Actuator comprising an electric motor and a linear drive

Abstract

The present invention relates to an actuator (1) comprising an electric motor (75) having a rotor shaft (81) with a pinion (82). The actuator (1) also comprises a linear drive (2) having a spindle (50) and having a gear wheel (80), wherein the spindle (50) and the gear wheel (80) are accommodated in an actuator housing (40), the spindle in a rotationally fixed manner and the gear wheel in an axially fixed and rotatable manner. The gear wheel (80) has internal toothing (83) which meshes with a profiling (84) of the spindle (50) in such a way that a rotational movement of the gear wheel (80) is converted into a movement of the spindle (50) in an axially extending movement direction (41). The pinion (82) is torque-transmittingly coupled to the gear wheel (80), preferably by means of spur gear toothing, and the spindle (50) is arranged parallel to, radially offset from, and axially overlapping with the rotor shaft (81) and / or the electric motor (75). Furthermore, the gear wheel (80) is mounted in the actuator housing via precisely one bearing (90).

Description

[0001] Actuator with an electric motor and a linear drive

[0002] The present invention relates to an actuator with an electric motor, comprising a rotor shaft with a pinion, a linear drive with a spindle and with a gear. The spindle is rotationally fixed and the gear is axially fixed and rotatably accommodated in an actuator housing. Furthermore, the gear has internal teeth that mesh with a profile of the spindle such that a rotational movement of the gear is converted into a movement of the spindle in an axial direction. The pinion is coupled to the gear in a torque-transmitting manner, preferably by means of spur gear teeth. The spindle is arranged parallel to, radially offset from, and axially overlapping with the rotor shaft and / or the electric motor.

[0003] Such actuators are already known from DE 102016 207 827 A1, which provide a nonlinear actuation force for an actuation unit for an automatic transmission (preferably a PRND automatic transmission system) of a motor vehicle. A corresponding guide track is provided to generate the nonlinearity.

[0004] The present invention aims to provide a generic actuator in a simple, safe and compact manner.

[0005] This object of the invention is achieved by a generic actuator having the features of claim 1. Further embodiments are described in the subclaims.

[0006] It is provided that the gear, which on the one hand meshes with the spindle via an internal toothing and on the other hand is coupled to the pinion of the rotor shaft, is mounted in the actuator housing via a bearing, preferably via exactly one bearing. This allows forces acting radially and / or axially on the gear to be supported while at the same time saving space. In particular, it is also possible to support forces acting radially on the spindle. According to the invention, it is further provided that the electric motor has a motor housing and that the bearing is accommodated and supported by a bearing holder. The bearing holder is firmly connected to the actuator housing and in particular is formed integrally and from a single material from the actuator housing. According to the invention, the bearing holder is arranged between the bearing and the motor housing in such a way that the radial and / or axial position of both the bearing and the motor housing is thereby fixed.

[0007] For further optimization of the design, the bearing can be arranged radially and / or axially overlapping the electric motor or an electric motor housing with respect to the spindle. The axial direction corresponds to the axial direction of movement of the spindle, while the radial direction is orthogonal to this.

[0008] A stable, compact and also testable unit can be created by providing that the actuator housing accommodates the linear drive and the electric motor. Furthermore, it can also be provided that the actuator housing has a partition wall which is arranged radially between the linear drive and the electric motor. This partition wall can, for example, be arranged at a radial distance from the axis of rotation of the rotor shaft and at least partially enclosing it in the circumferential direction such that the electric motor is accommodated by this partition wall. Assembly can then be facilitated by inserting the electric motor with its electric motor housing into the space formed by the partition wall and possibly an outer wall of the actuator housing and supporting it there in the radial direction with respect to the rotor shaft. Furthermore, the electric motor can be rotationally supported on the partition wall and / or the actuator housing in the circumferential direction.

[0009] In a further development, it can be provided that the bearing holder radially encloses a bearing outer ring of the bearing and the bearing holder has a first and a second radial projection, wherein the first radial projection bears axially on the bearing outer ring and does not project radially inwards beyond the bearing outer ring. The first radial projection lies axially between the gear and the bearing. In particular, it can be provided that the gear has, on the one hand, a radially extending part which has the toothing at the radial end and, on the other hand, an axially extending part which forms the radially inner region of the gear. The first radial projection can then be axially nested with the radially inner region and arranged axially between the radial part and the bearing outer ring. The second radial projection can also bear axially on the bearing outer ring, wherein it projects radially inwards beyond it.It lies axially between the bearing or bearing outer ring and the motor housing. This means that the first and second radial projection lie on opposite axial end faces of the bearing outer ring and thus fix the bearing axially in relation to the housing and the motor housing. In particular, the first radial projection, which does not project radially beyond the bearing outer ring, is assigned to the axial end face of the bearing outer ring that points axially away from the motor housing of the electric motor. This first radial projection can be a flanged rim that is only flanged after the bearing has been inserted into the bearing mount, while the other radial projection is a fixed rim. In this way, the position of the bearing in the axial direction in relation to the housing, the motor housing and the gear, or the radially extending part of the gear, can be fixed.Through this interaction, the axial position of the motor via the motor housing and the axial position of the gear via its radially extending part are simultaneously determined relative to each other and to the housing.

[0010] In a further development, it can be provided that the bearing receptacle has a circumferential region running axially from the first radial projection to the second radial projection, and at least part of the second projection and part of the circumferential region bear axially or radially against the motor housing of the electric motor. By means of the circumferential region bearing radially against the motor housing, at least the gear and possibly also the spindle can be supported radially, in particular on the actuator housing. The same then applies to axial support of the bearing via the bearing outer ring on the motor housing and thus on the actuator housing. In this case, at least the axially fixed gear can be fixed in its axial position. By means of this bearing receptacle, the bearing, the motor housing and also the gear can be fixed in relation to one another and to the housing in the radial direction and / or as described above in the axial direction.

[0011] A particularly space-saving design, in which both the gear and the spindle are at least radially supported, is achieved if the gear has an axially extending hub portion, the hub portion has internal teeth radially inside for establishing a toothing with the spindle, and a bearing seat radially outside for the bearing. In particular, it can be provided that the internal teeth, i.e., the toothing area with the spindle, and the bearing seat, are nested radially and axially with one another.

[0012] A particularly space-saving mechanism for converting a linear movement of the linear drive, in particular a linear movement of the spindle, into a rotary movement, which can be used, for example, to actuate a parking lock and which advantageously also has a non-linear characteristic, can be achieved in a further development by providing a gear for converting the linear movement of the linear drive into a rotary movement, wherein the gear comprises a lever which rotates a shaft to be subjected to a torque. Furthermore, the gear has a coupling element which is connected to the linear drive, in particular to a component of the spindle, via a first connection point and to the lever via a second connection point. This arrangement is designed such that energy is transferred between the linear drive and the lever exclusively via the coupling element.Furthermore, it is provided that the coupling element is rotatably mounted in both connection points.

[0013] In a further development of the actuator, it is additionally provided that the lever is connected at a second lever end via a third connection point in a rotationally fixed manner to the shaft and at a first lever end via the second connection point in a rotationally fixed manner to the coupling element, and the lever creates a rigid connection between the two connection points. The coupling element creates a rigid connection between the first and second connection points, so that a linear movement of the first connection point by the linear drive results in a first pivoting movement of the second connection point about the first connection point, as well as in a second pivoting movement of the second connection point about the third connection point, so that due to the rotationally fixed connection of the lever to the shaft, the second pivoting movement causes the shaft to rotate. The coupling element further connects the lever and the linear drive, orthe spindle with each other in such a way that the second connection point is moved along a trajectory curve, so that in a first working range around a first end point of the trajectory curve a movement of the first connection point is translated by the linear drive into a first rotational movement of the shaft and in a second working range around a second end point a movement of the first connection point is reduced by the linear drive into a second rotational movement of the shaft, wherein the first rotational movement covers a larger angular range with a smaller force transmission in a time interval than the second rotational movement and in the second end point the coupling element is aligned perpendicular to the lever and to the movement axis of the linear drive and the lever is aligned parallel to the movement axis.

[0014] A non-linear characteristic curve of the shaft can preferably be achieved by connecting the lever at a second lever end to the shaft via a third connection point and at a first lever end to the coupling element via the second connection point. The lever establishes a rigid connection between the two connection points, while the coupling element establishes a rigid connection between the first and second connection points. In this way, a linear movement of the first connection point, which is caused by the linear drive, results in a first pivoting movement of the second connection point around the first connection point.At the same time, however, this linear movement also causes a second pivoting movement of the second connection point around the third connection point, so that due to the rotationally fixed connection of the lever to the shaft, the second pivoting movement causes a rotation of the shaft.

[0015] The coupling element connects the lever to the linear drive in such a way that the second connection point is moved along a trajectory curve, in which, in a first working range around a first end point of the trajectory curve, a movement of the first connection point is translated by the linear drive into a first rotational movement of the shaft. In a second working range around a second end point of the trajectory curve, a (linear) movement of the first connection point is reduced by the linear drive into a second rotational movement of the shaft. In this context, “reduced” and “over-reduced” means that the first rotational movement covers a larger angular range in a time interval with a smaller force transmission than the second rotational movement: when the first rotational movement is generated, a transmission takes place, and when the second rotational movement is generated, a reduction takes place.At the first end point, the coupling element is aligned parallel to the linear drive's axis of motion and perpendicular to the lever. This describes an arrangement in which, for example, when a linear drive spindle is retracted (first end point), a maximum torque is exerted on the then vertically positioned lever by a parallel arrangement of the coupling element and spindle. As the spindle advances further from the retracted position, the torque decreases.

[0016] In an alternative development, the lever is connected at a first lever end via a third connection point in a rotationally fixed manner to the shaft and at a second lever end via the second connection point in a rotationally fixed manner to the coupling element. The lever thereby establishes a rigid connection between the two connection points. The coupling element establishes a rigid connection between the first and second connection points, such that a linear movement of the first connection point by the linear drive results in a first pivoting movement of the second connection point about the first connection point and also in a second pivoting movement of the second connection point about the third connection point. Due to the rotationally fixed connection of the lever to the shaft, the second pivoting movement causes a rotation of the shaft.The coupling element connects the lever and the linear drive in such a way that the second connection point is moved along a trajectory. In a first operating range around a first end point of the trajectory, a movement of the first connection point is translated by the linear drive into a first rotational movement of the shaft. In a second operating range around a second end point of the trajectory, a movement of the first connection point is translated by the linear drive into a second rotational movement of the shaft, whereby the first rotational movement covers a larger angular range in a time interval with a smaller force transmission than the second rotational movement. At the first end point, the coupling element is aligned parallel to the movement axis of the linear drive and perpendicular to the lever. This is the reverse arrangement to the first alternative described.In this case, the coupling element and the spindle are initially parallel, particularly adjacent to each other or overlapping, when the spindle is extended. The maximum torque is then transmitted when the spindle is extended and the spindle moves to retract. An example of the invention, to which it is not limited and from which further inventive features may arise, is shown in the following figures. They show:

[0017] Fig. 1 : a cross section through an actuator,

[0018] Fig. 2: a perspective view of an actuator according to Fig. 1 , and

[0019] Fig. 3: a symbolic representation of a trajectory curve of the lever for shaft actuation,

[0020] The structure of the actuator 1 is first explained using the example of Figs. 1 and 2.

[0021] Fig. 1 shows an actuator 1 for converting a rotational movement of a rotor shaft 81 into a rotational movement of a shaft 5, in particular via an intermediate linear movement of a linear drive 2.

[0022] First, an electric motor 75 generates a torque, which is transmitted to the rotor shaft 81. The torque is transmitted to a spindle 50 of the linear drive 2 via a gear stage 74. The gear stage 74 comprises a pinion 82 on the rotor shaft 81 and a gear 80, which is rotationally fixedly coupled to the spindle 50 via an internal toothing 83 of a toothing point 72. Pinion 82 and gear 80 are coupled to one another via intermeshing toothings. The gear 80 is arranged axially fixed in an actuator housing 40 and represents a nut 71 of the linear drive 2. A rotational movement of the gear 80 sets the spindle 50 into an axial linear movement along a movement axis 41.

[0023] The spindle 50 has an end cap 51, which is connected here to a coupling element 6 via a support roller 52. A one-sided connection via exactly one support roller 52, as well as a connection via support rollers 52 arranged on both sides, each with its own coupling element 6, can be provided, as shown in Fig. 2.

[0024] The support roller 52 represents a first connection point 7 for the rotatable mounting of the coupling element 6. As shown in Fig. 2, the coupling element 6 is designed as a linearly extending, rigid sheet metal part, which is connected at one end via the first connection point 7 to the spindle 50 and via a second connection point 8 at the second end to a lever 4. The coupling element 6 is also rotatably mounted on the lever 4 via the second connection point 8.

[0025] The lever 4 extends from its first lever end 9 with the second connection point 8 to a third connection point 10 at the second lever end 11. The lever 4 is rotationally connected to the shaft 5 at the third connection point 10. For this purpose, the lever 4 has a hole 53 with an internal toothing 54. The shaft 5 has a corresponding external toothing 55, which engages with the internal toothing 54. Fig. 1 shows that the shaft 5 is rotatably mounted in an actuator housing 40. It passes through the actuator housing 40 in the direction of a shaft axis 56. The shaft axis 56 runs perpendicular both to the movement axis 41 of the spindle 50 and to the extension direction 57 of the coupling element 6.

[0026] Outside the actuator housing 40, the shaft 5 is connected to an actuating element 60 (not shown here). This can be an eccentric disc, a contour disc, or the like, which is rotated or pivoted by the shaft 5. This actuating element can then be used to actuate a parking lock, a brake, a clutch, or the like.

[0027] Spindle 50, end cap 51, coupling element 6 and lever 4 are components of a gear 3, which converts a linear movement of the spindle 50 of the linear drive 2 into a rotational movement 23,24 of the shaft 5 to drive the said actuating element.

[0028] As shown in Fig. 1, the gear 80 is mounted in the actuator housing 40 via exactly a single bearing 90. The bearing 90 has an inner bearing ring 98 and an outer bearing ring 93. The gear 80 comprises a hub 86 which extends in the radial direction from the common toothing with the pinion 82 as far as the spindle 50 and to which a hub section 85 adjoins in the axial direction, radially on the inside. The hub section 85 has a bearing seat 97 radially on the outside for receiving the bearing inner ring 98. Radially on the inside, the hub section 85 has the internal toothing 83 which overlaps radially and axially with the bearing seat 97, i.e. the bearing seat 97 and the internal toothing 83 are nested. The bearing seat 97, like the bearing 90 itself, has two axial end faces. One end face, the hub side, faces the hub 86, the other end face, the motor side, faces the electric motor 75.The hub side of the bearing seat 97 comprises a step against which the bearing inner ring 98 is axially supported, while the bearing inner ring 98 is axially supported on the motor side by a retaining ring which is inserted into a groove provided there after the bearing inner ring 98 has been inserted onto the hub section 85.

[0029] The bearing outer ring 93 is received in a bearing receptacle 92. The bearing receptacle 92 is fixedly connected to the actuator housing 40 and is formed integrally therefrom. The bearing receptacle 92 is formed by a first radial projection 94 and a second radial projection 95, which are connected to one another via a circumferential region 96. The first radial projection 94 is formed on the hub side. Its radially inner end is aligned with the radial inside of the bearing outer ring 93. The second radial projection 95 is provided on the motor side of the bearing outer ring 93 and is preferably formed by flanging in the radial direction after the bearing 90 has been inserted into the bearing receptacle 92. The second radial projection 95 then projects radially inward beyond the bearing outer ring 93.

[0030] The electric motor 75 is housed in a motor housing 76. The electric motor 75 comprises at least a stator and a rotor, which is connected in a rotationally fixed manner to the rotor shaft 81. Both the stator and the rotor are housed in the motor housing 76 and are therefore not shown in the figures. The motor housing 76 has at least one axial step, so that the second radial projection 95 rests completely on the motor housing 76 in the axial direction and the circumferential region 96 partially rests on the motor housing 76 in the radial direction. The motor housing 76 and thus the electric motor 75 are thus at least partially fixed axially and radially by the bearing mount 92.

[0031] The actuator housing 40 completely accommodates the electric motor 75 with its motor housing 76, the rotor shaft 81, the gear stage 74, the linear drive 2 and the gearbox 3. The gearbox 3 and the linear drive 2 are arranged radially outside the motor housing 76, with the gearbox 3 being separated from the motor housing 76 by a partition wall 91. The partition wall 91 extends axially through the actuator housing 42 and separates the interior of the actuator housing 40 into a motor compartment 87 and a gearbox compartment 88. The partition wall 91 does not extend completely through the actuator housing 40, leaving a gap in which the gear stage 74 connects the rotor shaft 81 in the motor compartment 87 via the hub 87 of the gear 80 to the spindle 50 of the linear drive 2 in the gearbox compartment 88. The partition wall 91 also serves to radially support and fix the motor housing 76.

[0032] The bearing receptacle 92 is formed from the actuator housing 40 such that it is arranged on the one hand in the gear chamber 88 and on the other hand in the motor chamber 87 and axially adjoins the partition wall 91. The motor housing 76 is constructed essentially rotationally symmetrically to the rotor rotation axis 26. The gear-side step 28 of the motor housing 76 corresponds radially on the one hand with the circumferential region 96 and on the other hand with a corresponding step 29 of the actuator housing 40. The step 28 of the motor housing 76 further corresponds axially with the second radial projection 95 of the bearing receptacle 92, as well as with the step 29 of the actuator housing 40, so that the motor housing 76 is axially and radially fixed by the step 29, the bearing receptacle 92 and the partition wall 91.

[0033] The gear 80 has a motor-side end face which is cup-shaped and has the external toothing 73 on the radial outside for engagement with the pinion 81. Extending axially radially inward from the hub 86 of the gear 80 is the hub section 86, which forms the bearing recess 92 on the radial outside and the internal toothing 83 on the radial inside. The gear 80 is mounted in the actuator housing 40 exclusively via the bearing 90 arranged in the bearing recess 92. The spindle 50 meshes with the internal toothing 83 and is thus also mounted in the actuator housing 40 via the bearing 90. The bearing 90 is axially fixed, so that the gear 80 is axially supported thereby and thus causes the axial lifting movement of the spindle 50. The spindle 50 is supported in the radial direction by the bearing 90 and by the support rollers 52 of the first connection point 7 of the coupling element 6. For this purpose, the support rollers 52 are arranged in corresponding receptacles or recesses provided in the actuator housing 40.Grooves in the axial direction. The actuator housing 40 has an internal contour 42 for this purpose. This contour 42 is embossed into the actuator housing 40 parallel to the spindle 50 and serves to accommodate a support roller 52. Corresponding contours 42 are preferably embossed into the actuator housing on both sides of the spindle 50. The support rollers support the spindle 50 on the actuator housing 40, wherein the support rollers 52 coincide with the first connection point 7. The support rollers 52 are supported on correspondingly positioned support surfaces 44 of the contour 42 in the actuator housing 40 and roll there. In this way, the efficiency of the actuator 1 can be improved (in principle I, plain bearings on one or both sides are also conceivable). The support surfaces 44 preferably run parallel to the movement axis 41 of the spindle 50 or the linear drive 2.

[0034] The movement axis 41 of the spindle 50 is parallel to the rotation axis 27. The gear unit 3 is located radially spaced from the electric motor 75 and is preferably completely axially overlapped by the motor housing 76. In the extended state, a large part of the spindle 50 is also located in the axial overlap area of ​​the motor housing 76. However, an axially projecting part of the spindle 50 is always in engagement with the internal gearing 83 of the gearing point 72. The actuator housing 40 is initially designed in the motor compartment 87 such that it accommodates the motor housing 76 and holds it axially and radially using the partition wall. Furthermore, the actuator housing 40 in the gear compartment 88 is designed such that it restricts the freedom of movement of the gear unit 3.Stops can be provided on the inside of the actuator housing 40, which limit the axial advance of the spindle 50 along the movement axis 41 by the spindle 50 striking this stop with the end cap 51 when it is fully disengaged. The position of the stop, or the dimensions of the actuator housing 40, are here particularly dimensioned such that in this second position P2 the coupling element 6 is substantially perpendicular to the spindle 50. For the opposite position P1, i.e. the position in which the spindle is to be fully retracted, a second stop is provided on the inside of the actuator housing 40. This stop can, for example, be provided such that the lever 4 strikes this second stop with its first lever end and is thus limited in its pivoting movement. In the position shown in Fig.1, however, the stop is provided on the side of the spindle 50 facing away from the lever, on the inside of the actuator housing 40, so that here too the movement of the spindle 50 is limited. Overall, the dimensions of the actuator housing 40 and / or the positions of the stops are determined such that the movement of the spindle 50, or the angular position of the shaft 5, can only take place between two extreme positions P1 and P2, which ensure a bijective, non-linear course of the transmitted torque or the rotational speed of the shaft 5. This means that in a first position P1, a maximum torque (minimum rotational speed) is transmitted when the spindle 50 is moved in the then only possible direction, and in the second position P2, a minimum torque (maximum rotational speed) is transmitted.

[0035] In Fig. 1 and Fig. 2, the spindle 50 is in the second position P2, as a result of which the direction of extension 57 of the coupling element 6 is practically parallel to the movement axis 41 of the spindle 50 and to the lever 4. In position P2, the spindle 50 is practically fully retracted and the second connection point 8 is located at a first end point 21. If the spindle 50 is extended, the travel path of the spindle 50 is coupled to a maximum travel path of the second connection point 8 perpendicular thereto via the coupling element 6. This means that in this case the linear movement of the linear drive 2 is converted into a first rotational movement 23 of the shaft 5. In this case, an initially minimal torque is transmitted to the shaft 5 at a maximum rotational speed.

[0036] An illustration of the transmitted torque and the associated rotational speed is shown in Fig. 3. In the left-hand part of Fig. 3, the second connection point 8 is located at a second end point 22. In the right-hand part, it is located at a first end point 21, as also shown in Figs. 1 and 2. At the second end point 22 of the second connection point 8, the first connection point 7 of the coupling element 6 is located on the movement axis 41 of the spindle 50. A linear movement for retracting the spindle 50 in the direction 61 pulls the lever 4 via the second connection point 8 into a second rotational movement 24 around the third connection point 10. The second connection point 8 follows a trajectory curve 20 with the distance r between the second connection point 8 and the third connection point 10. This movement of the lever 4 is characterized by a minimum rotational speed and a maximum torque at the second end point 22.In the right-hand part of Fig. 3, the second connection point 8 is located at a first end point 21. Here, the spindle 50 is retracted so far that the lever element 4 lies practically completely parallel to the spindle 50 on the movement axis 41. Extending the spindle 50 then leads to a maximum rotational speed and minimum torque of the lever 4. In Figures 1 and 2, the second connection point 8 is located at this first end point 21.

[0037] In the area between the two end points 21, 22, the lever 4 is thus driven with a nonlinear torque characteristic. Shaft 5 is driven accordingly, and the nonlinear characteristic of shaft 5 can be used to actuate a nonlinear load, such as a parking lock.

[0038] The described design of the actuator 1 enables a compact actuator 1 which is stably constructed, requires only a minimum of space, is particularly short in the axial direction and furthermore enables a non-linear characteristic curve for the rotational movement of the shaft 5 both with regard to the rotational speed and the output torque.

[0039] List of reference symbols

[0040] Actuator

[0041] Linear drive

[0042] Gearbox

[0043] lever

[0044] Wave

[0045] Coupling element first connection point second connection point first lever end third connection point second lever end trajectory curve first end point second end point first rotational movement second rotational movement first pivoting movement second pivoting movement rotor rotation axis

[0046] Level

[0047] Actuator housing movement axis contour

[0048] Support surfaces

[0049] spindle

[0050] End cap

[0051] Support roller

[0052] Hole

[0053] Internal toothing External toothing Shaft axis 7 Direction of extension 1 Direction 1 Nut 2 Toothing point 3 External toothing 4 Gear stage 5 Electric motor 6 Motor housing 0 Gear 1 Rotor shaft 2 Pinion 3 Internal toothing 4 Profiling 5 Hub section 6 Hub 7 Motor compartment 8 Gear compartment 0 Bearing 1 Partition wall 2 Bearing holder 3 Bearing outer ring 4 First radial projection

[0054] 95 second radial projection

[0055] 96 circumference range

[0056] 97 warehouse location

[0057] 98 bearing inner ring

[0058] P1 , P2 spindle positions

Claims

Patent claims 1. Actuator (1) with an electric motor (75), comprising a rotor shaft (81) with a pinion (82), a linear drive (2) with a spindle (50) and with a gear (80), wherein the spindle (50) and the gear (80) are axially fixed and rotatably received in an actuator housing (40), the gear (80) has an internal toothing (83) which meshes with a profiling (84) of the spindle (50) such that a rotary movement of the gear (80) is converted into a movement of the spindle (50) in an axially extending direction of movement (41), the pinion (82) is coupled to the gear (80) in a torque-transmitting manner, preferably by means of a spur gear, and the spindle (50) is arranged parallel, radially offset and axially overlapping to the rotor shaft (81) and / or the electric motor (75), wherein the gear (80) is mounted in the actuator housing via a bearing (90), characterized in that the electric motor (75) has a motor housing (76), a fixedly connected to the actuator housing (40),in particular, a bearing receptacle (92) formed integrally and in one piece from the actuator housing (40) receives and supports the bearing (90), and the bearing receptacle (92) is arranged between the bearing (90) and the motor housing (76) in such a way that the radial and / or axial position of both the bearing (90) and the motor housing (76) is thereby fixed.

2. Actuator (1) according to claim 1, characterized in that the bearing (90) is arranged in the radial and / or axial direction with respect to the spindle (50) overlapping the electric motor (75) or a motor housing (76) of the electric motor (75).

3. Actuator (1) according to one of claims 1 or 2, characterized in that the actuator housing (40) accommodates the linear drive (2) and the electric motor (75) and has a partition wall (91) which is arranged radially between the linear drive (2) and the electric motor (75).

4. Actuator (1) according to one of the preceding claims, characterized in that the bearing receptacle (92) radially encloses a bearing outer ring (93) of the bearing (90), the bearing receptacle (92) has a first and a second radial projection (94, 95), wherein the first radial projection (94) axially bears against the bearing outer ring (93), does not project radially inward beyond the bearing outer ring (93) and is arranged axially between the gear wheel (80) and the bearing (90), and wherein the second radial projection (95) axially bears against the bearing outer ring (93), projects radially inward beyond it and is arranged axially between the bearing (90) and the motor housing (76).

5. Actuator (1) according to claim 4, characterized in that the bearing receptacle (92) has a circumferential region (96) extending axially from the first radial projection (94) to the second radial projection (95) and at least a part of the second projection (95) and a part of the circumferential region (96) abut axially or radially on the motor housing (76).

6. Actuator (1) according to one of the preceding claims, characterized in that the gear wheel (80) has an axially extending hub section (85), the hub section (85) has the internal toothing (83) radially on the inside and a bearing seat (97) for the bearing (90) radially on the outside, wherein the internal toothing (83) and the bearing seat (97) are nested radially and axially.

7. Actuator (1) according to one of the preceding claims, characterized in that a gear (3) is provided for converting the linear movement of the linear drive (2) into a rotary movement, wherein the gear (3) comprises a lever (4) which drives a shaft (5) to be subjected to a torque, the gear (3) further comprises a coupling element (6), the coupling element (6) is connected via a first connection point (7) to the linear drive (2) and via a second connection point (8) to the lever (4). so that energy is transferred between the linear drive (2) and the lever (4) exclusively via the coupling element (6), and the coupling element (6) is rotatably mounted in both connection points (7, 8).

8. Actuator (1) according to claim 7, characterized in that the lever (4) is connected at a second lever end (11) via a third connection point (10) to the shaft (5) in a rotationally fixed manner and at a second lever end (9) via the second connection point (8) to the coupling element (6) in a rotationally fixed manner, and the lever (4) establishes a rigid connection between the two connection points (8, 9), the coupling element (6) establishes a rigid connection between the first and second connection points (7, 8), so that a linear movement of the first connection point (7) by the linear drive (2) results in a first pivoting movement (25) of the second connection point (8) about the first connection point (7), as well as in a second pivoting movement (26) of the second connection point (8) about the third connection point (10), so that due to the rotationally fixed connection of the lever (4) to the shaft (5), a rotation of the shaft (5) is caused by the second pivoting movement (26). becomes,the coupling element (6) connects the lever (4) and the linear drive (2) in such a way that the second connection point (8) is moved along a trajectory curve (20), so that in a first working range around a first end point (21) of the trajectory curve (20), a movement of the first connection point (7) is translated by the linear drive (2) into a first rotational movement (23) of the shaft (5), and in a second working range around a second end point (22), a movement of the first connection point (7) is translated by the linear drive (2) into a second rotational movement (24) of the shaft (5), wherein the first rotational movement (23) covers a larger angular range in a time interval with a smaller force transmission than the second rotational movement (24), and at the second end point (22), the coupling element (6) is oriented perpendicular to the lever (4) and to the movement axis (41) of the linear drive (2), and the lever (4) is oriented parallel to the movement axis (41).

9. Actuator (1) according to claim 7 or 8, characterized in that the lever (4) is connected at a second lever end (10) via a third connection point (10) to the shaft (5) in a rotationally fixed manner and at a second lever end (9) via the second connection point (8) to the coupling element (6), and the lever (4) establishes a rigid connection between the two connection points (8, 10), the coupling element (6) establishes a rigid connection between the first and second connection points (7, 8), so that a linear movement of the first connection point (7) by the linear drive (2) results in a first pivoting movement (25) of the second connection point (8) about the first connection point (7), as well as in a second pivoting movement (26) of the second connection point (8) about the third connection point (10), so that due to the rotationally fixed connection of the lever (4) to the shaft (5) by the second pivoting movement (26), a rotation of the shaft (5) caused,the coupling element (6) connects the lever (4) and the linear drive (2) in such a way that the second connection point (8) is moved along a trajectory curve (20), so that in a first working range around a first end point (21) of the trajectory curve (20), a movement of the first connection point (7) is translated by the linear drive (2) into a first rotational movement (23) of the shaft (5), and in a second working range around a second end point (22), a movement of the first connection point (7) is translated by the linear drive (2) into a second rotational movement (24) of the shaft (5), wherein the first rotational movement (23) covers a larger angular range in a time interval with a smaller force transmission than the second rotational movement (24), and at the first end point (21), the coupling element (6) is aligned parallel to the movement axis (41) of the linear drive (2) and perpendicular to the lever (4).

Images