DE102010005166A1 - Electromagnetically actuated low pressure drain valve for use in swash-plate type axial piston machine utilized as hydraulic motor, has main coil and auxiliary coil producing magnetic force acting valve body in respective directions - Google Patents

Abstract

The valve (22) has a valve body (40) associated with sealing surfaces (72, 74) and mechanically prestressed towards an opening position. The valve body is shifted in another direction in a closing position using a magnetic actuator. A main coil (50) and an auxiliary coil (52) produce magnetic force acting on the valve body in the respective directions. The main and auxiliary coils are arranged coaxial to each other. A main anchor (54) and an auxiliary anchor (56) are assigned to the main and auxiliary coils, respectively.

Description

The The invention relates to an electromagnetically actuated valve and a hydraulic machine designed with such a valve.

Such valve-controlled hydraulic machines are for example from the EP 1 537 333 B1 known. This document shows a hydraulic machine in axial or radial piston construction, which can be operated in principle as a motor or as a pump, wherein the delivery or absorption volume via the valve control is infinitely adjustable. In one described embodiment, the hydraulic machine is designed as an axial piston machine, wherein a plurality of piston arranged in a cylinder is supported on a rotatably mounted swash plate. Each piston defines with the associated cylinder chamber a working space which can be connected via a low-pressure side valve and a high-pressure side valve with a pressure medium inlet or a pressure medium outlet.

at The known solution, the two valves are electric openable or lockable non-return valves, which can be controlled via the pump control to the respective Working space in "Full Mode", in the "Partial Mode "or in" idle mode "to operate. As a result, the delivery or displacement volume is infinitely variable be adjusted from a maximum value to 0. Over a Control unit is the hydraulic machine according to a control algorithm operated in order to minimize the pulsation sum flow volume (Pump) or total displacement (motor). The volume flow adjustment is often done after a live control, they however, may also be after phase-cut or phase-cut control be performed.

hydraulic machines with a changeable via the valve control Sucking / delivery volume is also called digital displacement units (DDU). In principle, all positive displacement principles are applicable. However, piston engines are advantageous, in particular in radial piston construction, since this will allow the input and output for to execute each displacement separately and thus to actively control. It can be quite useful between Pump and motor operation to distinguish, so then the control element look different for the low and high pressure connection can.

requirement for the above type of control (DDU) is that the low-pressure and high-pressure valves with high dynamics can be switched, so that the above-described pressure fluid flow paths very quickly shut off or released to flow through can be. The low-pressure side or high-pressure side Control elements can be used, for example, as switching valves, preferably be designed in a seat design, preferably be actuated by a magnetic actuator. To such a Valve become different, sometimes contradictory requirements posed. A minimized in terms of space hydraulic machine sets in its overall dimensions small valve with the largest possible and thus low-resistance flow cross-section ahead. Such a large flow cross-section requires However, a larger valve lift, what the demand After high valve dynamics with the smallest possible electrical Power consumption contradicts. On top of that, the requirements to the valve with different operating points of the hydraulic machine vary. From high speeds, for example, arise large Volume flows and demands for short switching times, low speeds go with long duty cycles for accompanied by the magnetic coils. About the at the respective connection applied pressure also change the mechanical loads as well as the requirements for the sealing system.

In the US 7,077,378 B2 discloses a low-pressure side valve for such a hydraulic machine, wherein an annular flow opening is closed by an approximately cup-shaped valve member. This annular flow opening is limited by an inner and an outer sealing seat, so that the specific surface pressure at the sealing edge compared to a conventional valve cone is comparatively low. In the known solution, the plate or cup-shaped valve element is biased by a spring into an open position and can be adjusted by means of a magnetic actuator in its closed position in which the valve element rests on the above-described sealing seats and the flow opening blocked. When flowing through this valve, the plate-shaped valve element biased in its opening direction can be subjected to flow forces effective in the closing direction, so that the throughflow cross-section is reduced and the pressure loss is correspondingly increased. Although it would be possible to counteract this undesired closing movement by means of a stronger opening spring, this would impair the dynamics of the valve or necessitate a stronger magnet coil with associated power electronics. To avoid this disadvantage, according to the US 7,077,378 B2 a permanent magnet is used, which acts on the valve element in its open position with a magnetic force. When the magnetic actuator is energized, the field of the permanent magnet is neutralized and a magnetic force acting in the closing direction is generated. In such a solution, therefore, a correspondingly powerful magnetic actuator is required. In addition, this shows as well Solution not the desired dynamics, since first the field of the permanent magnet must be weakened before the valve element can be moved in the direction of its closed position.

In the WO 2007/128977 A2 a solution is proposed in which the magnetic actuator is designed with two coils. A main coil generates a magnetic field effective in the closing direction on the valve element. Furthermore, a secondary coil is provided, which weakens the field of the permanent magnet when energized, so that when the secondary coil is energized, the valve element is very quickly adjustable via the main coil in its closed position.

The disadvantage of this solution is that, on the one hand, a considerable outlay in terms of apparatus is required for the main coil, the secondary coil and the additional permanent magnet. Furthermore, the control engineering effort is considerable, since the two coils operating point must be energized depending on angle of rotation or timely to control the valve element in the required manner. The main coil can also be used in the solution according to the WO 2007/128977 be energized as required before switching. The switching point is then determined by switching on the secondary coil.

One Another disadvantage of using a permanent magnet is in that it attracts magnetic particles in the pressure medium, so that there is an accumulation of such particles in the seating area and thus can lead to a malfunction of the valve.

In contrast, The invention is based on the object, an electromagnetic operated valve and one with such a valve executed hydraulic machine to create in which the adjustment a valve element with low device engineering and regulatory technical Effort is possible.

These Task is in terms of electromagnetically actuated Valve by the combination of features of claim 1 and with regard to the hydraulic machine by the characteristics of the sibling Claim 18 solved.

According to the invention the solenoid operated valve with a Valve seat associated valve body running, which is biased in a first direction, and by means of a magnetic actuator in a second direction is adjustable. About a main coil is a acting in the second direction on the valve body Magnetic force and a secondary coil in the first one Direction of the valve body acting magnetic force generated. The main and secondary coils are arranged so that the energized Main coil counteracts the bias and thus acts as an adjustment and the secondary coil when energized in the same direction as the Preload acts. Contrary to the prior art described above Here are the magnetic circuit for main and secondary coil constructively separated. The orientation of the magnetic fields does not play Roller so that the coils are reverse polarity protected. Furthermore you can the coils on the applied current level in their force effect be controlled separately as needed.

In such a solution, therefore, no permanent magnet is required, wherein the valve body is biased by the sub-coil in a basic position and is held in this even when energized main coil. The adjustment of the valve body is then simply by Stromlosschalten the secondary coil, so that it can be adjusted with very high dynamics. In contrast to the prior art described at the beginning, no time is lost for the construction of the magnetic field generated by the main coil. The necessary magnetic field reduction can be made dynamic by so-called quick-clearing. Furthermore, the control engineering effort is minimal, since only one of the coils must be de-energized, while in the prior art described above, two magnetic coils had to be energized rotating angle and timely to initiate the closing process. Another advantage is that in certain cases with less demand on the dynamics of the valve can be completely dispensed with the powering of the secondary coil. With the secondary coil, another functionality can be mapped. If the valve opened by the pretension flows through against the pre-load, in 2 from B to A z. B. in idle mode, closing acting flow forces can occur. These can be compensated by energizing the secondary coil. By varying the current level can be responded to variable flow forces.

at a preferred solution is that in the first switching position the valve body in the first direction acting force with energized secondary coil larger than that of the energized main coil and on the valve body acting force, so that the valve body at the same time energized coils acted upon in the direction of the first switching position becomes.

According to the invention it is preferred when the valve is in an open position is biased and thus by means of the magnetic actuator in the closing direction is adjustable. Of course, the invention is Concept, however, can also be used with a normally closed valve.

at a compact embodiment of the invention the main and secondary coils are arranged coaxially with each other.

there stand one of the main coil associated main anchor and one of the secondary coil associated secondary armature in operative connection with a on the valve body acting ram.

at An embodiment of the invention are for simplicity of construction main anchor, side anchor and pestle integrally formed.

there it is preferred if a main and secondary anchor forming Anchor against a tappet section is radially expanded.

This anchor collar can be equipped with axially parallel compensation holes and a central receptacle for a spring 38 be executed.

at In a variant of the invention, coil carriers of the main and secondary coil and a two pole rings of the coil assembly spacing separating ring integrally formed. This the coil windings and Polringe receiving one-piece component can be very simple be produced by injection molding.

Of the Construction of the valve can be further simplified if the inner diameters of the main and secondary coils are the same are.

at In one embodiment, it is preferred if the two Coils axially one behind the other lying in a bobbin are included, to avoid overlay the magnetic fields at least in the region between the coils an area is provided of a paramagnetic material.

at In one embodiment, the plunger is in led to a bobbin and a spring biased in one direction.

According to the invention intended to carry out the valve with a seat bush, at the valve seat is formed and in a valve sleeve or used directly in a housing bore of a hydraulic machine is. It is preferred if the one-piece magnet armature only in the seat bush is performed.

According to one Embodiment of the invention, the valve body two concentric, circumferential sealing surfaces, each one a corresponding valve seat is assigned, so that an approximately annular flow cross-section forms.

at In a variant of the invention, the valve body is resilient stored on the plunger.

According to the invention it is preferred that electromagnetically actuated valve as Use low pressure valve.

other advantageous developments of the invention are the subject of further Dependent claims.

in the Following are preferred embodiments of the invention explained in more detail with reference to schematic drawings. Show it:

1 a highly schematic representation to explain the operating principle of a valve-controlled hydraulic machine with digitally variable displacement / delivery volume (DDU);

2 a longitudinal section through a first embodiment of a low-pressure side valve of the hydraulic machine 1 in the open state;

3 the valve off 2 when closed;

4 a longitudinal section through another embodiment of a low-pressure side valve;

5 a sectional view of a both a main coil and a secondary coil associated one-piece magnet armature of the valve 4 ; and

6 a further simplified embodiment of a low-pressure side valve.

The following is based on 1 the functional principle of a valve-controlled hydraulic machine 1 explained, whose delivery / swallowing volume is digitally adjustable (DDU). The hydraulic machine is designed in the illustrated embodiment as an axial piston machine in a swash plate design, wherein 1 shows a very simplified transaction. In the following, only the essential components for understanding the invention will be explained. For more detailed information, reference is made to the prior art described above. In the following description is the hydraulic machine 1 operated as a hydraulic motor, in principle, the statements apply to the hydraulic motor but also for a pump with adjustable displacement.

According to the schematic representation in 1 has the hydraulic machine 1 a cylinder drum 2 in which a variety of cylinder bores 4 are formed, in each of which a piston 6 axially ver slidably guided. Each of the pistons 6 limited with the cylinder bore 4 a workroom 8th whose volume depends on the stroke of the pistons 6 is independent. These are each about a piston shoe 10 supported on an inclined swash plate, with the output shaft 12 connected is. In the illustration according to 1 is the cam formed due to the rotation of the swash plate 14 represented, which represents the rotation angle dependence of the piston stroke and thus the volume of the respective working space. As in 1 shown on the right, is every working space 8th via an inlet valve 16 with one all workspaces 8th common supply line 18 connected, which is subjected to a system or high pressure. This high pressure can for example via a pump 20 be generated.

Every working space 8th is also about a drain valve 22 with a likewise all working rooms 8th common drain line 24 connected in a tank 26 opens.

As already explained, in the illustrated embodiment, the drain valves 22 and the inlet valves 16 each designed as electrically unlockable or lockable check valves. The inlet valve 16 is biased via a spring, not shown, in its illustrated basic position in a closed position and can be powered by energizing a Magnetaktors 28 bring in an open position, so that the pressure medium from the supply line 18 in the respective workspace 8th can flow in. The drain valve 22 is biased in its illustrated basic position via a spring in an open position. By energizing the magnet actuator 30 can this drain valve 22 bring into a locked position in which the pressure medium is not from the work space 8th can flow out. The activation of the magnetic actuator 28 . 30 via a control unit via which the modes described above (full mode, partial mode, idle mode) are adjustable, so that the displacement of the hydraulic motor 1 is infinitely adjustable, with suitable control of the valves 16 . 22 also the pulsation can be lowered to a minimum. In the illustrated embodiment, the control of the valves takes place 16 . 22 depending on the angle of rotation of the output shaft 12 , which have a Drehwinkelaufnehmer 36 detected and via a signal line to the control unit 34 is reported. In principle, of course, other characteristics, such as that on the output shaft 12 acting torque, the displacement of the hydraulic motor 1 or the angle of rotation of the swash plate in the control of the valves 16 . 22 be taken into account.

2 shows the basic structure of the low-pressure side check valve, which in a hydraulic motor according to 1 the drain valve 22 equivalent. For a pump would be the valve 22 the inlet or suction valve. According to 2 has the low pressure or drain valve 22 one by a spring 38 in an open position biased valve body 40 that by means of the magnetic actuator 30 in a closed position against a valve seat 42 is adjustable, so that an annular flow cross-section 44 is locked. The drain valve 22 is designed as a so-called "poppet valve", wherein the valve element 40 a pestle 46 who's at his in 2 lower end portion of a mushroom-shaped closing plate 48 wearing. With open flow cross-section 44 (View after 2 ) is a pressure medium connection between an inlet-side connection channel A and one in the working space 8th opening channel B open so that pressure fluid from the inlet channel A ago in the working space 8th or in the opposite direction, from the workroom 8th can flow to the channel A. With a flow from A to B occur virtually no effective in the closing direction flow forces, so that the valve disc 48 in principle by the force of the spring 38 could be kept alone in its open position. In the case of a flow from B to A, the forces resulting from the pressure medium flow act in the closing direction, so that the spring 38 alone is no longer sufficient to the valve plate 48 to hold in its open position. To fix the in 2 illustrated opening position of the valve disk 48 is the actuating magnet 30 according to the invention with a main coil 50 and a secondary coil 52 which are a main anchor 54 or a secondary anchor 56 assigned. According to the invention, the valve disk 48 by energizing the secondary coil 52 held in its open position. This generates an energized current 2 shown Mag netfeld, through which - as explained in more detail below - the valve disk 48 is held in its open position. According to the invention in the illustrated basic position of the low-pressure or drain valve 22 also the main coil 50 be energized. The generated magnetic field (see 2 ) acts in the closing direction on the valve disk 48 - In the relative position shown is the over the coil 50 on the valve plate 48 acting force, however, less than that on the secondary coil 52 generated force, so the valve disk 48 with simultaneously energized coils 50 . 52 is obtained in the illustrated open position.

Now that the operating principle is clear, constructive details of the drain valve according to the invention 22 explained.

The valve has a valve bush 58 into a corresponding hole in the cylinder drum 2 can be screwed. The valve bush 58 opens axially over the channel B in the running in this embodiment with a ball head working space 8th and further has a radial bore star opening in channel B. 60 , In the valve socket 58 is a seat bush 62 screwed in whose order fangswandung on the one hand to the channel A and on the other hand to the valve seat 42 down opening drainage channel 64 is trained. In the valve seat side end portion of the drain channel 64 are a variety of connecting webs 66 formed, which the annular drainage channel 64 divide into circular ring segments. The mouth areas of these circular ring segments form a circumferential inner sealing edge 68 and an outer sealing edge 70 from, which are employed in each case obliquely to the valve axis and on which with a closed drain valve 22 circumferential sealing surfaces 72 . 74 of the valve disk 48 lie sealingly, so that the annular flow cross-section 44 is locked.

As shown in 2 is the valve plate 48 executed mushroom-shaped, with the two sealing surfaces 72 . 74 at the workroom 8th are formed away from the rear side. The pestle 46 penetrated in the illustrated embodiment, a rearwardly projecting hub projection 76 of the valve disk 48 and is recorded there rotatably. In the illustrated embodiment, the axial connection between the plunger takes place 46 and the valve plate 48 via a tension spring 78 in a spring seat 80 of the spring plate 48 is received and a spring plate at the bottom of the spring retainer 80 is supported. The end portion of the tension spring remote therefrom 78 engages one at the in 2 lower end portion of the plunger 46 attached spring plate 82 at, which is slightly axially spaced from the adjacent end face 84 of the spring plate 48 runs, so that this by the force of the tension spring 78 elastic on the pestle 46 is stored.

He is in 2 up to the hub projection 76 subsequent part of the plunger 46 is axially displaceable in a guide bush 86 a multi-part bobbin 88 taken up, with radial projections in corresponding recesses of the seat bushing 62 dips in and there over a spring washer 90 is secured. The guide bush 86 has an axial guide hole 92 for the pestle 46 , In the closed position ( 3 ), the hub projection emerges 76 in a Stirnausnehmung 94 the guide bush 86 one.

Radially outside the pilot hole 92 is at the guide bush 86 an annular recess 96 provided in which the secondary coil 52 is used in sections. Upwards ( 2 ) is the secondary coil 44 by a magnetizable pole ring 98 covered, in the axial direction of a separating ring 100 adjoined. This separating ring 100 is at the bottom of a jacket section 102 the guide bush 86 supported, in a corresponding inner recess 104 the seat bush 62 dips. In these of the coat section 102 encompassed area of the guide bush 86 is a coil holder 106 used, with an axial projection 108 down to the bottom of the guide bush 86 extends. This axial projection 108 is from the main coil 50 encompassed, thus in the annulus between the coil holder 106 and the jacket section 102 the guide bush 86 is used. In the 2 bottom face of the main coil 50 is about another pole ring 110 axially on the separating ring 100 supported.

At the height of the separating ring 100 has the guide bush 86 a disk-shaped section 87 from a paramagnetic material, such as a stainless steel, with the other two magnetic field conducting parts of the guide bushing 86 For example, is connected by welding and helps to ensure that the magnetic fields of the two coils 50 and 52 are clearly separated from each other. When energizing the coil thus no force occurs on the valve body 40 in an undesirable direction.

The in 2 overhead end portion of the plunger 46 passes through an internal bore 112 of the bobbin holder 106 , This is in its central area to a spring chamber 114 for the spring 38 extended. This is on the one hand on an annular shoulder 116 of the spring chamber 114 supported on the other hand, and on the main anchor 54 on, which together with the adjacent end face of the axial projection 108 of the bobbin holder 106 a main working air gap 118 a main stage of the magnetic actuator 30 limited. To optimize the magnetic characteristic, the main anchor emerges 54 with an anchor projection 120 in a Stirnausnehmung 122 of the axial projection 108 one.

In the 2 below, from the main working air gap 118 distant end face of the main anchor 54 lies on a spacer 124 on which the secondary anchor 56 in the axial direction to the main anchor 54 is spaced. The secondary anchor 52 engages with his with a ring protrusion 126 executed end face on a radially projecting support shoulder 128 of the plunger 46 so that the force of the spring 38 over the main anchor 54 , the spacer ring 124 and the secondary anchor 56 on the pestle 46 is transmitted and this down ( 2 ) biased so that the spring plate 48 is held by the spring force in its illustrated open position. Between the one with the ring projection 126 providing the end face of the secondary anchor 52 and the correspondingly designed end face of the guide bush 86 is a side working air gap 130 formed in the opening position of the drain valve 22 is minimal.

The energization of the two coils 50 . 52 via the to the multi-part bobbin 86 attached control electronics 132 ,

With energized secondary coil 52 is the valve plate 48 magnetically locked in its open position. To close the valve disk 48 are, as already explained above, in the illustrated opening position of the drain valve 22 initially both coils 50 . 52 energized, wherein the aforementioned auxiliary working air gap 130 is minimal. In this position is the main working air gap 118 maximum, so that on the main anchor 54 acting magnetic force is correspondingly low, so that the valve disc 48 by the force of the spring 38 and that of the secondary coil 52 generated magnetic field is locked even in low current further in its open position. As shown in the illustration 2 is removable, causes the separator ring made of paramagnetic material 100 in that the magnetic fields of the two coils 52 . 54 are separated. Without such a separation of the magnetic fields could that of the main coil 50 generated magnetic field the auxiliary working air gap 130 or that of the secondary coil 52 Magnetic field generated the main working air gap 118 flood so that a magnetic force could be generated in the undesired direction. Consequently, the components are selected with regard to the material so that a superposition of the two magnetic fields with simultaneously energized coils 50 . 52 is not to be feared. That is why the seat bushing is also used 62 made of a paramagnetic material. The components of the bobbin 88 (Guide bush 86 , Coil holder 106 , Pole rings 98 . 124 and separating ring 98 ) are preferably positively connected with each other and behave within the valve construction as a single component.

The secondary anchor 56 developed due to the already minimal auxiliary working air gap 130 even at a low current level sufficient force to the drain valve 22 to keep it open. By varying the current level, the locking force can be adapted to the conditions of use. This may be required, for example, at higher speeds of the hydraulic machine when the pistons 6 high volume flows through the drain valve 22 to press.

Once the magnetic field of the main coil 50 is constructed, the secondary coil 52 de-energized to close, eliminating the magnetic force component effective in the opening direction and the main armature 54 against the force of the spring 58 a lift upwards ( 3 ) and doing the main working air gap 118 closes. It takes the skin anchor 54 the pestle 46 with, so the secondary anchor 52 in the axial direction upwards ( 3 ) and the auxiliary working air gap 130 is enlarged. The valve plate 48 Performs a corresponding stroke until the two sealing surfaces 72 . 74 on the sealing edges 78 respectively. 70 rest and the flow area 44 is closed. This closing force can also be restored by varying the current level for energizing the main coil 50 to adjust.

An advantage of this concept is that the magnetic field of the skin coil 50 before closing the drain valve 22 already fully assembled and thus the maximum possible force on the valve disk 48 exercises. The valve plate 48 is then practically biased. The comparatively small secondary coil 52 sets the drive signal (independent on / off) due to its much smaller time constant compared to the main coil 50 much faster so that the dynamics of the valve is increased.

To open the valve, the main coil 50 de-energized, so that the valve plate 48 by the force of the spring 38 moved back to its basic position. This opening movement can be achieved by energizing the secondary coil 52 be supported, so that the return movement of the valve disk 48 is accelerated. In this way, both in the closing direction and in the opening direction of the drain valve 22 higher valve dynamics than conventional solutions.

Based on 4 and 5 An embodiment with a simplified structure will be explained.

The basic structure of in 4 in longitudinal section shown drain valve 22 corresponds to that of the above-described embodiment, so that a further description of corresponding components is dispensed with and the same reference numerals as in the 2 and 3 be used.

In the 4 variant shown has a valve sleeve 58 , at which the ball head of the working space 8th , the radial hole star 60 and the terminals A, B are formed. This valve bush 58 is screwed into a housing bore, not shown, of the hydraulic machine. In the valve socket 58 is a seat bushing in the illustrated embodiment 62 screwed in, at the two sealing edges 68 . 70 of the valve seat 42 are formed. Similar to the previously described embodiment is in the seat bushing 62 the annular drainage channel 64 formed, whose cross section is in the sectional view according to 4 down, to the sealing edges 68 . 70 decreased.

The smaller secondary coil 52 is at the in 4 illustrated embodiment not in a multi-part coil holder but directly in a hub portion 134 the seat bush 62 added. This is in the hub section 134 a circumferential Stirnnut 136 provided, the outer peripheral wall is extended relative to the inner circumferential wall in the axial direction and the secondary coil 52 embraces.

On the in 4 upper annular face of the secondary coil 52 is the pole ring 98 put on, over the separating ring 100 from the main coil 50 associated wieteren pole ring 110 is spaced. The main coil 50 is in the illustrated embodiment in a front view 138 of the bobbin holder 106 used, the cover-shaped on the in 4 upper end surface of the seat bush 58 is attached. At this bobbin holder 106 the spring is supported 38 off, the one-piece, two coils 50 . 52 associated armature 140 in an open position ( 4 ). At this magnet armature 140 is the spring plate 48 springy over the tension spring 78 as well as the spring plate 84 spring-mounted.

5 shows an individual representation of the one-piece magnet armature 140 , Accordingly, this has a guide section 142 whose in 5 lower end to a tappet section 144 is downgraded. On the latter is in a similar manner as in the embodiment according to the 2 and 3 the spring plate 48 of the valve body 40 placed. The guide of the magnet armature 140 takes place along the guide section 142 in a guide hole 146 ( 4 ) of the seat bush 62 , At the guide section 142 closes upwards ( 5 ) An anchor collar 148 on, which in the illustrated embodiment has an approximately cylindrical outer circumference and in the direction of its upper end face over a circumferential step 150 downgraded and over a Stirnausnehmung 152 retracted frontally. The one with the circumference level 150 and the Stirnausnehmung 152 Engineered area limits the main working air gap 118 ( 4 ) between the end face of the armature 140 and the adjacent, correspondingly shaped end face of the bobbin holder 106 , The side working air gap 130 is through a lower ring end face 154 of the anchor collar 148 and the adjacent end face of the boss portion 134 limited. This side working air gap 130 is in the opening position of the valve 22 minimal.

As further 4 is removable, has the anchor collar 148 a central recording 156 for an end portion of the spring 38 , On a pitch circle whose diameter is slightly larger than the outer diameter of the guide section 142 is, there is a variety of compensation holes 158 , which run parallel to the anchor axis and the recording 156 to cut.

In the above embodiments, coil carriers 168 . 170 the main coil 50 or the secondary coil 52 as well as between the pole rings 98 . 110 lying separating ring 100 designed as separate components. The device complexity can be further reduced if these components, ie the bobbin 168 , the coil carrier 170 and the non-conductive magnetic flux separating ring 100 is manufactured in one piece by injection molding, wherein the two pole rings 98 . 110 to be overmoulded. This can be done, for example, that in the Polringen 98 . 110 Recesses are provided for the plastic melt, so that the cavity of the injection mold is completely filled and thus the coils 50 . 52 with the associated coil carriers 168 . 170 and the separator ring 100 form a structural unit. In other words, an integral bobbin is formed, the two above with 168 . 170 designated coil carrier and the separator ring 100 as well as the two pole rings 98 . 110 and the actual coil windings 50 . 52 along with their connections.

In particular 4 is removable, the inner diameter of the pole rings 98 . 110 and the separator ring 100 as well as the two coils 50 . 52 substantially equal and corresponding to the outer diameter of the anchor collar 148 trained, so that it is encompassed sliding.

The fit between the pilot hole 146 and the guide section 142 is made comparatively accurate to a tilting of the armature 140 to avoid. In the case in which it should come to a tilting, especially the pole ring 110 the guide of the magnet armature 148 support, so that excessive tilting is reliably prevented.

An advantage of in 4 illustrated embodiment is that the number of components compared to the solution described above is significantly reduced, since only a one-piece magnet armature 140 , the valve sleeve 48 , the seat bush 62 as well as the coils 50 . 52 , a coil holder 106 and the said rings 98 . 100 . 110 or the one-piece coil carrier and the valve plate 48 must be provided.

6 shows a further simplified embodiment, the basic structure of the embodiment according to 4 corresponds and in which on a valve sleeve 58 is waived.

Just as in the embodiment according to 4 has that in 6 illustrated drain valve 22 a one-piece magnet armature 140 that with the main coil 50 as well as the secondary coil 52 works together and in the seat 62 is guided. This takes the secondary coil 52 on while the main coil 50 in the lid-shaped bobbin holder 106 is included. The valve plate 48 is springy on the one-piece magnet armature 140 stored and has two sealing surfaces 72 . 74 who are in the execution play according to the 4 and 6 at plan end portions of the spring plate 48 are formed. These sealing surfaces 72 . 74 act with the sealing edges 68 . 70 the seat bush 62 together.

On the outer circumference of the seat bush 72 is a thread 160 executed, over this with the above-described components in a housing bore 162 the hydraulic machine can be screwed. This housing bore 162 flows into the workroom 8th and is according to the geometry of the in the 2 . 3 and 4 used valve sleeve 58 executed so that, for example, a ball head of the work space 8th formed. In this housing bore 162 also open the over the valve 22 to be controlled fluid channels.

The coil holder 106 is in the embodiment according to 6 with a lid part 164 executed, in the assembled state on an outer surface of the housing 166 seated and thus the housing bore 162 covered at the top.

Otherwise, this corresponds to 6 illustrated embodiment of the above-described embodiments, so that further explanations are unnecessary. The function of the embodiments according to the 4 to 6 essentially corresponds to that of the first described embodiment.

The inventive concept can both on low-pressure side and high-pressure side valves insert that closed or open when de-energized could be.

Disclosed are an electromagnetically actuated valve and one with Hydromachine executed in such a valve. Has according to the invention a solenoid actuator of the valve a main coil and a secondary coil. When energizing the secondary coil is a valve body of the Valve biased in a basic position. This basic position is also respected when both coils are energized simultaneously. To close the valve is energized at the same time Coils the secondary coil de-energized, so that in the opening direction effective main spool the valve is moved out of its home position.

1

hydromachine

2

cylinder drum

4

bore

6

piston

8th

working space

10

piston shoe

12

output shaft

14

cam

16

inlet valve

18

supply line

20

pump

22

drain valve

24

drain line

26

magnetic actuator

30

magnetic actuator

34

control unit

36

Speed Sensor

38

feather

40

valve body

42

valve seat

44

Flow area

46

tappet

48

valve disc

50

main coil

52

secondary coil

54

main anchor

56

In addition to anchor

58

valve sleeve

60

Radial bore star

62

seat bushing

64

drain channel

66

web

68

sealing edge

70

sealing edge

72

sealing surface

74

sealing surface

76

hub projection

78

tension spring

80

spring mount

82

spring plate

84

face

86

guide bush

87

disc-shaped section

88

bobbins

90

spring washer

92

guide bore

94

front recess

96

recess

98

pole ring

100

separating ring

102

shell section

104

inner recess

106

spool holder

108

axial projection

110

Another pole ring

112

internal bore

114

spring chamber

116

annular shoulder

118

Main operating air gap

120

anchor lead

122

front recess

124

spacer ring

126

annular projection

128

radial shoulder

130

Besides working air gap

132

control electronics

134

hub portion

136

ring groove

138

end recording

140

armature

142

guide section

144

tappet section

146

guide bore

148

anchor Bund

150

peripheral step

152

front recess

154

Annular face

156

admission

158

compensating bore

160

thread

162

housing bore

164

cover part

166

outer surface

168

coil carrier

170

coil carrier

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• - EP 1537333 B1 [0002]
• US 7077378 B2 [0006, 0006]
• - WO 2007/128977 A2 [0007]
• WO 2007/128977 [0008]

Claims (18)

Electromagnetically actuated valve with a valve seat ( 72 . 74 ) associated valve body ( 40 ) which is mechanically biased in a first direction to a first switching position and adjustable by means of a magnetic actuator in a second, opposite direction to a second switching position, wherein with a main coil ( 50 ) one in the second direction on the valve body ( 40 ) acting magnetic force can be generated and a secondary coil ( 52 ) is present, characterized in that with the secondary coil ( 52 ) one in the first direction on the valve body ( 40 ) acting magnetic force can be generated. Valve according to claim 1, wherein in the first switching position of the valve body ( 40 ) force acting in the first direction when the secondary coil is energized ( 52 ) is greater than that of the energized main coil ( 50 ) and on the valve body ( 40 ) Acting force. Valve according to claim 1 or 2, wherein the first switching position, the open position of the valve body ( 40 ). Valve according to one of the preceding claims, wherein the main coil ( 50 ) and the secondary coil ( 52 ) are arranged coaxially with each other. Valve according to claim 4, wherein one of the main coil ( 50 ) associated main anchor ( 54 ) and one of the secondary coil ( 52 ) associated secondary anchor ( 56 ) in operative connection with a on the valve body ( 40 ) acting plunger ( 46 ), with energized coils ( 50 . 52 ) a main working air gap ( 118 ) greater than a secondary working air gap ( 130 ). Valve according to claim 5, wherein the main armature, secondary armature and plunger are in one piece as a magnetic armature ( 140 ) are formed. Valve according to claim 6, wherein an anchor collar ( 148 ) of the magnet armature ( 140 ) opposite a guide / tappet section ( 142 . 144 ) is radially expanded. Valve according to claim 7, wherein the anchor collar ( 148 ) axially parallel compensation bores ( 158 ) and a central recording ( 156 ) for a spring ( 38 ) Has. Valve according to one of the claims 4 to 8, wherein coil carriers ( 168 . 170 ) of the main coil ( 50 ) and the secondary coil ( 52 ) and a separating ring ( 100 ) are integrally formed. Valve according to one of the claims 4 to 9, wherein the inner diameters of the coils ( 50 . 52 ) are the same. Valve according to one of the claims 4 to 10, wherein the two coils ( 50 . 52 ) axially one behind the other in a bobbin ( 88 ), at least in the region between the coils ( 50 . 52 ) an area ( 87 ) is formed of a paramagnetic material. Valve according to claim 11, wherein the plunger ( 46 ) in the bobbin ( 88 ) is guided and by means of a spring ( 38 ) is biased in one direction. Valve according to one of the preceding claims, with a seat bushing ( 62 ), at which the valve seat ( 72 . 74 ) is formed and in a valve sleeve ( 58 ) or directly into a housing bore ( 162 ) of a hydraulic machine can be used. Valve according to one of the claims 6 to 10 and claim 13, wherein the magnet armature ( 140 ) only in the seat bush ( 62 ) is guided. Valve according to one of the preceding claims, wherein the valve body ( 40 ) two concentrically encircling sealing surfaces ( 72 . 74 ), each having a sealing edge ( 68 . 70 ) of a valve seat ( 42 ) assigned. Valve according to one of the claims 5 to 15, wherein the valve body ( 40 ) resiliently on the plunger ( 46 ) is stored. Valve according to one of the preceding claims, this being a low pressure valve. Hydraulic machine with actively controllable low-pressure-side valves and with high-pressure-side valves, characterized by a low-pressure valve ( 30 ) according to one of the preceding claims.