CN112013151A

CN112013151A - Actuator for hydraulic valve and hydraulic valve

Info

Publication number: CN112013151A
Application number: CN202010139213.8A
Authority: CN
Inventors: 迪特·迈什; 哈特莫特·韦伯
Original assignee: Eco Holding 1 GmbH
Current assignee: Eco Holding 1 GmbH
Priority date: 2019-05-29
Filing date: 2020-03-03
Publication date: 2020-12-01
Also published as: DE102019114408A1

Abstract

The invention relates to an actuator for a hydraulic valve, in particular a hydraulic transmission valve, having a magnetizable actuator housing (14) which encloses magnet coils (16), and having a pole group (24) which is arranged in a housing receiving opening (23) of the actuator housing (14), wherein the pole group (24) comprises at least one pole core (28) and a pole tube (30), wherein an armature (40) which is received so as to be axially movable is arranged in an interior (36) of the pole group (24). In order to reduce friction between the armature (40) and the pole group (24), an air gap (48) is formed, wherein the air gap (48) is formed completely between a peripheral surface (50) of the armature (40) and an inner surface (45) of the interior (36), and the air gap (48) is formed in such a way that a constant distance (A) is produced between the armature (40) and the pole group (24) over the circumference of the armature (40) in order to centrally support the armature (40) in the pole group (24). The invention also relates to a hydraulic valve (12).

Description

Actuator for hydraulic valve and hydraulic valve

Technical Field

The invention relates to an actuator for a hydraulic valve and to a hydraulic valve, in particular a hydraulic transmission valve of a motor vehicle.

Background

In order to be fail-safe also in the extreme case with a large transmission oil change interval, in the case of a so-called service life expectancy, the transmission valve must have a high degree of robustness. Although a high degree of robustness can be achieved with large clearances in the component to be moved, this has a negative effect on the quality of the adjustment and the resulting magnetic forces. Furthermore, this large gap results in leakage and an increase in lateral forces acting on the magnet.

DE 102011053023 a1 discloses a hydraulic valve which, in addition to having a high actuating quality, has a high degree of robustness. A high degree of robustness is achieved in that dirt particles in the working medium do not cause the transmission valve to jam, since the armature can exert such a large axial force that the armature can always freely split open. At the same time, the hydraulic valve has a high actuating quality, which is achieved by means of a plurality of constructional measures. In particular, transverse forces between the armature and the pole tube are thereby minimized.

The quality of the adjustment can be further improved by constructing the pole group in a substantially one-piece construction. The pole tube and the pole core are connected by means of a connecting web that is thin-walled relative to the pole tube and the pole core. DE 102014013602B 3 therefore discloses a hydraulic valve whose actuator has a pole tube and a pole core which is connected integrally to the pole tube via a connecting web. This minimizes the transverse forces between the pole tube and the armature, wherein, in order to maintain a reliable function of the actuator, all important geometries are followed, including wherein a central position of such an armature and additionally a central insertion of the armature into the interior of the pole group are achieved.

Disclosure of Invention

The object of the invention is to provide an actuator which has a high force density while further reducing the transverse forces acting on the armature. A further object is to provide an improved hydraulic valve which has the highest possible force density of its magnetic actuators and can be produced cost-effectively in this case.

The above-mentioned object is achieved by the features according to the invention. Advantageous embodiments and advantages of the invention result from the exemplary embodiments, the description and the drawings.

An actuator for a hydraulic valve, in particular a hydraulic transmission valve, is proposed, which comprises a magnetizable actuator housing, which encloses a magnet coil. The actuator furthermore has a pole group arranged in a housing receiving opening of the actuator housing, wherein the pole group comprises at least one pole core and a pole tube, wherein the pole core and the pole tube are integrally connected by a connecting web. The pole core is connected to the connecting web via a pole core cone and/or the pole tube is connected to the connecting web via a pole tube cone. An armature which is accommodated in an axially movable manner is arranged in the interior of the pole group, wherein the armature is delimited in the axial direction on its first end face by a closure cap which is formed opposite it, preferably integrally with the pole group, and by a bearing disk which is arranged opposite on its second end face which is arranged opposite the first end face. The actuator according to the invention has an air gap for reducing friction and for a defect-free magnetic function between the armature and the pole group, wherein the air gap is formed completely between a peripheral surface of the armature and an inner surface of the interior space, wherein the air gap is formed to provide a constant distance between the armature and the pole group over the circumference of the armature for the central support of the armature in the pole group. In other words, the armature is accommodated centrally in the pole group on account of the constantly designed distance between the armature and the pole group over the circumference of the armature (this distance is embodied as an air gap).

The integrally formed pole group, which consists at least of a pole core and a pole tube, has the advantage that the mechanical axis of the entire pole group can be determined during the production of the pole group, in particular of the armature-receiving component of the pole group (the pole group consisting of pole tube and pole core and connecting web), and therefore the envelope of the armature is advantageously defined, since the two axes of the pole group and of the armature can be coaxially aligned in a congruent manner, or in other words can be completely coaxially formed, in order to thus ensure advantageous operating properties of the armature. In order to minimize the transverse forces, the armature must be arranged centrally movably in the pole group, in particular in the pole tube, and can likewise be moved centrally into the conical region of the pole core. When the armature is in the central position, the lateral forces are balanced so that their sum is zero. The greater the deflection from the central bearing, the greater the lateral forces generated thereby. The sum of the forces results in a higher axial force, and thus a higher magnetic force, due to the minimized lateral forces.

Since the armature does not contact the inner surface, the armature also does not exert a force on the pole core, and the longitudinal axis of the pole group, which is defined during production, is not deformed by the relatively thin connecting webs between the pole core and the pole tube as a result of the force of the armature on the pole core. An important advantage is the reduction of friction and the consequent increase of the force density of the actuator. Another advantage is that no magnetic isolating layer needs to be constructed between the armature and the pole set, as is required in the prior art, since the armature is not in contact with the pole set due to the air gap. This saves coating effort and subsequent grinding.

The high force density is achieved in that the components forming the metal circuit for the magnetic flux are connected and/or pressed against each other such that no air gap is present between them to hinder and/or attenuate a possible magnetic flux. These components are a pole group consisting of pole tubes, pole cores and connecting webs, as well as an actuator housing and a pole disk.

The central component, i.e. the pole group, has the smallest possible concentricity deviations on different diameters, since it is machined in the stresses on a machine. The central member, i.e. the pole group, contains all important geometries to meet the high functional requirements of the actuator. The precise diameters required for this purpose can be produced in what is known as clamping, so that they are precisely configured relative to one another. Thus, the best possible centre position of the component is given in the assembled state. Furthermore, the pole group is the only component to be constructed precisely in the so-called magnetic circuit. All other components are not very demanding to produce and can be produced in a cost-effective manner.

In one embodiment, the armature is accommodated in the pole group in a movable manner by means of a support element which extends at least partially through the armature. This provides the possibility of the armature being accommodated completely without contact in the pole group and thus being accommodated movably in the pole group without contact with it. The support element may extend along the symmetry of the armature, however the support element may also be arranged transversely to the armature. The support element can likewise extend over the outer circumference of the armature.

It is proposed that the support element is configured to extend in the direction of and coaxially with the longitudinal axis of the actuator. It is therefore advantageous that no transverse forces act on the armature during the movement of the support element, since the armature moves in the direction of the longitudinal axis of the actuator. This advantage is supported by the support of the support element in the pole group. In particular, friction losses can be minimized if the support element is mounted with the smallest possible cross section and/or in pole groups with a small axial extent. In other words, the bearings formed in the pole groups are as short as possible, in particular in their axial extent.

In a further embodiment of the actuator according to the invention, a bearing opening for bearing the support element is formed in the closure cap. The closing cap forms the end of the pole group in the axial direction, so that advantageously openings for bearing the support elements can be introduced in a cost-effective manner, for example by drilling, into the closing cap integrated into the pole group. In order to form low-friction sliding bearings, further machining of the openings (for example honing, grinding and/or polishing) can also be carried out at low cost, since the openings for machining can be realized simply, since this is directly achievable. The closure cap can also be constructed as a separate component.

The further bearing position of the support element is advantageous because it is also cost-effective to construct in the bearing disk. The support disk is usually produced independently of the pole tube and the pole core and is usually joined into the pole group by means of a press fit after the armature has been introduced into the interior of the pole group.

The support disk is therefore a simple disk-shaped or cylindrical component, into which a further opening is introduced for realizing the support position. This can likewise be produced as simply and cost-effectively as in a closure cap. The support disk may also be part of a bushing or a pole plug.

It is to be noted here that the closing cap can also be joined into the pole tube after the production of the integrally formed pole group section consisting of pole tube, pole core and connecting web, whereby the production of the bearing point in the closing cap is further simplified.

The free surfaces formed in the interior chambers in front of and behind the armature are advantageously of the same size, so that when the armature moves in the interior chamber, the hydraulic fluid present can move in the interior chamber and does not have to be conducted out of the interior chamber in order to cause rapid movement of the armature. The pressure obtained by means of an area of the same size as the armature moves due to the required compression in the volume in front of or behind the armature is sufficient to achieve a fast reaction time of the hydraulic valve, while advantageously damping the armature and, correspondingly, the piston of the hydraulic valve which moves by means of the armature.

The armature is preferably fixedly connected to the support element in order to avoid relative movements between the two components, which could lead to a malfunction of the hydraulic valve.

Advantageously, the support element is constructed in the form of a rod, in particular a solid or thick-walled rod. The rod is adapted to cause linear movement with the armature.

According to a further aspect, the invention relates to a hydraulic valve, in particular a hydraulic transmission valve, having a control valve and an actuator for moving the control valve, wherein the actuator is constructed according to the invention.

In order to ensure the function of a hydraulic valve in an electromechanical transmission control device, it is in principle necessary to implement the support of the armature as robustly as possible against external influences. In addition to the mechanical robustness achieved, robustness to contaminated operating media is thus avoided, which can be produced, for example, in the form of debris by friction between the pole set and the armature, since the armature is not in contact with the pole set.

The hydraulic valve according to the invention can be used as a transmission valve for a transmission clutch (in particular a starting/shifting clutch or a synchronizer) to be coupled in a comfortable friction fit, which can be used with only a small change in transmission oil or without a change in transmission oil at all. In addition, the transmission valve can be used in countries with poor quality of the oil of the transmission case.

Drawings

Other advantages are given by the following description of the figures. An embodiment of the invention is shown in the drawings. The figures, description and embodiments contain a large number of combined features. The person skilled in the art can also appropriately consider these features individually and conclude other combinations of significance.

Exemplarily showing:

fig. 1 shows a longitudinal section through an actuator according to the invention of a hydraulic valve according to the invention; and

fig. 2 shows a longitudinal section through the pole group with armature of the actuator according to fig. 1.

Detailed Description

In the drawings, the same or similar type of components are denoted by the same reference numerals. The drawings are only examples and should not be construed as limiting.

Fig. 1 shows an actuator 10 according to the invention of a hydraulic valve 12 according to the invention in longitudinal section. Starting from actuator 10, hydraulic valve 12, which is not shown in detail in the components thereof designed for hydraulic functions, also comprises a control valve having a housing with a hydraulic connection, which has an axially movable, hydraulically through-passable piston, which is accommodated so as to be axially displaceable in order to release and close a flow opening formed in the housing. The piston is axially positioned by means of the actuator 10.

The actuator 10 comprises a magnetizable actuator housing 14 which surrounds the magnet coil 16 on its outer circumference 18 and on at least one end side 20. The magnetic coil 16 is embedded or injected for electrical insulation reasons in a carrier 22, preferably made of plastic. The carrier 22, equipped with the magnetic coil 16, is received in a housing receiving opening 23 of the actuator housing 14.

The carrier body 22 is arranged between the magnet coil 16 and the pole group 24, wherein the carrier body is designed with its circumferential surface 26 at least partially surrounding the pole group 24.

The pole group 24, which is embodied in the form of a cap, is formed from a pole core 28 and a pole tube 30, which are connected to one another in the axial direction by means of a connecting web 32. Pole core 28, pole tube 30 and connecting web 32 are formed in one piece. The pole core 28 is arranged facing the piston, while a pole tube 30, which is designed in the form of a cap and is arranged opposite the piston, is designed to be almost closed by means of a closing cap 31 on the end side of the pole group 24 facing away from the piston.

The connecting web 32 is designed as a hollow cylinder and is connected on its side facing the pole core 28 to a pole core cone 34. Likewise, the connecting webs 32 can be connected to the pole tube taper of the pole tube 30 on their side facing the pole tube 30. The pole core 28 and the pole tube 30 can also each have a taper, between which a connecting web 32 is arranged. In the interior 36 of the pole group 24, which has a longitudinal axis 38, an armature 40 is accommodated so as to be movable in the direction of the longitudinal axis 38.

For the sake of simplicity of assembly, the actuator housing 14 is designed as a hollow cylinder and has, in its region facing the end of the piston arrangement, a pole disk 42 which surrounds the pole core 28 and is arranged supported in the axial direction on the carrier body 22 and the actuator housing 14. The pole disk 42 can likewise be pressed into the actuator housing 14. Advantageously, the actuator housing 14 can be of a hat-shaped or in other words can-shaped design, and the carrier body 22 carrying the magnetic coil 16 can be simply inserted into the actuator housing 14 and can be covered with the pole disk 42 designed to receive the pole group 24.

The magnet coils 16, the pole groups 24 with the armature 40 and the pole discs 42 arranged in the actuator housing 14 form the main part of the actuator 10 of the hydraulic valve 12.

As can be gathered, in particular, from the enlarged longitudinal section of the pole group 24 in fig. 2, a shoulder 44 is provided on the inner surface 45 of the pole group 24 in the region of the pole tube 30 and the connecting web 32, wherein the shoulder 44 is formed by two different inner diameters I1, I2 of the interior 36. The first inner diameter I1 present in the pole tube 30 and in the section of the connecting web 32 is smaller than the second inner diameter I2 formed in the remaining inner space 36. Possible lateral forces acting on the armature 40 are further reduced by means of the shoulder 44.

In the operating position of the armature 40, in which it rests against the closure cap 31, the shoulder 44 covers the armature 40 in the direction of the closure cap 31, but is also formed in the connecting web 32. In other words, in this operating position, the armature 40 is surrounded, at least as far as the shoulder 44, by the inner surface 45 with the larger inner diameter I2, as viewed from the pole tube 28. The shoulder 44 serves to remove dirt particles, for example, as a result of mechanical wear, or to remove cutting residues in the hydraulic fluid with which the hydraulic valve 12 is operated. In this way, such dirt particles are prevented from reaching and/or being able to be fixed on the circumferential surface 50 of the armature 40. The shoulder 44 may additionally be formed with a scraping edge, wherein the scraping edge is formed in the form of a chamfer.

As an alternative to the above-described embodiment, the shoulder 44 can also be provided on the armature 40. In this embodiment, the inner chamber 36 has a constant inner diameter, whereas the armature 40 has two different outer diameters, wherein the region of the armature 40 with the larger outer diameter is arranged towards the closure cap 31. It is likewise possible in a further alternative to implement the actuator 10 according to the invention without the attachment 44. That is, neither the armature 40 nor the pole set 24 has a shoulder 44.

The interior 36 is substantially closed off with respect to the piston by means of a support disk 46. The support disc 46, in addition to limiting the axial movement of the armature 40, is also arranged to avoid excessive draining of the hydraulic fluid contained in the internal cavity 36. The hydraulic fluid provided for the low-friction movement and damping of the armature 40 can thus pass over the hydraulic piston and/or its housing via the corresponding movement gap, but nevertheless prevents excessive or complete emptying by means of the bearing disk 46.

In order to reduce friction, an air gap 48 is formed between the armature 40 and the pole set 24 of the actuator 10, wherein the air gap 48 is formed completely between the circumferential surface 50 of the armature 40 and the inner surface 45. The air gap 48 is designed to provide a constant distance a around the circumference of the armature 40 between the armature 40 and the pole set 24, i.e. the inner surface 45, for the central support of the armature 40 in the pole set 24.

For this purpose, in the present exemplary embodiment, the armature 40 is accommodated movably in the pole group 24 by means of a support element 54 which passes at least partially through the armature. The support element 54 is arranged in a receiving opening 56 which passes completely through the armature 40 in the axial direction, wherein the support element is connected to the armature 40 in a material-engaging manner. Likewise, the support element can be connected to the armature 40 in a force-fitting and/or form-fitting manner. For example, the receiving opening 56 can be provided with an internal thread, wherein the support element 54 has an external thread complementary thereto. In order not to loosen the screw connection during operation of the actuator 10, the support element 54 and the armature 40 can be connected to one another, for example in a bonded manner, at the first end face 58 of the armature 40 in order to prevent a relative movement of the two components.

The receiving opening 56 is configured coaxially with a symmetry axis 60 of the armature 40 extending in the axial direction. The support element 54 received in the receiving opening 56 is configured to extend beyond the first end face 58 and a second end face 59 configured to face away from the first end face 58. That is to say in other words, the support element 54 has a greater axial extension than the armature 40. This is advantageous because the element sections 62 of the support element 54 which project beyond the armature 40 can thereby be supported in the pole group 24. The support element 54, which has an element longitudinal axis 64 and is advantageously designed in the form of a rod, is configured coaxially with the armature 40. Thus, the element longitudinal axis 64 corresponds to the axis of symmetry 60.

The support in the pole group 24 is implemented by means of a first support opening 66 in the closure cap 31 and a second support opening 68 formed in the support disk 46. In order to reduce the friction between the support element 54 and the

components

31, 46 having the bearing

openings

66, 68, the bearing

openings

66, 68 of the

components

31, 46, which are designed in the form of plain bearings, are kept as short as possible over their axial extent. As can be seen in fig. 2, i.e. the enlarged illustration of the pole group 24, the second bearing opening 68 has two different opening diameters D1, D2, which are formed in the bearing disk 46, wherein the opening section of the second bearing opening 68 formed facing the armature 40 has a first opening diameter D1, which is greater than the second opening diameter D2 of the opening section of the second bearing opening 68 located facing the piston.

The bearing locations formed by the bearing

openings

66, 68 have the largest possible large distance from one another. Due to the large distance of the bearing positions of the support element 54, the misalignment of the bearing positions in the region of action between the armature 40 and the inner surface 45 is smaller than if the distance between the bearing positions were shorter. This has the advantage that the armature 40 moves centrally in the interior 36 during its axial movement, thereby reducing the resultant transverse forces.

The bearing

openings

66, 68, which preferably have a circular diameter, are kept as small as possible in order to reduce friction. The absolute value of the diameter depends on the armature 40 and its possible stroke and is therefore not referred to as absolute.

Furthermore, in the interior 36, the free surfaces in front of or behind the armature 40 are of the same size, so that when the armature 40 moves, the hydraulic fluid moves in the pole body 24 and, except in the bearing position, no outflow of hydraulic fluid from the interior 36 has to take place. The hydraulic fluid present in the interior 36 serves to specifically cushion the armature 40, thus ensuring this cushioning.

The support disk 46 is likewise magnetic or magnetizable, so that to avoid adhesion of the armature 40 to the support disk 46, the release disk 70 is arranged facing the armature 40 of the support disk 46.

Likewise, the support disk 46 can also have a release disk 70 arranged facing the armature 40.

The embodiment of the pole group 24 described ensures that the armature 40 is almost ideally located on the longitudinal axis 38 and moves in each stroke position, since the geometric tolerances (by machining the pole group 24 in the clamping) are minimized and the actuator 10 can therefore operate with low transverse forces and low friction and therefore with high efficiency.

Claims

1. Actuator for a hydraulic valve, in particular a hydraulic transmission valve, having a magnetizable actuator housing (14) which encloses a magnet coil (16), and having a pole group (24) which is arranged in a housing receiving opening (23) of the actuator housing (14), wherein the pole group (24) comprises at least one pole core (28) and a pole tube (30), wherein the pole core (28) and the pole tube (30) are integrally connected by a connecting web (32), and wherein the pole core (28) is connected to the connecting web (32) by a pole core cone (34) and/or the pole tube (30) is connected to the connecting web (32) by a pole tube cone, and wherein an axially movably accommodated armature (40) is arranged in an interior (36) of the pole group (24), and wherein, in the axial direction, the armature (40) is delimited on its first end face (58) by a closure cap (31) of a pole group (24) which is configured opposite the armature and by a bearing disk (46) which is arranged opposite on a second end face (59) of the armature which is arranged opposite the first end face (58),

in order to reduce friction between the armature (40) and the pole group (24), an air gap (48) is formed, wherein the air gap (48) is formed completely between a circumferential surface (50) of the armature (40) and an inner surface (45) of the interior (36), wherein the air gap (48) is formed in such a way that a constant distance (A) is produced between the armature (40) and the pole group (24) over the circumference of the armature (40) in order to centrally support the armature (40) in the pole group (24).

2. The actuator of claim 1,

the armature (40) is movably accommodated in the pole group (24) by means of a support element (54) which extends at least partially through the armature.

3. The actuator of claim 2,

the support element (54) is configured to extend in the direction of a longitudinal axis (38) of the actuator (10) and is coaxial with the longitudinal axis.

4. An actuator according to claim 2 or 3,

the support element (54) is mounted in the pole group (24).

5. The actuator according to any one of claims 2 to 4,

a bearing opening (66) for bearing the support element (54) is formed in the closure cap (31).

6. An actuator according to any of claims 2 to 5,

the support element (54) is mounted in the mounting plate (46).

7. An actuator according to any of the preceding claims,

the free surfaces formed in the interior (36) in front of and behind the armature (40) are of the same size.

8. An actuator according to any of the preceding claims,

the armature (40) is fixedly connected to the support element (54).

9. An actuator according to any of the preceding claims,

the support element (54) is designed in the form of a rod.

10. A hydraulic valve comprising a control valve and an actuator (10) for moving the control valve, wherein the actuator (10) is configured according to any one of claims 1 to 9.