drive, in particular spindle drive

Abstract

The present invention relates to a driver for adjusting an adjusting element (2) of a motor vehicle (3), wherein the driver (1) has a transmission system (4) having two driving parts that are adjustable relative to each other between a retracted position and an extended position along a geometric drive axis (14), and having a plurality of transmission system components coupled to each other in a force or torque transmission manner to transmit forces introduced into drive couplings (8, 9), wherein the driver (1) has a feed gear (7) for performing particularly linear drive motion along the geometric drive axis (14), wherein one of the two driving parts has a drive unit (15) with a drive motor (5) connected downstream thereto by the feed gear (7), wherein the drive motor (5) has a motor shaft (6) having a geometric motor shaft axis (16) and transmitting torque generated by the drive motor (5), and a bearing assembly (17) having at least one motor shaft bearing (11) having a geometric bearing central axis (18) and being configured to radially support the motor shaft (6). The recommended driver (1) has a radial force introduction unit (19) which, in the assembled state, is radially applied to the rotating motor shaft (6) such that the motor shaft (6) abuts against one side of the motor shaft bearing (11) in a defined manner.

Description

[0001] The present invention relates to the drive as described in the preamble of claim 1, particularly a spindle drive.

[0002] The actuators discussed can be used for all possible adjusting elements of a motor vehicle. Examples of this include the tailgate, tail cover, doors, especially side doors, engine hood, etc.

[0003] The prior art upon which this invention is based (DE 10 2020 113 958 A1) relates to a drive in the form of a spindle drive. The latter has a transmission system with multiple drive components through which torque can be transmitted. In the transmission system, torque is transmitted from the motor shaft of the drive motor to the feed gear component of the feed gear in such a way. In this case, the feed gear is designed as a spindle-spindle-nut gear having a spindle and a spindle nut meshing with it, wherein the input-side feed gear component of the feed gear is formed by the spindle. The spindle-spindle-nut gear converts rotational motion into linear drive motion between two drive couplings of the drive. Furthermore, a reduction gear designed as a planetary gear is connected between the drive motor and the feed gear. The drive motor has a bearing assembly for supporting the motor shaft, which has at least one motor shaft bearing.

[0004] In this configuration, the motor shaft is periodically supported with radial clearance (bearing clearance), allowing it to move radially relative to the drive motor, and particularly relative to the motor housing, even to a very small extent. One challenge is the tendency for the motor shaft to vibrate freely, accompanied by modulated interference noise.

[0005] This invention is based on the problem of designing and improving known drivers in such a way that optimization is achieved regarding the development of noise in the driver.

[0006] This objective is achieved by the features of the feature portion of claim 1.

[0007] The basic consideration is to radially press the motor shaft, which has a specific radial clearance, against its associated motor shaft bearing to prevent free vibration and suppress corresponding modulation interference noise. This is achieved by loading a specific side of the motor shaft, which clamps the motor shaft within the motor shaft bearing, or, in the case of multiple motor shaft bearings, one or two bearings. This results in the motor shaft occupying a predetermined position within the motor shaft bearing, which improves operational smoothness.

[0008] Specifically, it is recommended that the driver have a radial force introduction unit, which is designed to apply radial force to the rotating motor shaft in the assembled state, such that the motor shaft abuts against one side of the motor shaft bearing in a defined manner.

[0009] Claims 2 and 3 define a force application device that allows radial force to be applied purposefully and in a controlled manner to a motor shaft and ensures defined contact between the motor shaft and one side of the motor shaft bearing.

[0010] Claims 4 and 5 specify preferred locations for the radial force introduction unit and force application device within the drive. Therefore, the motor shaft is typically particularly prone to vibration, especially on the axial side of the drive motor facing the feed gear. However, in principle, other locations within the drive may also be advantageous, for example, for reasons of easier assembly and maintenance, such as on the side of the drive motor facing away from the feed gear. This arrangement can be made inside or outside the motor housing.

[0011] According to a particularly preferred design of claim 6, the force application device for radial application or deflection of the motor shaft is preferably an elastic stirrup, particularly made of metal and / or spring plate. This component can be radially mounted between existing transmission components and / or gear components in a particularly simple and space-saving manner, one of which is coupled to the drive portion of the motor shaft in a torque transmission manner, or formed by the motor shaft itself.

[0012] The stirrups, as claimed in claim 7, prevent rotation via one or more outwardly oriented end edges to ensure the motor shaft remains in a defined position within the motor shaft bearings. For torsional connections, the stirrups are anchored radially outward through their respective edges to one of the drivetrain components and / or gear components.

[0013] Claim 8 relates to a reduction gear connected downstream of a drive motor, which particularly preferably comprises a planetary gear according to claim 9. In this case, the stirrup is specifically installed between two gear components, one of which is coupled to the drive portion of the motor shaft in a torque transmission manner. The drive portion, which is radially applied or deflected by a force-applying device, is preferably the sun gear of the planetary gear. Claim 10 specifies a radial arrangement of the stirrup between the sun gear and the ring gear of the planetary gear.

[0014] According to a particularly preferred design of claim 11, the force-applying device for radial application or deflection of the motor shaft is preferably a rigid annular appendage, particularly made of metal and / or cast material, extending around the motor shaft. Examples here are polyetheretherketone, polypropylene, polyphthalamide, or polyketone.

[0015] Claims 12 to 15 relate to further particularly preferred variations of the force application device.

[0016] Claim 16 specifies a radial arrangement of the annular additional portion between the motor shaft and one of the motor shaft bearings that radially support the motor shaft.

[0017] A preferred variation of the path of the motor shaft axis is given in claim 17, under the condition that the radial force is introduced by the radial force unit or the force application device.

[0018] Claim 18 relates to a particularly preferred design in which the feed gear is designed as a spindle-spindle nut gear.

[0019] According to a particularly preferred design of claim 19, the actuator has a drive housing having an inner housing tube and an outer housing tube radially surrounding a radial force introduction unit or force application device to protect these components from the environment surrounding the actuator.

[0020] The invention will be explained in more detail below with reference to the accompanying drawings, which illustrate embodiments only. In the drawings:

[0021] Figure 1 A perspective view of the rear region of a motor vehicle having at least one proposed drive is shown, as well as a partial cross-sectional side view of the drive in a retracted state, and the motor shaft of the drive motor of the drive under various load conditions is shown very schematically.

[0022] Figure 2 A cross-sectional view of the axial portion of the proposed driver and an exploded view of the axial portion of the driver are shown in a first embodiment.

[0023] Figure 3 The diagram shows a) a cross-sectional view of the axial portion of the proposed second embodiment of the driver and b) an exploded view of the axial portion of the driver.

[0024] Figure 4 It shows the method for using according to Figure 3 Various variations of the annular additional portion of the second embodiment of the proposed driver.

[0025] The drive 1 shown in the figure, preferably a spindle drive in this case, is used for motor adjustment of the adjustment element 2 of the motor vehicle 3, which is configured, for example, according to... Figure 1 The tailgate. This is certainly advantageous, but not limiting. Instead, the proposed actuator 1 can be used for all possible adjusting elements 2 of the motor vehicle 3, such as the rear cover, doors, especially side doors, engine hood, etc. of the motor vehicle 3.

[0026] Figure 1 The drive 1 is shown to have a transmission system 4 with multiple transmission components. In this sense, the transmission components are the parts that can transmit the force and / or torque required for the adjustment of the adjustment element 2 in the drive 1.

[0027] The transmission system 4 has a drive motor 5 with a motor shaft 6 extending axially, and a feed gear 7 with an input-side feed gear assembly and an output-side feed gear assembly for generating drive motion, particularly linear drive motion, between two drive couplings 8 and 9. The "feed gear assembly" is the gear component required to generate the feed motion, such as a threaded rod ("spindle"), rack, etc. Figure 1 In the process, two drive connectors 8 and 9 are disposed on the end side of the driver 1 and are used to transmit drive motion to the motor vehicle 3, that is, the first drive connector 8 transmits to the adjustment element 2 and the second drive connector 9 transmits to the motor vehicle 3.

[0028] The motor shaft 6 is radially supported by at least one motor shaft bearing 11, which is preferably supported in the motor housing 10 of the drive motor 5, and is also axially supported. In this case, the support of the motor shaft 6 is typically achieved by a radial clearance (so-called bearing clearance) between the motor shaft bearing 11 and the motor shaft 6, such that the motor shaft 6 is radially movable relative to the drive motor 5, and in particular relative to the motor housing 10, even to a very small extent.

[0029] In this respect, the motor housing 10 of the drive motor 5 must be distinguished from the optional drive housing 12 of the proposed driver 1, which will be described in more detail below, and which, in addition to the drive motor 5, radially surrounds at least partially the reduction gear 13 and / or the feed gear 7. Instead, the motor housing 10 carries and protects the electrical and mechanical components of the drive motor 5 (e.g., stator, rotor, commutator, windings, etc.), but does not surround either the reduction gear 13 or the feed gear 7.

[0030] On one hand, the drive motor 5 and its motor shaft 6, and on the other hand, the feed gear component of the feed gear 7, respectively form the transmission components of the transmission system 4. Torque can be transmitted from the motor shaft 6 to the input-side feed gear component of the feed gear 7 via other transmission components of the transmission system 4.

[0031] The embodiment shown in the figure, and preferred in this respect, corresponds to a drive 1, particularly a spindle drive, for adjusting the adjusting element 2 of a motor vehicle 3, particularly a flap, wherein the drive 1 has a first drive connector 8 for coupling to the motor vehicle 3, in this case an adjusting element-side drive connector 8, and a second drive connector 9, in this case a body-side drive connector 9, wherein the drive 1 has a transmission system 4 having two drive portions that are linearly adjustable relative to each other, particularly, between a retracted position and an extended position along a geometric drive axis 14, and having a plurality of transmission components coupled to each other in a force or torque transmission manner to transmit the introduced... The force in the drive connectors 8 and 9, wherein each of the drive parts is associated with one of the drive connectors 8 and 9 respectively, wherein the drive 1 has a feed gear 7 for performing particularly linear drive motion along the geometric drive axis 14, wherein one of the two drive parts has a drive unit 15 with a drive motor 5 connected downstream thereto by the feed gear 7, wherein the drive motor 5 has a motor shaft 6 having a geometric motor shaft axis 16 and transmitting the torque generated by the drive motor 5, and a bearing assembly 17 for supporting the motor shaft 6 having at least one motor shaft bearing 11, particularly a sliding bearing, having a geometric bearing central axis 18 and being configured to radially support the motor shaft 6.

[0032] In this case, the bearing center axis 18 is defined as the axis that defines the radial center of the motor shaft bearing 11 under no-load conditions, and especially under load conditions. Here, and preferably, the bearing assembly 17 has a plurality of motor shaft bearings 11, particularly sliding bearings, which have a common geometric bearing center axis 18 and are configured to radially support the motor shaft 6.

[0033] Importantly, the drive 1 has a radial force introduction unit 19, which is designed to apply radial force to the rotating motor shaft 6 in the assembled state, such that the motor shaft 6 abuts against one side of the motor shaft bearing 11 in a defined manner.

[0034] In this context, radial application of motor shaft 6 means that a force having a force direction that is radially aligned with the geometric motor shaft axis 16 is introduced into motor shaft 6.

[0035] In this case, the side of the motor shaft bearing 11 against which the proposed motor shaft 6 abuts in a defined manner is defined by the position relative to the fixing element of the driver 1, that is, it always points to the same point in the driver 1.

[0036] The radial force introducing unit 19 applies a specific radial force to the rotating motor shaft 6. This force, within the bearing clearance (here, the bearing clearance is, for example, 0.01 mm to 0.1 mm, preferably 0.01 mm to 0.05 mm), forces the motor shaft 6 to move in a specific direction within the corresponding motor shaft bearing 11. As a result, the motor shaft 6 is positioned on the radial side of the motor shaft bearing 11 and abuts against it in a defined manner. Thus, the radial force introducing unit 19 forces the motor shaft 6 into a position offset from the geometric bearing central axis 18, i.e., the geometric motor shaft axis 16 and the geometric bearing central axis 18 extend coaxially with each other. Instead, the geometric motor shaft axis 16 extends in particular curved or obliquely relative to the geometric bearing central axis 18. In particular, the two geometric axes 16, 18 intersect at at least one intersection point 20.

[0037] By applying a targeted unilateral load, the motor shaft 6 is clamped in one or at least two of the plurality of motor shaft bearings 11, which results in the motor shaft 6 occupying a defined position in the respective motor shaft bearing 11. This, in turn, prevents free vibration of the rotating motor shaft 6 and prevents corresponding modulation interference noise.

[0038] In this context, the terms "axial" and "radial" always refer to the geometric drive axis 14. Accordingly, the axial direction is the direction in which the geometric drive axis 14 extends.

[0039] Furthermore, the radial force introduction unit 19 is preferably provided here with a force application device 21. The force application device 21 radially deflects the motor shaft 6 relative to the unloaded state and / or is coupled to the motor shaft 6 in a torque transmission manner, particularly torsion-resistant and preferably axially fixed coupling drive portion 22, thus pressing the motor shaft 6 and / or drive portion 22 in a specific radial direction.

[0040] To achieve the proposed function, namely, in the assembled state, the rotating motor shaft 6 is radially pressed into the motor shaft bearing 11 relative to one side and abuts against one side of the motor shaft bearing 11 in a defined manner, the force application device 21 applies force to the motor shaft 6 directly or through the drive portion 22 coupled to the motor shaft 6 in a torque transmission manner. As explained further below, the drive portion 22 is in particular a gear component.

[0041] In this case, the force application device 21 is preferably formed by a separate, i.e., independent component. However, according to another embodiment not shown here, it can also be imagined alternatively that the force application device 21 is formed by a component portion of a component that is torsionally and particularly axially fixed relative to the drive motor 5 or a component portion of a component that is rotatable and particularly axially fixed relative to the drive motor 5.

[0042] A “separate” or “independent” component refers to a component of the drive 1 that is provided for the proposed function of radially applying or deflecting the rotating motor shaft 6 to one side, and which itself does not particularly provide a torque transmission function for generating linear drive motion, and preferably does not provide any further function in the drive 1 at all, as will be explained in more detail below. In contrast, a “component part” refers to a part of a component that, in addition to the proposed function of radially applying or deflecting the rotating motor shaft 6 to one side, also provides at least one additional function in the drive 1, such as a housing function, thus a protective function, and / or a function as a gear component resisting torsion relative to the drive motor 5.

[0043] Here, and preferably, the radial force introduction unit 19 or the force application device 21 is radially applied to the motor shaft 6 outside the motor housing 10 of the drive motor 5.

[0044] A radial force introduction unit 19 or a force application device 21 can also be provided to radially apply force to the motor shaft 6 inside the motor housing 10 of the drive motor 5.

[0045] Furthermore, in this case, preferably, the radial force introduction unit 19 or the force application device 21 applies radially to the motor shaft 6 on the axial side of the drive motor 5 facing the feed gear 7.

[0046] The axial side of the drive motor 5 facing the feed gear 7 is where the torque generated by the drive motor 5 is transmitted from the drive motor 5 to the feed gear 7. On this side, the motor shaft 6 is particularly prone to vibration.

[0047] However, a radial force introduction unit 19 or a force application device 21 may also be provided to apply radial force to the motor shaft 6 on the side of the drive motor 5 opposite to the feed gear 7.

[0048] The side of the drive motor 5 facing away from the feed gear 7 is the axial side (rear side of the drive motor) facing the nearest drive connectors 8 and 9. On this axial side, the drive motor 5 or the motor housing 10 typically has an axial end cap 23 and / or a commutator (inside the motor housing 10) and / or a rotary encoder, such as a Hall sensor (outside the motor housing 10).

[0049] The following will explain a particularly preferred design of the force application device 21.

[0050] Therefore, according to Figure 2 The radial force introduction unit 19 has a preferred elastic stirrup 24 as a force application device 21, which is made of metal and / or spring plate 24.

[0051] In this context, "elasticity" refers to the elastic deformation of the stirrup 24 during assembly, and its ability to deform back to its original internal state before assembly after disassembly.

[0052] In the assembled state, the stirrups 24 extend around the motor shaft 6 and / or are coupled to the drive portion 22 of the motor shaft 6 in a torque transmission manner.

[0053] The stirrups 24, particularly the spring plate 24, have a thickness (radial dimension) of 0.1 mm to 1 mm, preferably 0.1 mm to 0.5 mm, and more preferably 0.1 mm to 0.2 mm, over their entire length extending around the central axis 18 of the geometric bearing.

[0054] Furthermore, the stirrup 24 has an inner profile 25 that extends around the drive portion 22 in the assembled state and is radially closer to the geometric bearing central axis 18 in the first profile portion 26 than in at least one second profile portion 27.

[0055] Therefore, the first contour portion 26 is radially more inward than at least one second contour portion 27 (in this case, two second contour portions 27) or the inner contour 25. Figure 2 As shown, one or more second profile portions 27 particularly form the majority of the inner profile 25, except for at least one end 28 of the stirrup 24, which has an edge oriented radially outward or inward, as will be further described below.

[0056] Due to the special profile of the inner contour 25 of the stirrup 24, the rotating motor shaft 6 is subjected to radial application of the stirrup 24 in the assembled state, preferably indirectly, such that the motor shaft 6 abuts against one side of the motor shaft bearing 11 in a defined manner, which will be described in more detail below.

[0057] The first profile portion 26 of the inner profile 25 here, and preferably in the assembled state, has a profile that is tangential to the geometric bearing central axis 18, i.e., a straight profile, but may also have a curved profile, particularly radially inward. Additionally or alternatively, at least one second profile portion 27 of the inner profile 25 in this case, and preferably in the assembled state, has a profile that is radially outward curved relative to the geometric bearing central axis 18, particularly an arc-shaped profile.

[0058] In this case, the first contour portion 26 is preferably defined by the curved edge 29 to the second contour portion 27 that is adjacent to it in each case.

[0059] Furthermore, and preferably provided herein, in the assembled state, particularly at one or both circumferential ends 28, the stirrup 24 has a radially outwardly oriented end edge 30 or a radially inwardly oriented end edge, through which the stirrup 24 is secured in the assembled state to prevent rotation. This will be explained in more detail below.

[0060] exist Figures 1 to 3 In the driver 1, the drive unit 15 has a reduction gear 13 connected downstream of the drive motor 5, and a feed gear 7 connected downstream of it. As defined above, the reduction gear 13 is arranged on the axial side of the drive motor 5 facing the feed gear 7.

[0061] Here, and preferably, the drive portion 22, which is coupled to the motor shaft 6 in a torque transmission manner and is radially applied or deflected by the force application device 21, is a gear component of the reduction gear 13.

[0062] Due to the specific contour of the stirrup 24 or its internal profile 25, the rotating motor shaft 6, in its assembled state, is radially applied via the drive portion 22, particularly the gear component, such that the motor shaft 6 abuts against one side of the motor shaft bearing 11 in a defined manner. Therefore, the stirrup 24 introduces radial force into the drive portion 22 or the gear component, which is firmly mounted on the motor shaft 6 relative to the radial direction, and thus the stirrup 24 or the radial force is applied or deflected radially together with the motor shaft 6.

[0063] Here, and preferably, the reduction gear 13 has a planetary gear 31 having a rotatable sun gear 32 and a rotatable planetary gear carrier 33 coaxial with it, as well as a fixed or fixable ring gear 34. The planetary gear carrier 33 carries at least one rotatable planetary gear 35, which meshes axially parallel to the corresponding sun gear 32 on one hand and axially parallel to the corresponding ring gear 34 on the other hand.

[0064] Here, "fixed" means that the gear ring 34 is anti-torsional relative to the drive motor 5 and / or drive housing 12.

[0065] like Figure 2 As shown, the drive portion 22, which is coupled to the motor shaft 6 in a torque transmission manner and is radially applied or deflected by the force application device 21, is preferably the sun gear 32 of the planetary gear 31.

[0066] Several can also be provided; here are two, gear stages 36 connected one after another, each formed by planetary gears 31. The sun gear 32 discussed is the sun gear 32 of the first gear stage 36.

[0067] Due to the specific contour of the stirrup 24 or its inner profile 25, the rotating motor shaft 6 is thus radially applied via the sun gear 32 in the assembled state, causing the motor shaft 6 to abut against one side of the motor shaft bearing 11 in a defined manner. The stirrup 24, particularly the first profile portion 26, accordingly introduces radial force into the sun gear 32, which is firmly mounted on the motor shaft 6 relative to the radial direction, and is therefore radially applied or deflected by the stirrup 24 or the radial force together with the motor shaft 6.

[0068] Furthermore, in this configuration, preferably, the stirrups 24 are arranged radially in the assembled state, particularly clamped between the sun gear 32 and the gear ring 34. Here, "clamped" means that the stirrups 24 are under permanent radial preload in the assembled state. The stirrups 24 are radially supported on the inside of the gear ring 34 and radially deflect the sun gear 32 due to the existing preload, resulting in the motor shaft 6 coupled to the sun gear 32 being subjected to the same degree of application or deflection.

[0069] In this configuration, the stirrup 24 is fixed to prevent rotation and is preferably relative to the gear ring 34. As the motor shaft 6 rotates, the sun gear 32 rotates accordingly relative to the stirrup 24. This prevention of rotation is achieved, in particular, by frictional engagement between the radially outward-oriented end edges of the stirrup 24 and the gear ring 34, or alternatively or additionally, by form-locking. In this configuration, the sun gear 32 preferably contacts only the first profile portion 26, particularly its center, and thus only a single contact area 37 with the stirrup 24 if the stirrup 24 is fixed to prevent rotation relative to the gear ring 34, as in this case, where, particularly, this is substantially linear. The sun gear 32 then slides along the stirrup 24 on the latter. Alternatively, according to another embodiment not shown here, it can also be imagined that the stirrup 24 is fixed relative to the sun gear 32 to prevent rotation, and that the stirrup 24 rotates relative to the gear ring 34 when the motor shaft 6 rotates together with the sun gear 32. Then, in particular, an anti-rotation device is formed by frictional locking, or alternatively or additionally, shape locking, between the radially inwardly oriented end edge of the stirrup 24 and the sun gear 32.

[0070] Figure 3 Another variation of the force application device 21 is also shown.

[0071] Here, the radial force introduction unit 19 preferably has a rigid annular additional portion 38 as a force application device 21, particularly made of metal and / or cast material.

[0072] In this context, "rigidity" means that the annular attachment 38 will not elastically deform during assembly, or at least will not deform significantly.

[0073] Here, “ring” means that the additional part 38 is mostly or completely closed on the circumference and has, in particular, an inner contour 25 that is mainly arc-shaped, and preferably also has an outer contour 39 that is at least mainly arc-shaped.

[0074] In the assembled state, the annular additional portion 38 extends around the motor shaft 6.

[0075] Here, preferably, the annular additional portion 38 has an inner contour 25 that extends around the motor shaft 6 in the assembled state, and is radially closer to the geometric bearing central axis 18 in at least one first contour portion 26 than in at least one second contour portion 27. Therefore, at least one first contour portion 26, in this case the only first contour portion 26, is also radially more inward than at least one second contour portion 27, in this case the only second contour portion 27, or the inner contour 25. Figure 3 As shown, the second contour portion 27 specifically forms most of the inner contour 25.

[0076] Due to the special profile of the inner contour 25 of the annular attachment 38, the rotating motor shaft 6 is radially applied by the annular attachment 38 in the assembled state, which is applied directly here, such that the motor shaft 6 abuts against one side of the motor shaft bearing 11 in a defined manner, which will be described in more detail below.

[0077] The first profile portion 26 of the inner profile 25 here, and preferably in the assembled state, has a profile that is tangential to the geometric bearing central axis 18, i.e., a straight profile, but may also have a curved profile, particularly radially inward. Additionally or alternatively, in this case, at least one second profile portion 27 of the inner profile 25 has a profile that is radially outward curved relative to the geometric bearing central axis 18, particularly an arc-shaped profile.

[0078] according to Figure 3 In this case, the first contour portion 26 is preferably formed by an internal flattening, while the second contour portion 27 has an arcuate shape. In this configuration, the motor shaft 6 preferably contacts only the first contour portion 26, particularly at its center, and the opposite portion of the second contour portion 27; thus, the annular additional portion 38 contacts only the two opposing contact areas 37, which are substantially linear. The motor shaft 6 slides within the annular additional portion 38. However, it is also conceivable in principle that... Figure 4 As shown in a), the motor shaft 6 contacts only the first contour portion 26, particularly at its center, i.e., the annular additional portion 38 contacts only the contact area 37, which is particularly essentially linear.

[0079] Figure 4 a) again shows the example previously described. Figure 3 The force application device 21 is assembled together with the motor shaft 6. Other variations of the force application device 21 are... Figure 4 As shown in b) to e), and will be described below.

[0080] Figure 4The variations in a) to d) show that the internal contour 25 can essentially have not only a single first contour portion 26 ( Figure 4 a) and b)), and can also have at least or exactly two first contour portions 26 ( Figure 4 c) and d).

[0081] In the latter case, the first profile portion 26 is not arranged radially opposite to the center of the force application device 21, so as to be radially applied to the rotating motor shaft 6 in one direction in the assembled state as described above.

[0082] Furthermore, here and preferably according to Figure 4 In the embodiments of b) to d), the annular additional portion 38 has an outer contour 39 extending around the motor shaft 6 in the assembled state, and at least one cavity 40, particularly a hole, is radially provided between the outer contour 39 and at least one first contour portion 26 of the inner contour 25. The hole is preferably a circular hole. Figure 4 d) or elongated hole ( Figure 4 b) and c)). However, basically, according to Figure 3 and 4 a) The radial region between at least one first contour portion 26 of the outer contour 39 and the inner contour 25 may also be without cavity 40.

[0083] In the case of cavity 40, preferably, web 41 is radially formed between at least one first profile portion 26 of inner profile 25 and cavity 40, the motor shaft 6 abuts against web 41 in the assembled state, and as part of radial force introduction unit 19, web 41 radially applies force to the rotating motor shaft 6 in the assembled state, such that the motor shaft 6 abuts against one side of motor shaft bearing 11 in a defined manner. Web 41 is preferably more elastic than the material of motor shaft 6 and / or dampens vibrations of motor shaft 6 during operation. In this respect, web 41 forms a damping element. By means of a technical embodiment having one, two or more such damping elements, the force acting from motor shaft 6 on motor shaft bearing 11 can be precisely adjusted. This radial force is adjusted in such a way that contact of motor shaft 6 is ensured, thereby ensuring the formation of a lubricating film. On the other hand, the selected radial force is designed to be so low that additional drag torque and bearing wear are kept at the lowest possible level. Alternatively, a predetermined increase in drag torque can be intentionally introduced to provide advantages in system applications.

[0084] Furthermore, it is preferably provided here, such as Figure 4As shown in the example in d), the annular additional portion 38 has at least one circumferential portion 42 with a reduced axial thickness. In this case, preferably, the cavity 40 and / or the web 41 are arranged in the respective circumferential portion 42. By reducing the thickness in the respective cavity 40 and / or web 41 regions, improved elasticity can be achieved, thereby realizing a damping effect.

[0085] Figure 4 e) Another variation is shown. In this variation, contrary to the other embodiments, the support for the shaft defined by the inner contour 25 is preferably circular and, in particular, substantially corresponds to the cross-section of the motor shaft 6, such that the motor shaft 6 is supported in the support with a clearance. Therefore, it is preferred here that the inner contour 25 of the annular additional portion 38 does not have the aforementioned first contour portion 26, wherein the inner contour 25 is arranged radially closer to the geometric bearing central axis 18 than in at least one second contour portion 27. Instead, only the second contour portion 27 forming the entire inner contour 25 is provided here. However, alternatively, it is also conceivable that the inner contour 25 may be formed with the first contour portion 26 as described above.

[0086] According to Figure 4 In a variation of e), it is now preferred that the annular additional portion 38 has one or more, particularly two, spring tongues 43 extending over a portion of the circumference of the additional portion 38. In the assembled state, the spring tongues 43 are radially supported on a component fixed to the housing relative to the drive motor 5, particularly on one side of the motor shaft bearing 11 or the motor housing 10.

[0087] In this case, and preferably, the corresponding spring tongue 43, as part of the radial force introduction unit 19, influences the radial offset of the remainder of the annular additional portion 38 by providing radial support on one side, thereby applying radial force to the rotating motor shaft 6 in the assembled state, such that the motor shaft 6 abuts against one side of the motor shaft bearing 11 in a defined manner as described above. Here, and preferably, the corresponding spring tongue 43 is more elastic than the material of the component fixed to the housing and / or dampens vibrations of the motor shaft 6 during operation.

[0088] like Figure 3 As shown, the annular additional portion 38 is arranged radially here, and preferably in the assembled state, between the motor shaft 6 and the motor shaft bearing 11 that radially supports the motor shaft 6, or one of them. Therefore, the motor shaft bearing 11 forms a reverse bearing for the annular additional portion 38, i.e., the annular additional portion 38 is radially supported on the inner side of the motor shaft bearing 11. In principle, another component fixed to the housing relative to the drive motor 5, such as the motor housing 10, can also be used as a reverse bearing, in which case the annular additional portion 38 is radially supported on the reverse bearing in the assembled state.

[0089] Due to the special profile of the annular appendage 38 or its inner contour 25, the rotating motor shaft 6 is directly radially applied in the assembled state, causing the motor shaft 6 to abut against one side of the motor shaft bearing 11 in a defined manner. Therefore, the annular appendage 38, particularly the first contour portion 26, introduces radial force into the motor shaft 6 and radially deflects it, or applies it to the motor shaft 6 in the radial direction.

[0090] In this case, and preferably, the annular additional portion 38 is fixed in the motor shaft bearing 11 to prevent rotation, particularly by locking of shape, force or material, in this case by press fit.

[0091] In the embodiment shown here, and which is preferred in this respect, the geometric motor shaft axis 16 is typically tilted or bent relative to the geometric bearing center axis 18 when the motor shaft 6 is radially applied by the radial force introduction unit 19 or the force application device 21. These two alternatives are... Figure 1 c) is shown schematically with a dashed line.

[0092] As mentioned earlier, in Figures 1 to 3 The proposed drive 1 shown as an example is a spindle drive. Therefore, it is provided here, and preferably, that the feed gear 7 is a spindle-spindle nut gear 44 having a spindle 45 and a spindle nut 46 meshing therewith, and that one of the two drive sections has a spindle 45, and the other of the two drive sections has a spindle nut 46. Here, the spindle 45 is axially fixed to a first drive connector 8, in this case to an adjusting element-side drive connector 8, and the spindle nut 46 is axially fixed to a second drive connector 9, in this case to a vehicle body-side drive connector 9, via a spindle guide 47.

[0093] Furthermore, the drive unit 1 is preferably provided here with a drive housing 12 having an inner housing tube 48 and an outer housing tube 49. In this case, the inner housing tube 48 extends and retracts within the outer housing tube 49. The inner housing tube 48 is axially fixedly connected to one of the two drive parts, and the outer housing tube 49 is axially fixedly connected to the other of the two drive parts. Preferably, the radial force introduction unit 19 and / or force application device 21 are radially surrounded by the drive housing 12, particularly the outer housing tube 49. Additionally or alternatively, the radial force introduction unit 19 and / or force application device 21 are axially arranged outside the motor housing 10 of the drive motor 5, as shown here.

[0094] Furthermore, preferably, the drive spring assembly 50, having at least one helical spring 51, is arranged coaxially with the geometric drive axis 14. In this case, the drive spring assembly 50 is arranged together with at least one helical spring 51 within the drive housing 12, particularly within the inner housing tube 48 and / or the outer housing tube 49. In this case, the drive spring assembly 50 preloads the two drive portions relative to each other, particularly into the extended position. Additionally, to guide at least one helical spring 51, a spring conduit 52 extends inside or outside the at least one helical spring 51, wherein the spring conduit 52 is preferably axially fixed at one end to one of the two drive portions, particularly to the drive portion having the drive unit 15.

Claims

1. A drive, particularly a spindle drive, for adjusting an adjusting element (2), particularly a flap, of a motor vehicle (3), in, The driver (1) has a first drive connector (8) and a second drive connector (9) for coupling to the motor vehicle (3). The driver (1) has a transmission system (4) having two drive sections that are linearly adjustable relative to each other between a retracted position and an extended position along a geometric drive axis (14), and has multiple transmission components coupled to each other in a force or torque transmission manner to transmit forces introduced into the drive connectors (8, 9), wherein each of the drive sections is associated with one of the drive connectors (8, 9). The driver (1) has a feed gear (7) for performing particularly linear drive motion along the geometric drive axis (14). One of the two drive sections has a drive unit (15) with a drive motor (5) connected downstream of the feed gear (7). The drive motor (5) has a motor shaft (6) having a geometric motor shaft axis (16) and transmitting torque generated by the drive motor (5), and a bearing assembly (17) having at least one motor shaft bearing (11) having a geometric bearing central axis (18) and being configured to radially support the motor shaft (6). Its features are, The driver (1) has a radial force introduction unit (19) which is designed to apply radial force to the rotating motor shaft (6) in the assembled state, such that the motor shaft (6) abuts against one side of the motor shaft bearing (11) in a defined manner.

2. The driver according to claim 1, characterized in that, The radial force introduction unit (19) has a force application device (21), and the force application device (21) radially deflects the motor shaft (6) or is coupled to the drive portion (22) of the motor shaft (6) in a torque transmission manner, particularly in a torsional and preferably axially fixed coupling.

3. The driver according to claim 2, characterized in that, The force application device (21) is formed by a single component, or the force application device (21) is formed by a component portion of a component that is torsionally and particularly axially fixed relative to the drive motor (5) or a component portion of a component that is rotatable and particularly axially fixed relative to the drive motor (5).

4. The driver according to any one of the preceding claims, characterized in that, The radial force introduction unit (19) or the force application device (21) applies radially to the motor shaft (6) outside or inside the motor housing (10) of the drive motor (5).

5. The driver according to claim 4, characterized in that, The radial force introducing unit (19) or the force applying device (21) applies radially to the motor shaft (6) on the axial side of the drive motor (5) facing the feed gear (7), or the radial force introducing unit (19) or the force applying device (21) applies radially to the motor shaft (6) on the side of the drive motor (5) away from the feed gear (7).

6. The driver according to any one of the preceding claims, characterized in that, The radial force introduction unit (19) serves as a force application device (21) and has preferably elastic stirrups (24), particularly made of metal and / or spring plates (24). The stirrup (24) extends around the motor shaft (6) and / or coupled to the drive portion (22) of the motor shaft (6) in a torque transmission manner in the assembled state, and the stirrup (24) has an inner profile (25) extending around the drive portion (22) in the assembled state, which is radially closer to the geometric bearing central axis (18) in a first profile portion (26) than in at least one second profile portion (27). Preferably, the first contour portion (26) of the inner contour (25) has a contour that is tangential to the geometric bearing central axis (18) or particularly radially inwardly curved in the assembled state, and / or, the at least one second contour portion (27) of the inner contour (25) has a contour that is radially outwardly curved relative to the geometric bearing central axis (18) in the assembled state, particularly an arc-shaped contour.

7. The driver according to claim 6, characterized in that, In the assembled state, particularly at one or both circumferential ends (28), the stirrup (24) has a radially outward oriented end edge (30) or a radially inward oriented end edge, through which the stirrup (24) is fixed in the assembled state to prevent rotation.

8. The driver according to any one of the preceding claims, characterized in that, The drive unit (15) has a reduction gear (13) connected downstream of the drive motor (5), and the feed gear (7) is connected downstream of it. Preferably, the drive portion (22), which is coupled to the motor shaft (6) in a torque transmission manner and is radially deflected by the force application device (21), is a gear component of the reduction gear (13).

9. The driver according to claim 8, characterized in that, The reduction gear (13) includes a planetary gear (31), which comprises a rotatable sun gear (32) and a rotatable planetary gear carrier (33) coaxial with it, and a fixed or fixable gear ring (34). The planetary gear carrier (33) carries at least one rotatable planetary gear (35), which engages axially parallel to the corresponding sun gear (32) on one side and axially parallel to the corresponding gear ring (34) on the other side. Preferably, the drive portion (22) that is coupled to the motor shaft (6) in a torque transmission manner and is radially deflected by the force application device (21) is the sun gear (32) of the planetary gear (31).

10. The driver according to claim 9, characterized in that, In the assembled state, the stirrup (24) is arranged radially between the sun gear (32) and the gear ring (34), and is clamped in particular. Preferably, the stirrup (24) is fixed to prevent rotation relative to the gear ring (34), particularly by means of radially outwardly oriented end edges, or the stirrup (24) is fixed to prevent rotation relative to the sun gear (32), particularly by means of radially inwardly oriented end edges.

11. The driver according to any one of the preceding claims, characterized in that, The radial force introduction unit (19), as a force application device (21), has a preferably rigid annular appendage (38), particularly made of metal and / or cast material, and the annular appendage (38) extends around the motor shaft (6) in the assembled state. Preferably, the annular additional portion (38) has an inner profile (25) extending around the motor shaft (6) in the assembled state, which is radially closer to the central axis (18) of the geometric bearing in at least one first profile portion (26) than in at least one second profile portion (27). Preferably, in the assembled state, at least one first contour portion (26) of the inner contour (25) has a contour that is tangential to the central axis (18) of the geometric bearing or, in particular, a contour that is radially inwardly curved, and / or, in the assembled state, at least one second contour portion (27) of the inner contour (25) has a contour that is radially outwardly curved to the central axis (18) of the geometric bearing, in particular, an arc-shaped contour.

12. The driver according to claim 11, characterized in that, The inner contour (25) has at least or exactly two first contour portions (26), and the first contour portions (26) are not arranged radially opposite each other.

13. The driver according to claim 11 or 12, characterized in that, The annular additional portion (38) has an outer contour (39) extending around the motor shaft (6) in the assembled state, and at least one or exactly one cavity (40), particularly a hole, preferably a round hole or an elongated hole, is radially provided between the outer contour (39) and at least one first contour portion (26) of the inner contour (25). Preferably, a web (41) is radially formed between the at least one first contour portion (26) of the inner contour (25) and the cavity (40), against which the motor shaft (6) abuts in the assembled state, and is radially applied to the rotating motor shaft (6) in the assembled state as part of the radial force introducing unit (19), such that the motor shaft (6) abuts against one side of the motor shaft bearing (11) in a defined manner. Preferably, the web (41) is more elastic than the material of the motor shaft (6) and / or dampens the vibration of the motor shaft (6) in operation.

14. The driver according to any one of claims 11 to 13, characterized in that, The annular additional portion (38) has at least one circumferential portion (42) with reduced axial thickness, preferably the cavity (40) and / or the web (41) are arranged in the corresponding circumferential portion (42).

15. The driver according to any one of claims 11 to 14, characterized in that, The annular appendage (38) has one or more, particularly two, spring tongues (43) extending over a portion of the circumference of the appendage (38), which, in the assembled state, are radially supported on one side of the component fixed to the housing relative to the drive motor (5), particularly the motor shaft bearing (11) or the motor housing (10). Preferably, the respective spring tongue (43), as part of the radial force introduction unit (19), affects the radial offset of the remainder of the annular appendage (38) by its radial support on one side, thereby applying radial force to the rotating motor shaft (6) in the assembled state, such that the motor shaft (6) abuts against one side of the motor shaft bearing (11) in a defined manner. Preferably, the respective spring tongue (43) is more elastic than the material of the component fixed to the housing and / or dampens the vibration of the motor shaft (6) in operation.

16. The driver according to any one of claims 11 to 15, characterized in that, In the assembled state, the annular additional portion (38) is arranged radially between the motor shaft (6) and the motor shaft bearing (11) that radially supports the motor shaft (6), or one of them. Preferably, the annular additional portion (38) is fixed to prevent rotation in the motor shaft bearing (11), particularly by form locking, force locking or material locking.

17. The driver according to any one of the preceding claims, characterized in that, When the motor shaft (6) is radially applied by the radial force introduction unit (19) or the force application device (21), the axis of the geometric motor shaft (16) is tilted or bent relative to the central axis of the geometric bearing (18).

18. The driver according to any one of the preceding claims, characterized in that, The feed gear (7) is a spindle-spindle nut gear (44) having a spindle (45) and a spindle nut (46) meshing therewith, and one of the two drive parts includes the spindle (45) and the other of the two drive parts includes the spindle nut (46).

19. The driver according to any one of the preceding claims, characterized in that, The driver (1) has a drive housing (12) having an inner housing tube (48) and an outer housing tube (49), the inner housing tube (48) extending and retracting within the outer housing tube (49), and the inner housing tube (48) being axially fixedly connected to one of the two drive parts, and the outer housing tube (49) being axially fixedly connected to the other of the two drive parts. Preferably, the radial force introduction unit (19) and / or the force application device (21) are radially surrounded and / or axially arranged outside the motor housing (10) of the drive motor (5) by the drive housing (12), particularly the outer housing tube (49).

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