ensuring the permanent fixation of the insert.

According to an advantageous embodiment, the valve may be formed as a proportional control valve for controlling a fluid flow of a device carrying a fluid. In this case, the valve may have a supply connection for supplying a hydraulic fluid, at least one working connection, at least one tank outflow for discharging the hydraulic fluid, as well as an in the piston arranged in the longitudinal direction of the passage, which is supported at one end by means of a spring which applies a spring force to the valve sleeve and is longitudinally coupled with a magnetic actuator, which is provided for applying a magnetic force. A control groove connects the working connection with either the tank drain or the supply connection. The spring is centered by a spring receiver disposed on the particulate filter.

A force on the piston is proportional to the difference between two effective surfaces in a first section of the piston. In order to realize a regular operation of the hydraulic valve, it is necessary to provide a corresponding counterforce available, which can be realized for example with a pressure on the difference of the effective surfaces of the piston. The difference results in an effective effective area. The size of the effective areas depends on the system parameters such as operating pressures of the hydraulic valve and the spring used. The spring may be, for example, a helical compression spring. The effect of active surfaces cancel each other if they have the same diameter. From the interaction of the magnetic force, the force of the spring and the active surface acted upon in each case sets a balance of power in the control positions and determines the output pressure at the working port. As a result, depending on the impressed current at the magnetic actuator, a fluid pressure can be generated at the working connection. The pressure is proportional to the current.

In addition to the filter function of the particulate filter, the integration of the spring receptacle for centering the valve spring in the particulate filter can save installation space and parts costs. The shape of the sieve plate makes it possible via a special geometry of the sieve plate a suitable receptacle for the spring and thus a centering of the spring. According to an advantageous embodiment, the spring receptacle may be formed as a centering arranged protuberance of a plate-shaped surface of the particulate filter, in particular, the spring cooperates for centering with a wall of the protuberance. In one embodiment, the spring can embrace the protuberance from an outer side of the protuberance, that is, it can be pushed over the protuberance during assembly. In an alternative embodiment, however, it is also conceivable that the protuberance can protrude outward and the spring can engage in the protuberance. Likewise, the Siebteller could also be made flat and centrally have a ring nozzle, in which engage the spring or the spring can embrace.

According to an advantageous embodiment, the protuberance may be formed at least partially through which the fluid can flow. It is also conceivable in principle that the protuberance is designed as a sheet metal part without openings and therefore fluid-impermeable. Since the spring, which surrounds, for example, the protuberance, is permeable to the fluid, it may be expedient if the protuberance is designed to be permeable to fluid. Also, the sieve plate can be provided with the holes of the sieve so flat before the introduction of the protuberance, so that only after the protuberance is introduced by a forming process such as deep drawing.

According to an advantageous embodiment, the spring receptacle may be formed in the longitudinal direction in the direction of the passage with a tapered conical shape. Such a design allows the spring to easily slide over the protuberance during assembly of the valve and centered by the special shape when pushed on yourself.

According to an advantageous embodiment, the supply connection and the tank discharge can be designed as radial bores in the valve bushing, which extend from the outside of the valve bushing to the passage. while the working port A is formed as an axial bore of the inlet opening. Thus, the most trouble-free inlet and outlet of the hydraulic fluid to the control grooves of the piston is given. The connections to control components of the transmission, in which the hydraulic valve is used, are as far as possible simple and safe to design and seal.

According to an advantageous embodiment, the hydraulic valve may be formed as a proportional pressure reducing valve, wherein a control force on the piston is exercised by the fact that the piston experiences a force in the longitudinal direction via the magnetic actuator and a force equilibrium can be generated via the spring and the acted upon by the hydraulic fluid active surfaces. In particular, the control force can be exerted on the piston in a first control position in that the piston undergoes a force in the longitudinal direction via the magnetic actuator and acted upon by the hydraulic fluid active surfaces of the control groove and can be acted upon by the spring with a force in the opposite direction. In a second control position, the control force can be exerted on the piston, characterized in that the piston experiences a force in the longitudinal direction via the magnetic actuator and can be acted upon by the spring with a force in the opposite direction.

Brief description of the drawings

Further advantages emerge from the following description of the drawing. In the drawings, embodiments of the invention are shown. The drawings, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

They show by way of example: 1 shows a longitudinal section through a valve according to an embodiment of the invention with an inserted particle filter.

FIG. 2 shows a longitudinal section through the valve from FIG. 1 with focus on the assembled particle filter; FIG.

Fig. 3 is a plan view of the particulate filter according to an embodiment of the invention;

4 shows a cross section through the particle filter from FIG. 3 along the line

IV-IV;

Fig. 5 is a side view of a valve according to an embodiment of the

Invention;

6 shows a detailed view of the valve from FIG. 5 with focus on the removed particle filter with spring receptacle;

Fig. 7 is a longitudinal section through the valve of FIG. 5 with inserted

particulate filter;

8 shows a detail section of the valve from FIG. 5 with focus on the mounted particle filter;

Fig. 9 is a plan view of the particulate filter according to an embodiment of the invention;

10 shows a cross section through the particle filter from FIG. 9 along the line

XX; FIG. 11 shows a section of an enlarged cross-section through the particle filter according to FIG. 3 with a first hole shape; FIG.

Fig. 12 shows a detail of an enlarged cross section through the

Particle filter according to FIG. 3 with a second hole shape and

Fig. 13 shows a detail of an enlarged cross section through the

Particle filter according to FIG. 3 with a third hole shape.

Embodiments of the invention

In the figures, the same or similar components are numbered with the same reference numerals. The figures are merely examples and are not intended to be limiting.

Figure 1 shows a longitudinal section through a valve 10 according to an embodiment of the invention with an inserted particle filter 20. The valve 10, which is designed as a vent valve 10 for venting a fluid-carrying device comprises a valve sleeve (valve housing) 12 with a longitudinal direction L formed passage 14 between an input port 32 and an output port 30. In the passage 14 valve member 16 is arranged, which is supported by a spring 40 which applies a spring force, disposed in a passage 14 and connected to the valve sleeve 12 insert 18 , The valve member 16 closes the outlet opening 30 of the passage 14 in a proper operation fluid-tight, when a force exerted by a pressure of the fluid at the inlet opening 32 of the passage 14 on the valve member 16 is greater than the spring force. Furthermore, the venting valve 10 comprises a particle filter 20, which is arranged at the inlet opening 32 of the passage 14. The particle filter 20 is on its outer edge 22 with a arranged at the inlet opening 32 of the passage 14 collar 34 fluid-tight manner.

The passage 14 has along its longitudinal direction L sections 24, 26, 28 with different diameters, wherein the valve member 16 formed as a ball 16 and the insert 18 are arranged in the portion 28 of the passage 14 and the valve member 16, the portion 26 against the portion 28th the passage 14 fluid-tightly closes when a force exerted by a pressure of the fluid at the inlet opening 32 of the passage 14 on the valve member 16 is less than the spring force. The valve member 16 is movably guided between a first valve seat 64 and a second valve seat 60. Both valve seats 64 and 60 are formed as conical seats. Between the cylindrical wall 68 of the section 28 and the ball 16 there is a gap 66 which is dimensioned such that it is gas-permeable but at the same time fluid-impermeable.

The ball as a valve member 16 is acted upon by a helical compression spring 40 as a force element of low force in the direction of the second valve seat 60. The force element, here the helical compression spring 40, engages over the first valve seat 64 in an annular groove. In this way, a compact design of the vent valve 10 according to the invention is advantageously achieved.

If the fluid is not under pressure, the ball 16 in the line shut-off position is in contact with the second valve seat 60. Gas bubbles located in the fluid can collect in the section 26 in front of the second valve seat 60.

The portion 28 of the passage 14, which is located between the ball 16 and the insert 18 is always filled with a fluid filling. Exceeds this fluid in section 28 defined by an overflow amount, the fluid flows via the fluid path 42 and the transverse bore 62 of the insert 18 back to a fluid reservoir.

As a result, no air can reach the section 28 and the ball 16 from the device so that such air can not reach the second valve seat 60 on the side of the ball 16 via the gap 66. This is prevented siphon-like by the fluid filling in section 28.

If a fluid pressure is built up in the device, this pressure lifts the ball 16 away from the second valve seat 60 against the force of the helical compression spring 40 and moves it from its line shut-off position into its atmospheric shut-off position abutting against the first valve seat 64 and shut off its fluid path 42.

During the path of movement of the line shut-off layer blocking the section 26 of the second valve seat 60 into the atmosphere shut-off layer, the gas collected in the section 26 can pass through the gap 66 past the ball 16 and through the fluid path 42 of the first valve seat 64 to a reservoir before the Ball 16 comes to rest on the first valve seat 64. Circulation of the ball 16 of fluid is prevented by the small width of the gap 66, which is impermeable to the fluid of higher viscosity than gas.

When pressure is reduced in the device, the ball 16 is moved by the helical compression spring 40 back into its resting on the second valve seat 60 Leitungsabsperrlage.

The valve bushing 12 has a sealing groove 46 arranged on an outer diameter 44 for receiving a radial seal 48. With the help of such a radial seal 48, the vent valve 10 in a bore of a fluid-carrying device can be mounted fluid-tight low and safe and, if necessary, also can be removed again to a possible replacement of the vent valve 10. The insert 18 also in the section 28 of the bore einpressbar.

The portion 24 of the passage 14 widens conically from the portion 26 in the longitudinal direction L to the inlet opening 32 of the passage 14. Thus, it is possible to use a particle filter 20 with a larger diameter so as to achieve a corresponding flow of the fluid despite the flow resistance of the particulate filter 20. FIG. 2 shows a longitudinal section through the valve 10 from FIG. 1 with focus on the mounted particle filter 20. The particle filter 20, which is preferably in the form of a plate sieve, is pressed into the collar 34 of the valve bush 12 and thus arranged in a self-locking manner. The collar 34 has for this purpose an undercut 36 for the axial fixation of the particulate filter 20. The particle filter 20 itself has at its outer edge 22 a crank 56 for clamping with the collar 34. The region of the undercut 36 of the collar 34 is formed as a step 54, which prevents the pressed-in particle filter 20 can slip out of its mounting position again. Thus, the assembled particulate filter 20 is reliably fluid-tight and captive mounted both by the step 54 and by his executed via the crank 56 self-locking in the collar 34 reliable.

FIG. 3 shows a plan view of the particle filter 20 according to one exemplary embodiment of the invention. The particle filter 20 is designed as a plate sieve. The particle filter 20 consists of a metallic material such as steel sheet of wall thickness 0, 1 mm, wherein the screen portion 58 has a plurality of sieve holes 50. The diameter 51 of the sieve holes 50 is, for example of the order of magnitude of 70 to 200 pm. The web width 52 between the screen holes 50 may be, for example, 50 to 150 pm. FIG. 4 shows a cross section through the particle filter 20 from FIG. 3 along the line IV-IV. Clearly, the plate shape of the particulate filter 20 with a Detecting bend 56, with which the particle filter 20 can be fixed fluid-tight and captive in the collar 34 of the valve sleeve 12.

FIGS. 1 to 13 are excerpts of an enlarged cross section through the particle filter 20 according to FIG. 3 with different hole shapes.

As can be seen in FIG. 11, the sieve holes 50 can be produced, for example, by conventional production methods such as drilling, punching, laser drilling, etc. The resulting cylindrical hole shape has a hydraulic throttle effect.

For producing the sieve holes 50, however, etching methods are also suitable by means of which, for example, the hole shapes shown in FIGS. 12 and 13 can be produced which have an approximate hydraulic diaphragm effect.

For this purpose, FIG. 12 shows a screen hole 50, which is formed from both sides of the particle filter 20 by hemispherical recesses 126, which in the context of the invention can also have basically different shapes (conical, etc.). The two recesses 126 can also be designed differently. An intersection of the two recesses 126 forms the narrowest point of the screen hole 50, wherein an axial position of the narrowest point during etching is variably adjustable. Also conceivable is an offset of the central axes of the recesses 126. A further possible form of the sieve holes 50 is also shown in FIG. 13. The screen hole 50 shown herein, unlike fig. 12 a single recess 126.

The design of the sieve holes 50 as diaphragms, it is possible to reduce the temperature-dependent influences of the hydraulic fluid in the flow through the screen. The flow resistance is thus more of the viscosity of the medium and less dependent on the temperature. In addition, the pressure losses across the sieve are significantly reduced.

The described aperture shape of the sieve holes 50 thus has the following advantages:

1 . Reduction of pressure losses (general, warm + cold)

2. Reduction of temperature influences

FIG. 5 shows a side view of a valve 10 according to an exemplary embodiment of the invention. The valve 10, which is designed as a proportional control valve 10 for regulating a fluid flow of a fluid-carrying device, comprises a valve sleeve 12 with a passage 14 formed in a longitudinal direction L between an inlet opening 32 and an (not visible) outlet opening 30, and a particle filter 20 , which is arranged at the inlet opening 32 of the passage 14. The particle filter 20 is fluid-tightly connected at its outer edge 22 with a collar 34 arranged at an inlet opening 32 of the passage 14. The valve 10 further comprises a supply port P for supplying a hydraulic fluid, which is protected in Figure 5 with a sieve 122 against possible contamination by particles in the hydraulic fluid, a working port A, which is formed as an inlet port 32, and a tank outlet T for discharging the hydraulic fluid ,

Details of the valve 10 are shown in FIG. 6, which shows an enlarged detail of the valve 10 from FIG. 5, as well as in FIG. 7, which shows a longitudinal section through the valve 10.

The valve 10 comprises a piston 86 arranged in the passage 14 in its longitudinal direction L, which is supported on the valve sleeve 12 at one end 108 by means of a spring 110 which applies a spring force and with a magnetic actuator 100 for applying a magnetic force is provided, is coupled longitudinally displaceable. A control groove 88 connects the working port A with either the tank drain T or with the Supply port P. The particulate filter 20 has a spring receptacle 1 12, which is designed as protuberance 1 13 of the particulate filter 20, on which the spring 1 10 is supported and which the spring 1 10 centers. The valve bush 12 has on its outer circumference 44 a sealing groove 46 into which a radial seal 48 is inserted. Another radial seal 124 is disposed between the region of the supply port P and the tank outlet T.

FIG. 6 shows a detailed view of the valve 10 from FIG. 5 with focus on the removed particle filter 20 with spring receptacle 12. The particle filter 20 is shown in FIG. 6 before being pressed into the inlet opening 32 of the valve bushing 12. The spring 1 10 can when inserting the particulate filter 20 into the inlet opening 32 of the valve sleeve 12, the spring receptacle 1 12 enclose and so be supported on the particulate filter 20, wherein the spring 1 10 is radially centered by the spring seat 1 12. The spring receptacle 1 12 is formed in the embodiment shown in Figure 6 as a centered protuberance 1 13 a plate-shaped surface of the particulate filter 20, wherein the spring 1 10 for centering with the wall 1 15 of the protuberance 1 13 13 cooperates and on this wall 15 applies, the spring retainer 1 12 is in the longitudinal direction L in the direction of the passage 14 with tapered, conical course 1 14 formed.

FIG. 7 shows a longitudinal section through the valve 10 from FIG. 5 with an inserted particle filter 20. In the case of the valve 10, which is designed as a proportional pressure reducing valve, a regulating force can be exerted on the piston 86 in that the piston 86 passes through the armature 104, which passes through the Spool 102 of the magnetic actuator 100 is driven, a force in the longitudinal direction L experiences and on the spring 1 10 and acted upon by the hydraulic fluid active surfaces 1 16, 1 18 a balance of power can be generated. The spring 1 10 in turn is based, centered by the spring receptacle 1 12, on the particulate filter 20 and above on the valve sleeve 12, since the particulate filter 20 is pressed into the valve sleeve 12 and thus firmly connected thereto. The supply connection P and the Tank drain T are formed as radial bores in the valve sleeve 12, which extend from the outside of the valve sleeve 12 to the passage 14, while the working port A is formed as an axial bore of the inlet opening 32. The passage 14 is formed in the valve sleeve 12 as a stepped axial bore from the input port 32 to the output port 30. The valve 10 is shown inserted into a valve receptacle 120, in which also the feeds of the hydraulic fluid to the working port A, the supply port P and the tank outlet T are formed. The sealing of the valve 10 in the valve seat 120 via the radially arranged seals 48 and 124th

The control of the valve 10 via the supply of hydraulic fluid in a control groove 88 of the piston 86 and thus taking place acting radially in the piston 86 arranged active surfaces 1 16, 1 18, via which the exertion of an axial force on the piston 86 is possible. A counterforce can be exerted on the piston 86 by energizing the coils 102 of the magnetic actuator 100 via the armature 104. The provision of the piston 86 via the supported on the valve sleeve 12 and on the other side at the end 108 of the piston 86 resting spring 1 10. The valve sleeve 12 is advantageously carried out in one piece with a pole tube not shown in detail.

The axial force transmission between armature 104 and piston 86 by means of a pin 130, which is arranged in the valve sleeve 12 out. The pin 130 allows a decoupling between anchor and piston bearing. A circumferential recess 132 allows for a reduction of the bearing surface, whereby the friction can be reduced. At the same time advantageously only axial forces are transmitted through the pin 130. By separating the two spaces of the valve 10, the tolerance situation is also significantly improved. As can also be seen from FIG. 7, a pole disk 134 is provided integrated in a bobbin 136 by being at least partially encapsulated by the material of the bobbin 136 or by injecting recesses of the pole disk 134. As a result, a smaller axial space is achieved and the assembly of the valve 10 is simplified.

The bobbin 136 includes an armature space, in which the armature 104 is slidably disposed, at one end of the valve 10 from. Protrusions 138 projecting into the armature space thereby form a stop for the armature 104, so that the bearing surface reduced as a result has an anti-adhesive effect.

A reservoir 140 provided in the bobbin 136, which is filled once, communicates with the armature space and prevents air from entering the valve 10. Further, the displacement of the fluid into the reservoir 140 prevents additional damping. The reservoir 140 is dimensioned such that the volume shift caused by the pin stroke is reduced.

In order to prevent a foreign body caused short circuit between a fork plug, not shown, and the pole plate 134, the valve 10 further comprises a chip protection cover 142.

FIG. 8 shows a detail section of the valve 10 from FIG. 5 with a focus on the mounted particle filter 20. The particle filter 20, which is preferably in the form of a plate sieve, is pressed into the collar 34 of the valve sleeve 12 and thus arranged in a self-locking manner. The collar 34 has for this purpose an undercut 36 for the axial fixation of the particulate filter 20. The particle filter 20 itself has at its outer edge 22 a crank 56 for clamping with the collar 34. The region of the undercut 36 of the collar 34 is formed as a step 54, which prevents the pressed-in particle filter 20 can slip out of its mounting position again. Thus, the assembled particulate filter 20 is performed both by the step 54 and by its over the bend 56 self-locking in the collar 34 reliable fluid-tight and captive mounted.

Figure 9 shows a plan view of the particulate filter 20 according to an embodiment of the invention. The particle filter 20 is designed as a plate sieve. The particle filter 20 consists of a metallic material such as steel sheet of wall thickness 0, 1 mm, wherein the screen portion 58 has a plurality of sieve holes 50. The diameter 51 of the sieve holes 50, which can be produced with different hole shapes as described for FIG. 3, is, for example, of the order of magnitude of 70 to 200 μm. The web width 52 between the screen holes 50 may be, for example, 50 to 150 m. In the central region of the particulate filter 20, the spring receptacle 1 12 can be seen as a protuberance 1 13 in plan view. The cone-shaped course 1 14 is formed as a sloping wall 1 15 of the protuberance 1 13. As shown in Figure 9, the protuberance 1 13 at least partially, namely formed in a central in the interior of the assembled spring 1 10 lying area, permeable by the fluid.

FIG. 10 shows a cross section through the particle filter from FIG. 9 along the line X-X. Clearly, the plate shape of the particulate filter 20 can be seen with a bend 56, with which the particle filter 20 can be fixed fluid-tight and captive in the collar 34 of the valve sleeve 12. On average, the spring receptacle 1 12 as protuberance 1 13 and the wall 1 15 with a conical course 1 14 can be clearly seen.

Claims

claims

Valve (10), in particular hydraulic valve (10), a fluid leading

Device comprising

a valve bushing (12) having a passage (14) formed in a longitudinal direction (L) between an inlet opening (32) and an outlet opening (30),

a particle filter (20) which at the inlet opening (32) of the

Passage (14) is arranged,

wherein the particle filter (20) at its outer edge (22) with a at an input port (32) of the passage (14) arranged collar (34) is fluid-tight manner.

Valve according to claim 1, wherein the particle filter (20) as a sieve, in particular as a plate sieve is formed.

Valve according to claim 1 or 2, wherein the particulate filter (20) in the collar (34) is pressed or einpressbar.

Valve according to one of the preceding claims, wherein the collar (34) has an undercut (36) for the axial fixation of the particulate filter (20) in the pressed state.

Valve according to one of the preceding claims, wherein the particulate filter (20) in the collar (34) is arranged self-locking.

Valve according to one of the preceding claims, wherein the particle filter (20) at its outer edge (22) has a crank (56) for clamping with the collar (34).

7. Valve according to one of the preceding claims, wherein the particulate filter (20) has a plurality of sieve holes (50) with approximate aperture effect.

8. Valve according to one of the preceding claims, wherein the valve is designed as a vent valve (10) for venting a fluid-conducting device, further comprising

a valve member (16) disposed in the passage (14) and supported by a spring (40) which applies a spring force to an insert (18) disposed in the passage (14) and connected to the valve sleeve (12) and the outlet opening (30) of the passage (14) in a normal operation fluid-tightly closes when a by a pressure of the fluid at the inlet opening (32) of the passage (14) on the valve member (16) applied force is greater than the spring force.

Valve according to claim 8, wherein the passage (14) has portions (24, 26, 28) of different diameters along its longitudinal direction (L), the valve member (16) and the insert (18) in the portion (28). the passage (14) are arranged and the valve member (16) fluid-tightly closes the portion (26) against the portion (28) of the passage (14), when a by the pressure of the fluid at the inlet opening (32) of the passage (14) force applied to the valve member (16) is less than the spring force.

10. Valve according to claim 8 or 9, wherein a by the clearance between the valve member (16) and a wall (68) of the valve sleeve (12) formed gap (66) is permeable to gas and fluid-impermeable.

1 1. Valve according to one of claims 8 to 10, wherein the insert (18) has a fluid channel (42) with a transverse bore (62) for guiding the fluid in Longitudinal direction (L) from the inlet opening (32) to the outlet opening (30) of the passage (14).

Valve according to one of claims 8 to 1 1, wherein the valve sleeve (12) has a on an outer diameter (44) arranged sealing groove (46) for receiving a radial seal (48).

Valve according to one of claims 8 to 12, wherein the insert (18) in the

Section (28) of the bore is einpressbar.

Valve according to one of claims 1 to 7, wherein the valve is designed as a proportional control valve (10) for regulating a fluid flow of a fluid-conducting device, further comprising

a supply port (P) for supplying a hydraulic fluid, at least one working port (A),

at least one tank drain (T) for draining the hydraulic fluid, a piston (86) arranged in the passage (14) in its longitudinal direction (L), which at one end (108) by means of a spring (1 10) which applies a spring force, is supported on the valve sleeve (12) and with a magnetic actuator (100) which is provided for applying a magnetic force, is longitudinally slidably coupled,

wherein a cam groove (88) selectively connects the working port (A) to the tank drain (T) or to the supply port (P), the spring (110) being centered by a spring retainer (112) disposed on the particulate filter (20) ,

Valve according to claim 14, wherein the spring receptacle (1 12) as a centered arranged protuberance (1 13) of a dish-shaped surface of the particulate filter (20) is formed, in particular the spring (1 10) for centering with a wall (1 15) of the Protrusion (1 13) cooperates.

16. Valve according to claim 145, wherein the protuberance (1 13) is formed at least partially through which the fluid can flow.

17. Valve according to one of claims 14 to 16, wherein the spring receptacle (1 12) in the longitudinal direction (L) in the direction of the passage (14) is formed with tapered conical course (1 14).

A valve according to any one of claims 14 to 17, wherein the supply port (P) and the tank drain (T) extend as radial bores in the valve sleeve (12) extending from the outside of the valve sleeve (12) to the passage (14) , are formed while the working port (A) is formed as an axial bore of the inlet opening (32).

19. Valve according to one of claims 14 to 18, wherein the hydraulic valve is designed as a proportional pressure reducing valve, wherein a regulating force on the piston (86) is exercisable in that the piston (86) via the magnetic actuator (100) a force in the longitudinal direction (L ) experiences and on the spring (1 10) and acted upon by the hydraulic fluid active surfaces (1 16, 1 18), a balance of power can be generated.

20. Valve according to one of claims 14 to 19, wherein an axial force transmission between the piston (86) and an armature (104) of the Magnetaktors (100) by means of a separately formed pins (130), which provided in the valve sleeve (12) is.

21. Valve according to claim 20, wherein the pin (130) has a circumferential recess (132) for reducing its bearing surface.

22. Valve according to claim 20 or 21, wherein a pole disc (134) is at least partially integrated in a bobbin (136) is provided.

23. A valve according to claim 22, wherein in the bobbin (136) a hydraulic fluid reservoir is provided, which is in communication with an armature space.

24. Valve according to claim 23, wherein the bobbin (136) projecting into the armature space projections (138) as a stop for the armature (104).

25. Valve according to one of claims 22 to 24, wherein the valve (10) has a chip protection cover (142) which covers the pole disc (134) with ribs.

26. Valve according to one of claims 14 to 25, wherein the valve bush (12) is provided integrally with a pole tube.