Electromechanical actuator and actuator-valve unit

Abstract

The invention relates to an electromechanical actuator (1) having a rotor (2); a stator (3) having a cutout (4); and at least one sliding element (5) which is operatively connected to the rotor (2) and which is moved by rotation of the rotor (2), the sliding element (5) protruding at least partially into the recess (4) in the radial direction (6) of the stator (3) when the actuator (1) is in the operating and / or stationary state. The invention also relates to an actuator-valve unit (100), which has a valve (101) and an electromechanical actuator (1).

Description

[0001] The invention relates to an electromechanical actuator and an actuator-valve unit.

[0002] Common actuators, in particular drive devices for control slides of hydraulic valves (for example, known from DE 10 2007 031 429 A1) have a rotor and a stator as parts of an electric machine. Here, the rotary motion of the motor is usually converted into a linear motion of the control slide after a certain stroke. The motor (i.e., the rotor and the stator) is located outside the motion space of the slide. In the common elongated arrangement, the motor must be offset backward by the stroke of the slide, that is, at a greater distance from the connecting surface between the slide and the valve or along the stroke direction of the slide. In the vertical arrangement (as shown in DE 10 2007 031 429 A1), the motor must be arranged above the slide, that is, along the height extension direction perpendicular to the longitudinal extension direction / stroke direction of the slide, with a greater distance, more precisely, arranged above the slide along the entire motion space of the slide. However, these arrangements lead to an increase in the structural size of common actuators. This reduces their scalability for higher requirements. In other words, the structural dimensions of conventional actuators are therefore excessively increased in the case of high force / travel requirements therefor.

[0003] The object of the present invention is to provide an electromechanical actuator and an actuator-valve unit which have a small overall size and advantageous expandability.

[0004] This object is achieved by the features of the independent claims. The dependent claims contain advantageous embodiments of the invention.

[0005] The object is achieved in particular by an electromechanical actuator. The actuator comprises a rotor, a stator and at least one sliding element. The sliding element is in operative connection with the rotor and is moved by the rotation of the rotor. The stator has a notch, wherein the sliding element at least partially extends into the notch of the stator in a radial direction of the stator when the actuator is in operation and / or in a stationary state.

[0006] Since the stator has a recess and the sliding element at least partially and at least temporarily protrudes through the recess, a compact construction of the actuator is ensured.

[0007] In some preferred embodiments, the stator has a complete cutout as the above-mentioned notch, in which the stator is completely interrupted along its circumferential direction. In a preferred alternative embodiment, the above-mentioned notch is a partial notch, such as an (incomplete) slot or a (radial) through hole in the stator. In the case of this partial notch, the remaining structure of the stator (along the circumferential direction of the stator) can be configured, for example: to close the magnetic circuit, for example as a tab with a magnetizable material and / or as a base plate with a magnetizable material; and / or to ensure a higher structural stability of the stator, for example as a reinforcing structure also with, for example, a magnetizable material.

[0008] As explained above, the sliding element "extends into the notch of the stator along the radial direction of the stator". In this regard, the radial direction of the stator is defined as a direction (or directions) extending from the inside to the outside of the stator. The sliding element extends in the radial direction here, so that the sliding element extends from the inside (of the stator) to the outside toward the notch. In this regard, "along the radial direction" includes all directions extending from the inside to the outside of the stator, especially directions parallel to or coaxial with the radius and extending from the inside to the outside of the stator.

[0009] For example, in some embodiments, the sliding element is arranged offset from a center point of the stator, thus forming, for example, a secant with the periphery of the stator.

[0010] In some embodiments, the sliding element at least partially extends into the notch in a radial direction. In other words, in such an example, the sliding element is oriented coaxially with the radius of the stator.

[0011] The sliding element preferably projects at least partially into the recess in the radial direction of the stator both in the idle state and during operation of the actuator.

[0012] In an advantageous embodiment, the stator is not rotationally symmetrical with respect to the rotation axis of the rotor. Here, the stator is advantageously rotationally symmetrical with respect to the rotation axis of the rotor except for the presence of the notch. Preferably, the stator is substantially annular, in particular circular, wherein the notch is advantageously slot-shaped, so that the stator as a whole is substantially slotted annular. Advantageously, the stator can thus be easily adapted to the requirements of the sliding element, for example the thickness or length of the sliding element, by adapting the size of the notch or slot.

[0013] Preferably, the rotor is rotationally symmetrical about its axis of rotation. The rotor is advantageously circular. In particular, the rotor advantageously has no notches that are equivalent to the stator or that are formed at positions of the rotor that are equivalent to the stator (in the stationary state). Advantageously, the rotor has no notches into which the sliding element projects when the actuator is stationary or in operation. This has the particularly advantageous effect that forces that may be caused by the rotation of the rotor and the resulting vibrations and / or noise can be suppressed or avoided as easily as possible by the symmetrical design of the rotor.

[0014] In an advantageous embodiment, the stator has a plurality of stator teeth. These stator teeth are distributed uniformly along the circumferential direction of the stator, wherein the stator has no stator teeth in the recess. In other words, the recess advantageously dispenses with at least one stator tooth. This ensures particularly simple production of the stator, since only one or more stator teeth have to be omitted.

[0015] In an advantageous embodiment, the actuator has a base plate. In this case, the stator teeth are preferably arranged on the base plate. In this case, the base plate is configured for holding the stator teeth and in some embodiments has a holding structure for this purpose. The base plate is preferably annular. The base plate is preferably part of the stator. In an alternative embodiment, the base plate is part of the housing or, for example, part of the aforementioned rotor or another rotor.

[0016] The base plate is preferably designed to close the magnetic circuit of the stator teeth.

[0017] In another advantageous embodiment, the connection between the rotor and the sliding element is configured to convert the rotation of the rotor during operation of the actuator into a radial reciprocating motion of the sliding element through the notch. This allows the sliding element to move at least partially, advantageously radially inside the stator, in particular to move in translation, thereby achieving a compact structural size of the actuator. In this regard, the radial reciprocating motion or radial stroke of the sliding element is the movement / stroke of the sliding element from the inside to the outside of the stator (outward motion) and from the outside to the inside of the stator (inward motion). This movement / stroke does not necessarily have to extend coaxially with the radius of the stator, but can extend coaxially with the radius of the stator.

[0018] In an alternative advantageous design, the connection between the rotor and the sliding element is configured to convert the rotation of the rotor when the actuator is in operation into a reciprocating motion of the sliding element through the notch, perpendicular to the radial direction. Here, the connection can advantageously cause the sliding element to reciprocate along the circumferential direction of the stator. Alternatively or in addition, the connection can advantageously cause the sliding element to reciprocate along the longitudinal direction of the stator, wherein the longitudinal direction of the stator is perpendicular to the radial direction, perpendicular to the circumferential direction and preferably parallel to the axis of rotation of the rotor. For these advantageous designs, the actuator has a reversing, for example (especially by means of a reversing gear transmission). As a result, the actuator can be advantageously used in a variety of applications.

[0019] In an advantageous embodiment with the radial reciprocating motion caused by the sliding element, the rotor preferably has a rotor gear. Here, the sliding element has a toothed rack, which is connected to the rotor gear. Thus, the rotation of the rotor is converted into the rotation of the rotor gear in a compact and simple manner.

[0020] In an advantageous embodiment, the teeth of the rack of the sliding element mesh directly with the teeth of the rotor gear, so that the rack is reciprocated in the radial direction (in particular coaxially with the radius) through the slot of the stator by the rotation of the rotor. This achieves a particularly compact and simple design of the connection between the rotor and the sliding element.

[0021] In a preferred embodiment, the rack of the sliding element is connected to the rotor gear by means of a transmission mechanism. In this case, various types of transmission mechanisms, in particular gear transmission mechanisms, can be used, in particular, depending on requirements such as for reversing the stroke direction. In particular, spur gear transmission mechanisms and planetary transmission mechanisms are advantageous.

[0022] In some preferred embodiments where the transmission mechanism is exemplarily a spur gear transmission mechanism, such a spur gear transmission mechanism is designed as a multi-stage spur gear transmission mechanism.

[0023] In an alternative advantageous design, the toothed rack of the sliding element is connected to the rotor gear by means of a planetary gear mechanism. In other words, the actuator has a planetary gear mechanism, which connects the sliding element to the rotor.

[0024] In a particularly advantageous embodiment, the rotor and the stator form a radial flow machine in which the rotor is arranged radially within the stator. In this case, the stator (with respect to its recess) partially surrounds the rotor in its circumferential direction. This allows a particularly simple and, in particular, very compact design of the actuator in the longitudinal direction (low height).

[0025] Advantageously, the radial flow machine described above is combined with an advantageous design of the connection as a planetary gear or as a direct connection of the rotor gear and the sliding element.

[0026] In a possible combination of a radial flow machine with a planetary gear, the rotor preferably has a substantially semi-closed, hollow cylindrical shape (can also be characterized as a hollow cylinder with a cover and no bottom), wherein the outer surface of the rotor holds the rotor magnets. Here, the rotor advantageously has a rotor gear on its inner side at its radial center. In other words, here, the rotor has a rotor gear on its cover inner surface at the radial center.

[0027] In an alternative advantageous embodiment, the rotor and the stator form an axial flow machine in which the rotor is arranged on the stator along its rotation axis. In other words, the rotor is arranged on the stator along the longitudinal direction of the stator, in particular directly on the stator.

[0028] Advantageously, the above-described axial-flow machine is combined with an advantageous design of the connection as a planetary gear or as a spur gear gear or as a direct connection of the rotor gear and the sliding element.

[0029] Particularly advantageous is the combination of an axial-flow machine with a connected embodiment as a spur gear mechanism, in particular a multi-stage spur gear mechanism. It is particularly advantageous here that the spur gear mechanism is (in particular completely) arranged in a space partially enclosed by the stator. This reduces the overall size of the actuator. In addition, the power density is increased by the adaptation of the operating range of the actuator that can be achieved with the aid of the spur gear mechanism. By increasing the power density, the actuator can be used for higher requirements and / or for a larger range of applications (smaller available space) with smaller overall dimensions at equal requirements.

[0030] In a particularly advantageous embodiment, the multi-stage spur gear transmission has a plurality of spur gears. Advantageously, the spur gear transmission has three or more or four or more spur gears. In an advantageous design, at least one of the spur gears is a double gear.

[0031] In a possible combination of an axial-flow machine with a direct connection between a rotor gear and a sliding element, the rotor gear rests directly against the rack of the sliding element and meshes therein. Here, the rotor is advantageously substantially disc-shaped and has rotor magnets arranged in an annular manner on the side opposite to the stator in relation to the longitudinal direction of the stator. Here, the rotor magnets are advantageously designed in the form of an annular plate, i.e., are formed as a relatively thin ring in relation to the longitudinal direction. Here, the rotor gear extends from the side opposite to the stator in the longitudinal direction into a space partially enclosed by the stator in the circumferential direction in order to reach the rack of the sliding element which extends through a notch into this stator space. This design has the particular advantage that the structural dimensions of the actuator can be reduced, in particular perpendicularly to the longitudinal direction (length, width).

[0032] In a particular embodiment, the rotor magnets are provided as individual plate magnets fastened to the outer surface of the rotor, or as magnets of an annular plate design, as explained above. Alternatively or in addition thereto, the rotor of a radial flow machine or axial flow machine can have rotor magnets of spoke design (rotor set with inserted / embedded permanent magnets).

[0033] The present invention also relates to an actuator-valve unit that solves the above-mentioned problem. The actuator-valve unit has at least a valve and an electromechanical actuator according to the above-mentioned special design. Here, the at least one sliding element of the actuator is connected to the valve, in particular each is connected to one of the valves.

[0034] In the above description, the design of the notch of the sliding element and the stator is described. It should be understood that the stator can have multiple notches, and each of the multiple sliding elements extends through these notches. In addition, it can be realized that multiple sliding elements extend into a single notch of the stator or each of the multiple notches.

[0035] Furthermore, the stator can have a plurality of (especially two) notches, which are in particular opposite to one another with respect to a center point of the stator or with respect to a longitudinal axis of the sliding element. Preferably, the at least one sliding element (in particular each) in the stationary state and / or in operation of the actuator extends at least partially simultaneously or alternately into the plurality of (in particular the two) notches in the notches in the radial direction of the stator.

[0036] As a result, the sliding element can, for example, extend primarily through one notch (as explained above) during a positive stroke (or in a stationary state) and, for example, extend through a further second notch in the stator and through the first notch during a negative stroke. In particular, this can prevent the sliding element from hitting the inner circumference of the stator during a negative stroke.

[0037] As explained above, the sliding element at least partially extends into the notch of the stator when the actuator is at rest and / or in operation. It is particularly advantageous here that the rest state defines the state when the sliding element rests at the center of its entire predefined stroke. With respect to this center of the stroke, a positive stroke is defined in the direction from the radial center point of the stator to the notch of the stator, while a negative stroke is defined in the direction from the notch of the stator to the center point of the stator (opposite to the radial direction, i.e. from the outside to the inside). The positive stroke and the negative stroke are not necessarily of the same length. In other words, the sliding element does not necessarily rest at the center of its entire stroke in the rest state, but preferably at a position defined by zero positive stroke and zero negative stroke (±0 mm stroke).

[0038] In this case, the negative stroke of the sliding element can, for example, reach just before the periphery of the stator opposite the notch. Advantageously, here, "just before" means that the negative stroke reaches at least 70% of the radius from the stator center point to the corresponding side (opposite the notch), advantageously at least 80% of the radius, advantageously at least 90% or at least 95% of the radius. As a result, most of the stroke of the sliding element can be carried out in the stator space, thereby ensuring a particularly compact design of the actuator. As explained above, the stator can have a further notch (second notch) which is opposite to the (first) notch explained above on the stator periphery with respect to the stator center point or with respect to the longitudinal axis of the sliding element. In this case, the extension of the negative stroke can then be equal to or greater than 100% of the radius starting from the stator center point. The negative stroke can, for example, reach a maximum of 105%, preferably 110% or more of the radius.

[0039] Further details, advantages and features of the invention will be apparent from the following description of exemplary embodiments with the aid of the accompanying drawings. In the drawings:

[0040] Figure 1 shows an exploded view of an electromechanical actuator according to a first embodiment of the present invention;

[0041] Figure 2 shows a perspective cross-sectional view of an electromechanical actuator according to a first embodiment of the invention;

[0042] Figure 3 shows another perspective cross-sectional view of an electromechanical actuator according to a first embodiment of the invention;

[0043] Figure 4 shows an exploded view of an electromechanical actuator according to a second embodiment of the present invention;

[0044] Figure 5 shows a perspective sectional view of an electromechanical actuator according to a second embodiment of the invention;

[0045] Figure 6 shows another perspective cross-sectional view of an electromechanical actuator according to a second embodiment of the invention;

[0046] Figure 7 shows an exploded view of an electromechanical actuator according to a third embodiment of the present invention;

[0047] Figure 8 shows a perspective sectional view of an electromechanical actuator according to a third embodiment of the invention;

[0048] Fig. 9 another cross-sectional view showing an electromechanical actuator according to a third embodiment of the present invention; and

[0049] Fig.10 A schematic block diagram of an actuator-valve unit according to one embodiment of the present invention is shown.

[0050] Figure 1 An exploded view of an electromechanical actuator 1 (hereinafter referred to as “actuator 1 ”) according to a first embodiment of the present invention is shown. Figure 2 and Figure 3 A cross-sectional illustration of an assembled state of an actuator 1 according to a first embodiment of the invention is shown.

[0051] about Figure 1 :

[0052] The actuator 1 according to the present embodiment has a cover 15, a circuit board 16, a rotor 2 having a rotor magnet 24, a total of three ball bearings 20, 36, a drive pinion 17, three planetary gears 18, a planet carrier 19, a stator 3, a ring gear 22, a sliding element 5 having a rack 12, a device plug 23, and a housing 14 having an opening 25. The ball bearings 20, 36 include a counter bearing 20 for the rack 12 (see the following description and Figure 2 ) and two pinion bearings 36.

[0053] In the present embodiment, the rotor 2 and the stator 3 form a radial flow machine in which the rotor 2 is arranged within the stator 3 with respect to the radial direction 6 . Figure 1 is a simplified decomposition diagram. Figure 2 In contrast, the rotor 2 is arranged axially between the toothed rack 12 and the toothed ring 22 in the assembled state. In the figures, a single exemplary radial direction 6 is shown. In this context, a “radial direction” is to be understood as any direction extending from the inside to the outside with respect to the stator 3. Since there are (infinitely) many radial directions 6 in this sense, the indefinite article “eine Radialrichtung (a certain radial direction)” is used here.

[0054] The stator 3 has a notch 4. The stator 3 has a slotted annular design. In other words, the stator 3 has a substantially annular shape with a slot-shaped notch 4. In the assembled state (see Figure 2 and Figure 3 ), the sliding element 5 extends through the notch 4 along the radial direction 6 of the stator 3. In other words, the sliding element 5 extends from the inside to the outside of the stator 3. As described below, the sliding element 5 performs a stroke along the radial direction 6. Here, in this embodiment, the sliding element 5 performs a reciprocating motion 34 parallel to the radial direction 6. The sliding element 5 extends through the opening 25 of the housing 14.

[0055] The device plug 23 is electrically connected to the circuit board 16, which in turn is electrically connected to the stator 3. The stator 3 is activated by means of the device plug 23 and by means of the circuit board 16 and feeds a magnetic field to the rotor magnet 24 of the rotor 2. Therefore, the stator 3 causes the rotor 2 to rotate along the rotation axis 7 of the rotor 2 by means of the rotor magnet 24. The rotation of the rotor 2 is converted into a rotation of the drive pinion 17 by means of the planetary gear 21. For this purpose, the planetary gear 21 has a planetary gear 18, a planet carrier 19 and a ring gear 22 in addition to the drive pinion 17. The drive pinion 17 is supported by means of a pinion bearing 36.

[0056] The rotor 2 also has a rotor gear 11, as shown in FIG. Figure 2 The rotor 2 is basically a semi-closed hollow cylinder, and the rotor magnets 24 are fastened to the outer peripheral surface 26 of the hollow cylinder. The outer peripheral surface 26 of the rotor 2 forms the outer surface of the hollow cylindrical rotor 2. In addition, it is known from the semi-closed shape that the rotor 2 has a cover surface 8, and the inner side 9 of the cover surface (such as Figure 2 ), the rotor 2 has a rotor gear 11. The rotor gear 11 is formed integrally with the rotor 2, in particular in one piece.

[0057] Thus, the rotation of the rotor 2 causes the rotation of the rotor gear 11. The rotor gear 11 further causes the rotation of the planetary gears 18, which are supported on the planet carrier 19 in the ring gear 22. The ring gear 22 is fixed in the present embodiment, i.e., does not rotate. The planetary gears 18 revolve around the ring gear 22, while the rotor gear 11 acts as a rotatable sun gear of the planetary transmission 21. The rotation of the planetary gears 18 further causes the rotation of the planet carrier 19, thereby causing the drive pinion 17 connected to the planet carrier 19 to rotate.

[0058] The drive pinion 17 is directly connected to the rack 12 of the sliding element 5, so that the sliding element 5 performs a stroke when the drive pinion 17 rotates. The rack 12 of the sliding element 5 is connected by means of a counter bearing 20 (see in particular Figure 3 ) is supported and pressed against the drive pinion 17. The toothed rack 12 of the sliding element 5 is in particular an integral, in particular one-piece section of the sliding element 5.

[0059] Here, the maximum negative stroke extending from the notch 4 to the opposite side 27 (opposite to the notch 4) along and against (i.e., from the outside to the inside of the stator 3) the radial direction 6 is predefined so that the rack 12 does not collide with the opposite side 27. For example, the maximum negative stroke is predefined so that it reaches up to 90% of the distance from the stator center point 35 (the center point of the drive pinion 17) to the opposite side 27.

[0060] In a particular example, the stroke movement 34 is predefined to ±12.5 mm, so that the entire stroke is 25 mm. The thickness of the sliding element 5 is, for example, 20 mm. In a further advantageous embodiment, the stroke movement 34 is asymmetrical. Here, the stroke movement 34 can be predefined to +10 mm / -5 mm, for example. "+" here means that the rack 12 is away from the stator 12 ( Figures 1 to 3 and “-” means that the rack 12 is pulled into the stator 12 ( Figures 1 to 3 on the right side of the image).

[0061] Instead, from Figure 3 As can be seen by the dashed line in , the stator 2 can have a second notch 38 on the opposite side 27. As a result, the rack 12 can move further than the maximum negative stroke explained above, for example up to or more than 100% of the distance from the stator center point 35 to the opposite side 27, i.e. up to the second notch 38 or through the second notch 38 and, for example, even further.

[0062] Since the stator 3 has the recess 4 , most of the sliding element 5 can be accommodated in the stator 3 , so that the structural size of the actuator 1 can be kept small.

[0063] Furthermore, it can be seen that the stator 3 is designed rotationally asymmetrically with respect to the rotation axis 7 of the rotor 2 due to the recess 4 . The rotor 2 is rotationally symmetrical with respect to its rotation axis 7 .

[0064] Refer to below Figures 4 to 6 Here, the description of the same elements from the first embodiment may be omitted or not repeated. Figure 4 An exploded illustration of an electromechanical actuator 1 according to a second embodiment of the invention is shown. Figure 5 a perspective sectional view showing an electromechanical actuator 1 according to a second embodiment of the invention; and Figure 6 Another perspective cross-sectional view of an electromechanical actuator 1 according to a second embodiment of the invention is shown. Figure 6 In the figure, for simplicity of illustration, the rotor 2 and the cover 15 are omitted, and more specifically, the actuator 1 is shown in a corresponding cutaway manner.

[0065] In the present embodiment, the rotor 2 and the stator 3 form an axial flow machine. Here, the rotor 2 is arranged along its axis of rotation 7 on the stator 3 or above the stator 3 .

[0066] For this purpose, the rotor 2 has an iron core 28 which is substantially disk-shaped and integrally, in particular in one piece, has a rotor gear 11. The rotor gear 11 of this embodiment substantially has a shape similar to the drive pinion 17 of the first embodiment. Here, the rotor gear 11 extends along the rotation axis 7 of the rotor 2 from the opposite side 33 of the stator into a space partially surrounded by the stator 3 in the circumferential direction, so as to reach the rack 12 of the sliding element 5 which extends into this stator space through the notch 4.

[0067] In addition, if Figure 4 It can be seen that the rotor 2 has an annularly arranged rotor magnet 24 on the opposite side 33 of the stator with respect to the rotation axis 7 of the stator 3 (with respect to the longitudinal direction of the stator 3). Here, the rotor magnet 24 is advantageously designed as an annular plate, that is, it is formed as a relatively thin ring with respect to the rotation axis 7. This design has the particular advantage that the structural size of the actuator 1 can be reduced, especially perpendicular to the rotation axis 7 (perpendicular to the longitudinal direction, that is, the length and width). As an alternative to the annular plate-shaped design of the rotor magnet 24, the rotor 2 can have a rotor magnet of a spoke-like design, wherein the rotor 2 is designed as a rotor group with inserted / embedded permanent magnets.

[0068] The stator 3 has a stator winding 29, a stator magnetic circuit 30 and a circuit board 16, wherein the circuit board 16 is in this embodiment (see Figure 5 ) is arranged between the stator winding 29 and the stator magnetic circuit 30. More precisely, the stator magnetic circuit 30 has a base plate 32 (in this example, annular) and a plurality of stator teeth 31, which extend along the rotation axis 7 of the rotor 2 perpendicularly to the base plate 32 in the direction of the rotor 2. The stator winding 29 is wound around the stator teeth 31. The circuit board 16 is arranged between the base plate 32 and the stator winding 29 along the rotation axis 7 and is electrically connected to the stator winding 29 to trigger and excite the stator winding.

[0069] In this embodiment, the stator 3 also has a notch 4. In this embodiment, the notch 4 is formed by omitting at least one stator tooth 31 in the stator 3. Exactly one stator tooth 31 is omitted here. In addition to the notch 4, the stator teeth 31 are evenly distributed along the circumferential direction 10 of the stator 3. As described above with reference to the first embodiment, in this embodiment, the stator 3 can also have a plurality of (especially two, particularly preferably two opposite) notches 4. Here, these additional notches 4 can be formed by omitting other stator teeth 31.

[0070] In addition, the stator winding 29 is not formed at the corresponding position of the notch 4. The substrate 32 is formed continuously at the position of the notch 4, that is, without interruption. The circuit board 16 is also formed continuously at the position of the notch 4, that is, without interruption. Therefore, the stator 3 of the present embodiment, especially the stator magnetic circuit 30 of the stator, is also designed to be non-rotationally symmetrical about the rotation axis 7 of the rotor 2, while the rotor 2 is rotationally symmetrical about its rotation axis 7.

[0071] The sliding element 5 thus projects in the radial direction 6 through the recess 4 of the stator, which is formed by omitting the stator teeth 31 and the corresponding part of the stator winding 29 .

[0072] The stator 3 causes the rotor 2 to rotate by means of the stator winding 29 and the rotor magnets 24. The rotor bearing 37 supports the rotor 2 relative to the housing 14 and relative to the cover 15. The rotation of the rotor 2 is directly converted into a stroke movement (reciprocating movement in the radial direction 6) 34 of the sliding element 5 by means of the teeth of the rotor gear 11 and the rack 12 of the sliding element 5 that mesh with each other. As shown in Figure 6 As can be seen in FIG. 1 , the rack 12 of the sliding element 5 is supported and pressed against the rotor gear 11 by means of the counter bearing 20. Figure 6 It can be seen that the toothed rack 12 is designed here such that the sliding element 5 is arranged in a radial direction, in particular coaxially with the radial direction.

[0073] This allows a particularly compact design of the actuator 1 to be achieved. Furthermore, this allows the actuator 1 to be more optimally expandable for higher requirements, such as greater forces to be achieved by the sliding element 5 or for longer sliding elements 5. In other words, the actuator 1 can also be provided for higher requirements without the structural dimensions of the actuator being excessively increased.

[0074] Refer to below Figures 7 to 9 Here, the description of the same elements from the first embodiment and the second embodiment may be omitted or not repeated. Figure 7 An exploded illustration of an electromechanical actuator 1 according to a third embodiment of the invention is shown. Figure 8 a perspective sectional view showing an electromechanical actuator 1 according to a third embodiment of the invention; and Fig. 9 1 shows a cross-sectional view of an electromechanical actuator 1 according to a third embodiment of the present invention. Fig. 9 In the figure, for simplicity of illustration, the rotor 2 and the cover 15 are omitted, and more specifically, the actuator 1 is shown in a corresponding cutaway manner.

[0075] Similar to the second embodiment, in this embodiment, the rotor 2 and the stator 3 form an axial flow machine. Here, the rotor 2 is arranged along its axis of rotation 7 on the stator 3 or above the stator 3 .

[0076] Furthermore, the electromechanical actuator 1 according to the present embodiment has a spur gear transmission mechanism 40, which will be referred to below. Figures 7 to 9 In this embodiment, the spur gear transmission mechanism 40 is multi-stage.

[0077] The spur gear transmission mechanism 40 has (as in particular from Figure 7 It can be seen that the spur gear transmission mechanism support 45. On this support 45, four spur gears 41-44 are supported on corresponding journals 46. The spur gear transmission mechanism 40 (also as shown) Figure 8 It can be seen that the stator 3 is accommodated in a space which is partially enclosed by the stator 3 (due to the recess 4 ).

[0078] As also in the above embodiment, in this embodiment, the sliding element 5 protrudes through the notch 4 in the radial direction of the stator 3. Here, in this embodiment, the sliding element 5 is oriented and arranged parallel to the radial direction of the stator 3.

[0079] Refer to below Figure 8 and Fig. 9 To explain the working mode of the spur gear transmission mechanism 40. Figure 8 In the perspective cross-sectional illustration of FIG. 1 , the fourth spur gear 44 (which will be further explained below) is not visible.

[0080] The rack 12 of the sliding element 5 is supported by means of a counter bearing 20 and pressed against the rotor gear 11 .

[0081] As explained above, the stator 3 causes the rotor 2 to rotate, wherein the rotor bearing 37 supports the rotor 2 relative to the housing 14 and the cover 15. The rotation of the rotor 2 is transmitted via the rotor gear 11 to the spur gear mechanism 40 and thus to the sliding element 5, as will be explained below.

[0082] The rotor gear 11 (here on a larger outer circumference (with Figure 7 The first spur gear 41 is meshed with the second spur gear 42 (here with a smaller outer circumference), which rotates accordingly. The second spur gear 42 (here with a smaller outer circumference) is meshed with the third spur gear 43, which also rotates accordingly. The third spur gear 43 (here with the same outer circumference) is meshed with the fourth spur gear 44. The first spur gear 41, the second spur gear 42 and the fourth spur gear 44 are double gears, while the third spur gear 43 is a single gear.

[0083] The fourth spur gear 44 meshes with its smaller outer circumference directly into the rack 12 of the sliding element 5 . Therefore, the rotation of the rotor 2 is converted into a stroke movement / reciprocating movement 34 of the sliding element 5 by means of the spur gear transmission 40 .

[0084] In addition to the advantages described above, the axial flow machine in this article with a spur gear transmission mechanism 40 also provides the following advantages. Through the multi-stage spur gear transmission mechanism 40, the adaptation of the mechanical power is introduced into a more favorable working range (higher speed, lower torque) of the actuator 1 (more precisely, the rotor 2, the stator 3), thereby improving its power density. This higher power density in turn causes the volume of active materials (for example, including copper, iron, magnets, etc.) to be reduced, so that the spur gear transmission mechanism 40 can be arranged in the enclosed space described above. Thereby, the structural size of the actuator 1 is reduced under the condition of equal power, so that a wider range of applications can be achieved. By reducing the volume of active materials (which are more costly than the spur gear transmission mechanism 40), the cost of the actuator 1 can be reduced.

[0085] Overall, the present embodiment achieves a relatively high power density in a compact design and at reduced costs.

[0086] Fig.10 A schematic block diagram of an actuator-valve unit 100 according to one embodiment of the present invention is shown.

[0087] The actuator-valve unit 100 has an actuator 1 according to the first embodiment, the second embodiment or the third embodiment. In addition, the actuator-valve unit has a valve 101. The valve 101 is at least partially closed and / or opened by a stroke movement 34 of a sliding element 5 of the actuator 1. In other words, the sliding element 5 in the actuator-valve unit 100 advantageously serves as a valve core.

[0088] In addition to the above written description of the invention, explicit reference is hereby made to the illustrations of the invention in the accompanying drawings for supplementary disclosure.

[0089] List of Reference Numerals 1 Electromechanical actuator (actuator) 2 Rotors

[0090] 3. Stator

[0091] 4. Gap

[0092] 5 Sliding element

[0093] 6 Radial direction

[0094] 7 Axis of rotation

[0095] 8 Cover surface

[0096] 9 Inside

[0097] 10 Circumferential direction

[0098] 11 Rotor gear

[0099] 12 Rack

[0100] 14 Housing

[0101] 15 Cover

[0102] 16 Circuit Board

[0103] 17 Drive pinion

[0104] 18 Planetary gear

[0105] 19 Planet carrier

[0106] 20 Opposed bearings

[0107] 21 Planetary transmission mechanism

[0108] 22 Ring gear

[0109] 23 Equipment plug

[0110] 24 Rotor magnets

[0111] 25 Opening

[0112] 26 Outer Surface

[0113] 27 Opposite side

[0114] 28 Iron Core

[0115] 29 Stator winding

[0116] 30 Stator magnetic circuit

[0117] 31 stator teeth

[0118] 32 substrate

[0119] 33 Opposite side

[0120] 34 stroke motion / reciprocating motion

[0121] 35 Stator center point

[0122] 36 Pinion bearing

[0123] 37 Rotor bearing

[0124] 38 Second Gap

[0125] 40 Spur gear transmission mechanism

[0126] 41 First spur gear

[0127] 42 Second spur gear

[0128] 43 Third spur gear

[0129] 44 Fourth spur gear

[0130] 45 Spur gear transmission mechanism bracket

[0131] 46 Journal

[0132] 100 Actuator-valve unit

[0133] 101 Valve

Claims

1. An electromechanical actuator (1), comprising: Rotor (2); A stator (3) having a notch (4); and at least one sliding element (5) which is in operative connection with the rotor (2) and is moved by the rotation of the rotor (2), wherein The sliding element (5) at least partially extends into the recess (4) along the radial direction (6) of the stator (3) when the actuator (1) is in operation and / or in a stationary state.

2. The electromechanical actuator (1) according to claim 1, wherein the stator (3) is non-rotationally symmetric with respect to the axis of rotation (7) of the rotor (2).

3. The electromechanical actuator (1) according to one of the preceding claims, wherein the rotor (2) is rotationally symmetrical about its axis of rotation (7).

4. An electromechanical actuator (1) according to one of the preceding claims, wherein the stator (3) has a plurality of stator teeth (31) on a base plate (32) that is in particular annular, wherein the stator teeth (31) are evenly distributed along a circumferential direction (10) of the stator (3), and wherein the stator (3) has no stator teeth (31) in the recess (4).

5. An electromechanical actuator (1) according to one of the preceding claims, wherein the connection between the rotor (2) and the sliding element (5) is configured to convert the rotation of the rotor (2) when the actuator (1) is in operation into a reciprocating motion (34) of the sliding element (5) through the gap (4) along the radial direction (6) of the stator (3).

6. The electromechanical actuator (1) according to claim 5, wherein the rotor (2) has a rotor gear (11), and the sliding element (5) has a rack (12) connected to the rotor gear (11).

7. The electromechanical actuator (1) according to claim 6, wherein the rack (12) of the sliding element (5) is connected to the rotor gear (11) by means of a planetary gear (21) or by means of a spur gear gear (40).

8. The electromechanical actuator (1) according to one of the preceding claims, wherein the rotor (2) and the stator (3) form a radial flow machine in which the rotor (2) is arranged radially inside the stator (3).

9. An electromechanical actuator (1) according to one of claims 1 to 7, wherein the rotor (2) and the stator (3) form an axial flow machine in which the rotor (2) is arranged on the stator (3) along its axis of rotation (7).

10. An actuator-valve unit (100) having at least a valve (101) and an electromechanical actuator (1) according to one of the preceding claims, wherein at least one sliding element (5) of the actuator (1) is connected to the valve (101).

Images