Actuators for Automotive Applications

Abstract

The present invention relates to an actuator for motor vehicle applications, in particular for motor vehicle locks, preferably an actuator integrated in a motor vehicle door lock. In its basic configuration, the actuator comprises an electric motor (4) and an actuating element (10) which is acted on directly or indirectly by the electric motor (4) via a drive train (5-9). The drive train (5-9) is equipped with at least one first evoloid toothing (5,6) and at least one second evoloid toothing (7,8) adjacent to each other. Each evoloid toothing (5,6;7,8) comprises an evoloid pinion (5,7) rotatable about an evoloid axis (5a,7a) and an evoloid output wheel (6,8) meshed with the evoloid pinion and rotatable about a wheel axis (6a,8a), respectively. According to the invention, the two evoloid toothings (5, 6; 7, 8) are positioned perpendicular to each other such that the majority of the two evoloid axes (5a, 7a) are perpendicular to each other.

Description

[Technical field]

[0001]

[0001] The present invention relates to an actuator for automotive applications, in particular a drive for a lock for a motor vehicle, preferably a drive integrated in a lock for a motor vehicle door, comprising an electric motor and an actuating element which is acted on directly or indirectly by the electric motor via a drive train, the drive train being equipped with at least one first and one second evoloid toothing adjacent to each other, each evoloid toothing having an evoloid pinion which can rotate about an evoloid axis and an evoloid output wheel which meshes with the evoloid pinion and can in each case rotate about a wheel axis.

[0002]

[0002] Actuators for automotive applications are used in various ways on and in motor vehicles. For example, such actuators are used to adjust the outside mirrors, to adjust the seats, to adjust the headlights, to operate the window lifters of a window lift drive, or to switch the windshield wipers on or off. In addition, in principle, hinge elements such as rear doors, trunk lids, car doors, engine hoods, etc. can also be actuated with the help of such actuators.

[0003]

[0003] In addition to these general automotive applications for actuators, these actuators are particularly preferably and actually used in connection with automotive locking devices, such as automotive locks, typically automotive locks, in particular automotive door locks.

[0004]

[0004] In this context, the actuator or drive acts as an opening drive, for example to ensure that the locking mechanism of a motor vehicle locking device is opened. To do this, the drive operates, for example, on a pawl, lifting it out of locking engagement with the rotary latch. Furthermore, such drives are often also used as closing drives, ensuring that the associated locking mechanism is closed. This is usually done from a pre-established pre-latch position to a main latch position or an overstroke position.

[0005]

[0005] The closing drive is often designed separately from the vehicle locking device or vehicle lock and is designed for this purpose as a spindle / spindle nut gear, as described in the prior art according to DE 20 2008 007 719 U1. However, the design effort in this connection is large, since, for example, both the actuator and the associated vehicle lock must have their own housing. Furthermore, couplings and flexible connection elements, for example in the form of Bowden cables, are required. Finally, there is often not enough space on the side door of a vehicle for the actuator on the one hand and the vehicle lock on the other hand.

[0006]

[0006] For this reason, in practice, compact actuator designs are preferred due to the often cramped installation conditions, which not only apply when the associated actuator is located on the inside of the vehicle door in connection with vehicle locks, but also in seat adjustment, outside mirror and even headlight adjustment applications, and in connection with window lifters.

[0007]

[0007] As the above mentioned applications sometimes require strong forces or high torques, multi-stage gears actuated by high-speed electric motors are often implemented, so that slow regulating movements with high torque can be realized at the output side of the gears. This is possible even if the electric motor is operated with low DC voltages and moderate currents, and therefore with relatively low power, as is usual in automotive applications.

[0008]

[0008] For this purpose, the general prior art according to DE 10 2017 125 819 A1 proposes an actuator equipped with an evoloid pinion on the output shaft of an electric motor, which also meshes with an evoloid output wheel which directly realizes a first evoloid toothing at the input of the drive train, which in turn has a second evoloid toothing.

[0009]

[0009] Such evoloid toothings are typically characterized by a high transmission or reduction ratio, so that a high torque can be made available at the output side by using a small number of gear stages. This means that, assuming that the electric motor is at the input side and moves at high speed, and taking into account that the actuating element provided at the output side of the drive train, in contrast, requires only a small adjustment movement but a high torque, it is usually possible at this point to achieve a high-speed reduction ratio, for example, of 5:1 or more, or even 10:1 or more.

[0010]

[0010] The two evoroid toothings in the general prior art according to DE 10 2017 125 819 A1 already ensure that a particularly compact design is achieved and at the same time high transmission or reduction ratios are available by using one or at most two gear stages. The comprehensive prior art according to DE 10 2008 054 398 A1 also shows comparable advantages.

[0011] In contrast to the first mentioned publication DE 10 2017 125 819 A1, which represents the closest prior art, the second mentioned drive (DE 10 2008 054 398 A1) is used primarily in connection with the actuation of brakes in motor vehicles, so that in this context it is particularly important that the thermal effects of the brakes can be controlled if suitable materials are used. For this reason, the individual gears are produced, if at all, from special plastics, for example polyphthalamide (PPA) or aromatic polyamide materials (PA). However, such plastics are not used for actuators used in or in connection with motor vehicle locking devices, since they are particularly costly and they are produced in extremely large quantities.

[0012]

[0012] Although the prior art is generally proven, there is still room for further improvement. This is because both of the closest teachings according to DE 10 2017 125 819 A1 and DE 10 2008 054 398 A1 are generally implemented in such a way that two evoloid toothings are adjacent to each other such that the evoloid axis and the associated wheel axis are parallel to each other in each case, so that a somewhat nested arrangement is observed overall, but the positioning of the individual output wheels one behind the other would result in a relatively large structure. The present invention generally seeks to improve on this. Summary of the Invention

[0013]

[0013] The present invention is based on the technical problem of further developing such an actuator for automotive applications in such a way that, compared to the prior art, improved space utilization is observed, resulting in improved compactness.

[0014]

[0014] In order to solve this technical problem, a typical actuator for automotive applications is characterized within the scope of the present invention in that the two evoloid teeth are arranged perpendicular to each other and the two evoloid axes are for the most part perpendicular to each other.

[0015]

[0015] This means that within the scope of the present invention, the two evoloid toothings continue to be directly adjacent to each other. However, the overall procedure is such that, in contrast to the prior art, the two evoloid toothings do not correspond to engagement surfaces aligned parallel to each other, but rather, according to the present invention, the respective engagement surfaces of the two evoloid toothings are positioned perpendicular to each other, in this way the installation space can be further more or less significantly reduced compared to the previous embodiments.

[0016]

[0016] Advantageously within the scope of the present invention, the two evoloid toothings or their engagement surfaces are positioned primarily perpendicular to each other, such that the evoloid axis and the wheel axis of one of the two evoloid toothings are positioned perpendicular to each other. This means that at least one of the two evoloid toothings is designed such that the evoloid axis of the evoloid pinion on the one hand and the wheel axis of the evoloid output wheel meshing with the evoloid pinion on the other hand enclose a primarily perpendicular angle between them and are therefore positioned perpendicular to each other. As a result, the evoloid output wheel can be placed "on" the evoloid pinion. This means that the evoloid output wheel extends from the evoloid axis of the evoloid pinion substantially perpendicularly above or below the evoloid axis and adjoins the evoloid pinion, so that the evoloid pinion and the evoloid output wheel can still contact each other unchanged. To this end, as will be explained in more detail within the scope of the embodiments, each evoloid output wheel is typically equipped with evoloid toothing, while the associated evoloid pinion is also equipped with evoloid toothing.

[0017]

[0017] The procedure is usually such that the evoloid axis of the first evoloid toothing and the wheel axis are mostly positioned perpendicular to each other. In contrast, the evoloid axis of the second evoloid toothing and the wheel axis are mostly positioned parallel to each other. The relativization of the positions in the sense of "largely" or "predominantly" takes into account the fact that the gears involved are most often designed and assembled as plastic gears with limited manufacturing accuracy.

[0018]

[0018] Since the two evoloid toothings are (directly) adjacent to each other, the design is also such that the wheel axis of the first evoloid toothing coincides with the evoloid axis of the second evoloid toothing. This is achieved and guaranteed within the scope of the present invention by the evoloid output wheel of the first evoloid toothing also being equipped with an evoloid pinion or by it being adjacent to the evoloid output wheel in such a way that the wheel axis and the evoloid axis coincide. As a result, the evoloid axis of the second evoloid toothing and the wheel axis can be positioned approximately parallel to each other.

[0019]

[0019] Furthermore, it is achieved that the evoloid axis of the first evoloid toothing and the drive axis of the output shaft of the electric motor coincide, so that the output shaft of the electric motor receives the evoloid pinion of the first evoloid toothing. Furthermore, according to an advantageous embodiment, the evoloid axis of the first evoloid toothing and the wheel axis are positioned perpendicular to each other, so that the overall operation is such that the evoloid output wheel of the first evoloid toothing adjoins a vertical extension above or below the output shaft of the electric motor as the evoloid axis of the first evoloid toothing in which the evoloid pinion is positioned.

[0020]

[0020] The evoloid output wheel of the second evoloid toothing is advantageously further equipped with an output pinion for driving the drive pawl as an actuating element. In this way, the two evoloid toothings associated with the output pinion define as a whole a drive train, which in a preferred variant acts directly on the actuating element or on the drive pawl as an actuating element. This direct action is due to the fact that the output pinion of the drive train usually meshes with the drive pawl via a toothed segment. This means that the drive pawl advantageously engages with the associated toothed segment in the output pinion. In addition, the drive pawl usually has a drive arm which acts on a locking mechanism, which essentially consists of a rotary latch and a pawl.

[0021]

[0021] In addition to the above-mentioned direct action of the actuating element or the drive pawl by the drive train, it is of course also possible in principle and within the scope of the invention for the actuating element to be acted on indirectly. In this case, an output pinion at the end of the drive train can act, for example, on another pinion, which in turn acts on the drive pawl. Of course, between the output pinion and the drive pawl or generally the drive element, other coupling means (other than the above-mentioned gears) can also be interposed, so that the drive element can be acted on indirectly with the help of the drive train.

[0022]

[0022] In order to achieve a cost-effective and durable design, the output pinions and the drive pawls in each case are usually made of metal, e.g. steel. As a result, repeated adjustment processes over long time scales can also be realized. In contrast, evoloid pinions and evoloid output wheels are usually designed as at least partially plastic gears. In most cases, evoloid pinions and evoloid output wheels are all-plastic gears. These can be manufactured particularly cost-effectively, for example, from thermoplastic resins, possibly embedded with glass or plastic fibers. Furthermore, such plastic gears are lightweight.

[0023]

[0023] The invention also relates to a motor vehicle lock, in particular a motor vehicle door lock, equipped with a locking mechanism consisting essentially of a rotary latch and a pawl. Furthermore, the motor vehicle lock, in particular said motor vehicle door lock, also has an actuator for the locking mechanism. The actuator can act as an opening drive for the pawl by lifting the pawl from locking engagement with the rotary latch. The rotary latch can then be opened by a spring support. However, it is also possible for the actuator to act as a closing drive for the rotary latch. In this case, the closing drive ensures that the rotary latch, which has been moved manually, for example, to a pre-latch position, is closed to the main latch position or to an overstroke position with the aid of an actuating element or a drive pawl in the example case. In principle, however, the actuator can act both as an opening drive for the pawl and as a closing drive for the rotary latch.

[0024]

[0024] In all these cases, the actuator according to the invention as described above is integrated into the associated motor vehicle lock, in particular a motor vehicle door lock. This further means that the actuator is accommodated together with the locking mechanism and, if applicable, with other lock components in a common lock housing, in particular a door lock housing or generally a common housing. The housing is also usually made of plastic for weight and cost reasons and is usually sealed against moisture and dust.

[0025]

[0025] Thus, an actuator for automotive applications is described which is particularly suitable for use with a motor vehicle lock in general, in particular with a motor vehicle lock, preferably with a motor vehicle door lock. In this connection, the actuator can advantageously perform the functions of an opening drive and / or a closing drive. For this purpose, the actuator is typically integrated into the housing of a general motor vehicle lock or a motor vehicle lock, preferably with a motor vehicle door lock.

[0026]

[0026] All of this is possible and implementable, since on the one hand a drive train with only two or three gear stages from two evoloid toothings and an output pinion on the output side are used, which engage the drive pawl as the actuating element. Nevertheless, this and other aspects make it possible to achieve transmission or reduction ratios comparable to those in the general prior art according to DE 10 2017 125 819 A1, i.e., for example, transmission or reduction ratios that can take values ​​of more than 50:1 and even more than 80:1 for the entire gear. As a result, high torques or forces are available at the actuating element.

[0027] At the same time, the actuator according to the invention is characterized by a particularly compact design, which is essentially due to the fact that, as described above, the two evoloid toothings are positioned perpendicular to one another, i.e. their respective engagement surfaces are positioned perpendicular to one another, so that, in particular, the evoloid output wheel of the first evoloid toothing can be positioned in a quasi-vertical projection above the associated evoloid pinion, which is located on the output shaft of the electric motor.

[0028]

[0028] In this way, no additional lateral installation space is required for the associated evoloid output wheel, and the evoloid output wheel of the second evoloid tooth can be placed directly adjacent to the electric motor, as will be explained in more detail in the following embodiments. In any case, these considerations make it clear that the invention results in an even smaller installation volume compared to the prior art, which offers special advantages in relation to a high transmission or reduction ratio, low weight and at the same time low costs. [Brief description of the drawings]

[0029]

[0029] The invention will now be explained in more detail with reference to the drawings which show only one embodiment. [Figure 1] FIG. 1 shows a perspective view of an actuator for automotive applications according to the present invention.

[0030] Detailed Description of the Invention

[0031]

[0030] Figure 1 shows an actuator for automotive applications. The actuator is generally used as a drive in connection with a vehicle lock, preferably a lock for a vehicle door. For this purpose, the actuator is integrated into a housing 1 for the associated vehicle lock, which is only shown in Figure 1. The housing 1 is made of plastic. It can be seen that the housing 1 not only houses the actuator, which will be described in more detail below, but also the locking mechanism 2, 3, consisting of a rotary latch 2 and a pawl 3, which have the conventional function. In this way, the actuator can act as a closing drive on the rotary latch 2, which is not shown in detail but which functions in a manner comparable to the prior art according to DE 20 2008 007 719 U1. In contrast, a variant is shown in which the actuator acts as an opening drive and for this purpose lifts the pawl 3 out of locking engagement with the rotary latch 2, as indicated by the corresponding arrow in Figure 1.

[0032]

[0031] The actuator is accommodated in a housing 1 together with the locking mechanism 2, 3 and is equipped as its basic configuration with an electric motor 4 and a drive train 5, 6, 7, 8. According to the present embodiment, the drive train 5-9 operates directly on an actuating element 10, which according to the present embodiment is designed as a drive pawl 10. With the help of the drive pawl 10, when the actuator is designed as an opening drive for the illustrated motor vehicle lock, the pawl 3 can be pivoted about its axis in the clockwise direction shown in FIG. 1, so that the pawl 3 releases the previously captured rotary latch 2 (which is in the illustrated closed position), which is then pivoted open with the help of a spring and releases the lock bolt (not shown). The same applies for the associated motor vehicle door.

[0033]

[0032] The drive train 5-9 is equipped in detail with at least two adjacent evoloid toothings 5, 6, 7, 8. A first evoloid toothing 5, 6 and a second evoloid toothing 7, 8 are implemented. On the output side of the drive train 5-9, an output pinion 9 is found, with which a drive claw 10 acts as an actuating element. For this purpose, the drive claw 10 is equipped with a toothed segment 10a which engages with the output pinion 9 and meshes with the drive claw. The drive claw 10 also has a drive arm 10b, through which the locking mechanisms 2, 3 act, specifically, according to this embodiment, the locking claw 3 is lifted out of the locking engagement with the rotary latch 2, as described above.

[0034]

[0033] The two evoloid toothings 5, 6; 7, 8 are directly adjacent to each other. Moreover, each evoloid toothing 5, 6, 7, 8 has a respective evoloid pinion 5 or 7 designed to be rotatable around an associated evoloid axis 5a, 7a. The associated evoloid output wheel 6, 8 is designed to mesh with the associated evoloid pinion 5, 7 and to be rotatable around an associated wheel axis 6a, 8a. It can be seen that the output pinion 9 provided on the output side of the drive train 5-9 is also equipped with an axis 9a which, according to this embodiment, coincides with the wheel axis 8a of the evoloid output wheel 8 of the second evoloid toothing 7, 8.

[0035]

[0034] According to the invention, the design is such that the two evoloid toothings 5,6;7,8 are positioned perpendicular to each other. The vertical arrangement is due to the fact that the two evoloid toothings 5,6;7,8 have the position of their respective evoloid axes 5a,7a perpendicular to each other. The design within the scope of this embodiment is such that the evoloid axis 5a of the first evoloid toothing 5,6 coincides with the drive axis of the output shaft of the electric motor 4. The evoloid pinion 5 of the first evoloid toothing 5,6 is positioned on the associated output shaft of the electric motor 4.

[0036]

[0035] Furthermore, since the evoloid axis 5a of the evoloid pinion 5 and the wheel axis 6a of the evoloid output wheel 6 of the first evoloid toothing 5, 6 are positioned perpendicular to each other, the evoloid output wheel 6 is positioned "on" the evoloid pinion 5 in a quasi-vertical projection or vertical extension of the output shaft of the electric motor 4, so that the evoloid axis 5a of the evoloid pinion 5 of the first evoloid toothing 5, 6 is positioned. As a result, the evoloid output wheel 6 of the first evoloid toothing 5, 6 does not require substantially any lateral installation space and at least partially covers the electric motor 4 with its cylindrical housing when viewed from the front.

[0037]

[0036] In contrast, the evoloid axis 7a and the wheel axis 8a of the second evoloid toothing 7, 8 are positioned parallel to each other. Moreover, the wheel axis 6a of the evoloid output wheel 6 of the first evoloid toothing 5, 6 is designed to coincide with the evoloid axis 7a of the evoloid pinion 7 of the second evoloid toothing 7, 8. As a result, the evoloid output wheel 8 meshing with the evoloid pinion 7 can be positioned directly adjacent to the electric motor 4. The evoloid output wheel 8 of the second evoloid toothing 7, 8 is rotationally fixedly connected to the output pinion 9. For this purpose, the associated one evoloid output wheel 8 and the other output pinion 9 have a common axis 8a, 9a.

[0038]

[0037] Each evoloid toothing 5, 6 and each evoloid toothing 6, 7 is in each case equipped with a helical evoloid toothing with a large transmission ratio. Furthermore, according to this embodiment, both evoloid pinions 5, 7 together with the two evoloid output wheels 6, 8 are in each case designed as plastic gears.

[0039]

[0038] In this way, a simple production with a high level of smoothness is observed.

[0040]

[0039] In contrast, the output pinion 9 together with the actuating element 10 or the driving claw 10 is usually made of metal, in particular steel. The output pinion 9 can be a cold-formed pinion, whereas the driving claw 10 can be designed as a combined stamped / formed part.

[0041]

[0040] With the aid of the illustrated actuator, a reduction ratio of the electric motor 4 of 50:1 or more, or even 80:1 or more can be realized and implemented so that ultimately, sufficient force or a sufficiently high torque is available on the drive arm 10b of the drive claw 10 to safely lift the claw 3 from its locking engagement with the rotary latch 2, in this embodiment. [Explanation of symbols]

[0042] Housing 1, Rotating latch 2, Locking mechanism 2,3, Claw part 3, Electric motor 4, Evoroid pinion 5,7, Evoroid axis 5a, 7a, Wheel axles 6a, 8a, Evoroid output wheel, 6,8, Evoroid teeth 5,6,7,8, Drive train 5,6,7,8,9, Output pinion 9, Axis 8a, 9a, Actuating elements 10 Driving claw 10, Toothed segment 10a, Drive arm 10b.

Claims

1. An actuator for motor vehicle applications, in particular for motor vehicle locks, comprising an electric motor (4) and an actuating element (10) which is acted on directly or indirectly by said electric motor (4) via a drive train (5-9), preferably an actuator integrated in a motor vehicle door lock, The drive train (5-9) comprises at least one first evoloid toothing (5, 6) and at least one second evoloid toothing (7, 8) adjacent to each other; Each of the evoloid toothing portions (5, 6; 7, 8) has an evoloid pinion (5, 7) rotatable about an evoloid axis (5a, 7a), and an evoloid output wheel (6, 8) meshing with the evoloid pinion and rotatable about a wheel axis (6a, 8a), 1. An actuator, characterized in that said two evoloid teeth (5, 6; 7, 8) are positioned perpendicular to each other such that the majority of said two evoloid axes (5a, 7a) are perpendicular to each other.

2. 2. An actuator according to claim 1, characterized in that the evoloid axis (5a) of one of the two evoloid toothings (5, 6) and the wheel shaft axis (6a) are positioned perpendicular to each other.

3. 3. An actuator according to claim 2, characterized in that the evoloid axis (5a) and the wheel axis (6a) of the first evoloid toothing (5, 6) lie largely perpendicular to each other.

4. 4. The actuator according to claim 1, wherein the evoloid axis (5a) of the first evoloid toothing (5, 6) and the drive axis of the output shaft of the electric motor (4) coincide.

5. 5. An actuator according to claim 1, characterized in that the wheel axis (6a) of the first evoloid toothing (5, 6) coincides with the evoloid axis (7a) of the second evoloid toothing (7, 8).

6. 6. An actuator according to claim 1, characterized in that the evoloid axis (7a) and the wheel axis (8a) of the second evoloid toothing (7, 8) are positioned substantially parallel to each other.

7. The actuator according to any one of claims 1 to 6, characterized in that the drive train (5-9) is equipped with an output pinion (9) as an operating element (10) for driving a drive claw (10).

8. 8. The actuator according to claim 7, characterized in that the driving claw (10) has a driving arm (10b) for engaging a toothed segment (10a) of the output pinion (9) and acting on a locking mechanism (2, 3) consisting essentially of a rotary latch (2) and a claw (3).

9. 9. An actuator according to claim 7 or 8, characterized in that the output pinion (9) and the drive claw (10) are in each case made of metal, for example steel, and the evoloid pinions (5, 7) and the evoloid output wheels (6, 8) are designed at least partially as plastic gears.

10. A lock for a motor vehicle, in particular a lock for a motor vehicle door, comprising a locking mechanism (2, 3) essentially consisting of a rotary latch (2) and a pawl (3) and an actuator for the locking mechanism (2, 3) which serves as an opening drive for the pawl (3) and / or as a closing drive for the rotary latch (3) and is accommodated together with the locking mechanism (2, 3) in a common housing (1), characterized in that the actuator is as claimed in any one of claims 1 to 9.

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