Driving element and electrical connector having the driving element

Abstract

The invention relates to an electrical connector (1) having a driven element (4) and a driver (2) driving the driven element, and a drive element (8) between the driver and the driven element, and a drive element for such an electrical connector. The electrical connector can be, for example, a charging connector for an electric vehicle. In this case, the driven element is a locking bolt, which is moved by a driver as an electric motor. The drive element (8) is part of a gear unit (10) and has a gear (16). In order to increase the service life of the electrical connector (1), according to the invention, an overload connector (14) is integrated in the drive element, between the gear of the drive element and the hub (30).

Description

Technical Field

[0001] The present invention relates to a driving element with a gear for an electrical connector and to an electrical connector with the driving element. Background Art

[0002] For example, in the prior art of charging connectors, in particular charging sockets for electric vehicles, such drive elements are used. To charge the electric vehicle, the charging connector is locked by means of a movable bolt. To move the bolt, a drive is provided, for example in the form of an electric motor. The drive element, usually a sprocket as part of a gear unit, is located between the drive and the bolt.

[0003] In practice, it has been shown that the service life of such plugs does not yet meet the highest requirements. The object forming the basis of the present invention is therefore to provide a drive element or an electrical connector with an increased service life. Summary of the invention

[0004] According to the invention, with the drive element mentioned above, the above mentioned problem is solved in that the drive element has an overload coupling between the gear and the hub.

[0005] For an electrical connector having a driven element, such as a locking bolt, and a driver for driving the driven element, this problem is solved by such a drive element being located between the driver and the driven element.

[0006] By using such an overload coupling, the service life of the plug can be surprisingly extended. The influence of acceleration and braking on the service life of the drive element appears to be mitigated by the overload coupling. In particular, failures of the drive element or the entire electrical connector due to broken teeth can be successfully prevented by the inventive measure.

[0007] In the following, the features which are each advantageous per se and which improve the invention independently of one another are described in more detail. The following features can be combined with one another as desired.

[0008] Thus, in the first configuration according to the invention, the overload coupling may not protrude axially beyond the gear. This means that the drive element with the overload coupling takes up the same installation space as a conventional drive element without an overload coupling. Thus, with this configuration, a drive element with an overload coupling may be used instead of a conventional drive element without an overload coupling, without structurally changing the electrical connector.

[0009] The gear is preferably an externally toothed gear, which facilitates the construction and assembly of the gear unit of the electrical connector.

[0010] In particular, the drive element is an injection-molded part, preferably made of plastic, so that it can be produced inexpensively in large quantities with low tolerances.

[0011] Preferably, the coaxial pinion can be integrally integrated into the drive element.Depending on the configuration, the pinion protrudes axially from the gear or is axially offset relative to the gear, so that the drive element can be used as part of a gear unit.

[0012] Preferably, a shaft section which likewise protrudes axially from the gear can be located between the pinion and the overload coupling. In another configuration, such a shaft section can be absent and the pinion can directly adjoin the gear in the axial direction or can also form a hub without a spacing between the pinion and the gear in the axial direction. The pinion preferably has a smaller number of teeth or a smaller diameter than the gear.

[0013] Furthermore, an axially protruding journal for rotatably placing the drive element in the electrical connector can be designed integrally with the hub of the drive element.

[0014] The pinion, the shaft section and / or the journal represent preferred axial extensions of the hub.

[0015] The overload coupling is preferably configured as a sliding coupling or sliding hub, and in particular as a friction coupling, wherein the torque can be transmitted between the hub and the gear via a friction connection. A coupling configured in this way is simple and inexpensive to manufacture.

[0016] The overload coupling can have a friction surface which is directed radially inwards or outwards, preferably annular. The friction surface can in particular form a gear part of the overload coupling. The friction surface is preferably aligned coaxially or concentrically with the axis of rotation of the gear.

[0017] The overload coupling preferably has a predetermined overload torque or slip torque, so that it acts as a torque limiter. If the slip torque has not yet been reached, the overload coupling forms a rotationally fixed connection between the hub and the gear. If the slip torque is exceeded, the overload coupling slips through and only transmits the remaining torque.

[0018] According to another advantageous configuration, a separate hub part can be inserted into the gear, which hub part is held in the gear in a friction-locking manner in the circumferential direction and is part of the overload coupling. In particular, the hub part can be supported in a friction-locking manner on the friction surface of the gear in the radial direction. In this case, the hub part preferably forms the hub of the drive element in its entirety.

[0019] In order to captively connect the hub part to the gear wheel, the hub part can be held in the gear wheel in an axial direction in a form-fitting manner.

[0020] The drive element can be assembled together simply when the hub part is axially latched (e.g. clamped) in the gear. Thus, in order to assemble the drive element together, it is only necessary to press the hub part into the gear in the axial direction. The drive element preferably consists only of the hub part and the gear, so that only these two elements have to be joined together in order to produce the drive element.

[0021] The axial form-fit connection can be realized, for example, by an axial blocking or axial latching form-fit element, which can be moved relative to each other in the circumferential direction. For example, in order to latch, the overload coupling can include at least one radially protruding protrusion (e.g., a burr or a rib), which at least partially extends in the circumferential direction, and a recess, which is complementary to the protrusion and receives the protrusion. Depending on the configuration, the protrusion can protrude inwardly or outwardly in the radial direction. Therefore, the complementary recess can rebound outwardly or inwardly in the radial direction. The recess preferably extends continuously in the circumferential direction, so that when the coupling slides over, the protrusion in the recess can rotate completely around the axis of rotation of the drive element in the circumferential direction.

[0022] In a variation of the above-described arrangement, the annular friction surface may also be arranged on the hub part.

[0023] The overload coupling preferably has a plurality of radially elastic spring elements which are spaced apart from one another in the circumferential direction and which press against radially opposing friction surfaces when the drive elements are coupled together. The spring elements produce the torque-transmitting friction connection of the overload coupling.

[0024] In a variant, the radially elastic spring element can be arranged on the hub part and the radially opposite friction surface can be arranged on the gear. Alternatively, the radially elastic friction element can also be arranged on the gear and the radially opposite friction surface can be arranged on the hub part. As already explained above, the friction surface is preferably annular. In order to be able to use the largest possible friction surface for the friction connection, it is more advantageous to arrange the spring element at the hub part, because in this way the friction surface is placed further outward in the radial direction.

[0025] A simple configuration with a long service life can be achieved when at least one spring element has a section, in particular a leaf spring-like section, which extends in a curved manner in the circumferential direction. The curved or curved section presses against the friction surface so that a friction connection is produced when the drive element is fully mounted. In addition, such a spring element is simple in construction and correspondingly easy to manufacture. In particular, such a spring element can also be molded integrally with the hub part or with the gear by the method of injection molding.

[0026] If the spring element is located radially inside the friction surface, the arcuate section is preferably more curved than the friction surface radially opposite the spring element.If the spring element is located radially inside the hub portion, the arcuate section is preferably less curved than the friction surface opposite the spring element.

[0027] To save material and increase flexibility, the arcuate segment can be connected to the rest of the hub part or the rest of the gear wheel via one spoke.

[0028] In another configuration, the curved section can be formed by a strip element which, in the case of the finally mounted drive element, presses against the friction surface in the section between its two ends. In the case of this configuration, the strip element acts as a leaf spring which deflects in the radial direction and creates a friction connection.

[0029] The strip-shaped element preferably has a depth in the axial direction which is greater than its material thickness in the radial direction or in a direction perpendicular to the axial direction.

[0030] The strip-like segment can be connected to the hub or the gear at least at one end and can form a base point there. At the base point, the strip-like segment can extend away from the hub or the gear in the radial direction. At its other end, the strip-like segment can be bent back in the radial direction to the hub or the gear. The other end can be a free end or can likewise be connected to the hub or the gear, thus forming a second base point. Due to the bend, on the one hand, abutment of the spring element against the friction surface and on the other hand radial elasticity are achieved in a constructive manner.

[0031] The at least one curved or heavily curved region may be located between a base point of the at least one spring element and a section of the spring element that abuts against the friction surface opposite the spring element.Deformations of the spring element may be concentrated, for example, in the curved or heavily curved region.

[0032] At least one spring element is preferably configured as a ring. This means, for example, that the spring element has two base points on the hub (or alternatively on the gear) which join the ends of the ring and where the spring element is connected to the hub (or alternatively to the gear).

[0033] When the at least one spring element is part of the hub part, the ring preferably extends radially outwards, i.e. away from the axis of rotation of the drive element. The base point of the spring element is located on the hub. Conversely, if the at least one spring element is located on the gear, the ring preferably extends radially inwards and the base point is located on the gear.

[0034] According to another advantageous configuration, the two base points of the ring are spaced further apart from each other in the circumferential direction than adjacent base points of two consecutive rings in the circumferential direction. Due to the large spacing between the two base points of the ring, a large span can be achieved, so that the spring element lies flat on the friction surface to generate high friction and at the same time has sufficient elasticity.

[0035] In a particular configuration of the ring, this can be lens-shaped or elliptical in axial view, at least in the undeformed state or at least in the deformed state, with the area with lower curvature bearing against the friction surface. The lens-shaped or elliptical shape thus results in a more extensive bearing than a circular ring. However, a circular configuration of the ring is also possible if the disadvantage of a smaller bearing area between the spring element and the friction surface is accepted.

[0036] The annular configuration of the spring element can be injection molded in a particularly simple manner. In the case of such a configuration, the spacer of the injection mold can be located between the pinion and the ring molded on the hub part, or in the ring itself. For example, a circumferential shoulder can be arranged between the pinion and the ring. The inner contour of the ring can be continued from the hub slightly in the direction of the pinion in the axial direction, so that a shaft section is formed between the pinion and the hub.

[0037] In the case of an electrical connector, there is preferably a stop against which the driven element moves in at least one end position. Specifically, the combination of such a mechanical stop with an overload coupling in the drive element leads to a significantly increased service life compared to the prior art.

[0038] In the following, the invention is explained in more detail by way of example using exemplary embodiments. For elements which correspond to one another in terms of function and / or construction, the same reference numerals are used in each case in the figures.

[0039] It should be noted that the combination of features of the described embodiments can be modified according to the above-described implementation. For example, if the technical effect of a feature is not important in a specific application, the feature described and / or described in the embodiment can be omitted. On the contrary, if the technical effect of another above-mentioned feature is advantageous for a specific application, the feature can be added to the described embodiment. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] In the attached picture:

[0041] Figure 1 A schematic diagram showing an electrical connector with a driving element according to the present invention is shown;

[0042] Figure 2 shows a schematic perspective exploded view of a drive element according to the invention;

[0043] Figure 3A schematic perspective view shows a drive element according to the invention in the assembled state. DETAILED DESCRIPTION

[0044] Figure 1 An electrical connector 1 is shown, which is used, for example, as a charging socket for an electric vehicle. The electrical connector 1 has a driver 2, for example an electric motor, and a driven element 4, for example a locking bolt 6. Located between the driver 2 and the driven element 4 is a drive element 8, which is in particular configured as a sprocket and can be part of a gear unit 10. In addition, the electrical connector 1 can have at least one preferably mechanical stop 12, which the driven element 4 stops when fully extended ( Figure 1 or moves against the mechanical stop 12 in the fully retracted position.

[0045] As reference below Figure 2 Explained in more detail, the drive element 8 has an overload coupling 14 between the gear 16 and the hub 18. The overload coupling 14 projects in the axial direction 20 without exceeding the gear 16. The overload coupling limits the maximum torque transmitted between the hub 30 and the gear 16 to a predetermined torque.

[0046] The overload coupling can be designed in particular as a sliding coupling, which slides past a predetermined sliding torque. If the sliding torque has not yet been reached, the hub and the gear are connected to each other in a rotationally fixed manner. When the sliding torque is exceeded, the hub and the gear rotate relative to each other, the overload coupling slides past and the overload coupling transmits only a reduced residual torque. The overload coupling thus acts as a torque limiter.

[0047] Furthermore, the drive element 8 may also have a pinion 22 which is preferably aligned coaxially with the gear 16 and offset in the axial direction relative to the gear 16. A shaft section 24 which is preferably toothless may be located between the hub 18 and the pinion 22.

[0048] Reference below Figure 2 and 3 The structure and function of the drive element 8 are explained in more detail. The drive element 8 preferably consists of only two parts, namely a gear part 26 forming the gear 16, and a hub part 28 forming the hub 30 of the drive element 8. The gear part 26 and the hub part 28 are preferably injection molded parts and are made of plastic. The gear part 26 and the hub part 28 together form the overload coupling 14.

[0049] To assemble the drive element 8, the hub part 28 is inserted into the gear part 26 in the axial direction 20. The hub part 28 is captively held in the gear part 26 in the axial direction by an axially blocking form-fit connection. In a circumferential direction 32 about the axial direction 20 or the axis of rotation 34 of the drive element 8, the hub part 28 is preferably held only in a friction-locking manner in the gear part 26. The friction-based overload coupling is produced by the friction-locking holding.

[0050] In order to simplify the assembly of the hub part 28 with the gear part 26 , the hub part 28 is locked or clipped into the gear part 26 in the axial direction 20 .

[0051] The form-fitting element 36, which enables the axial fixation of the hub part 28 in the gear part 26, can include, for example, at least one radially protruding rib 38, which is concentric with the gear and runs in the circumferential direction, and at least one groove-shaped recess 40, which is configured complementary to the rib 38 and continues in the circumferential direction 32. The recess 40 is preferably concentric with the gear. In the assembled state, the at least one rib 38 is received in the at least one socket 40.

[0052] The form-fit element 36 therefore serves not only for axial fixing but also for guiding in the circumferential direction in order to define a plane in which a relative rotation between the gear part 26 and the hub part 28 is possible when the coupling is slid over.

[0053] replace Figure 2 The configuration shown in FIG. 2 with a single continuous rib can of course also be provided with a plurality of ribs spaced apart from one another in the circumferential direction. Furthermore, instead of a single rib, a slot running in the circumferential direction or a plurality of protrusions arranged in an annular pattern adjacent to one another in the axial direction can be present, for example, at the hub portion 28 and the gear portion 26, in which configuration the slots of the hub portion 28 and the gear portion 26 are splined to one another in the axial direction 20.

[0054] The ribs 38 are actually molded into Figure 2 However, in a variant, it can also be designed on the hub part 28, so that the recess 40 is then located on the gear part 26 accordingly.

[0055] The overload coupling 14 has a friction surface 42 at the gear portion and a friction surface 44 at the hub portion. One of the two friction surfaces 42, 44, here the friction surface 44 at the hub portion, does not have to be continuous in the circumferential direction 32, but can be divided into several partial surfaces 46 spaced apart from one another in the circumferential direction.

[0056] When the drive elements are assembled together, the friction surfaces 42, 44 are pressed against each other to allow the drive torque to be transmitted from the driver 2 to the driven element 4 ( Figure 1 ).

[0057] In order to produce the friction connection, the overload coupling 14 has at least one radially elastic spring element 48, which is elastically deformed in the radial direction when the hub part 28 is inserted into the gear part 26 and presses one friction surface against the other friction surface in order to produce a friction connection between the hub part 28 and the gear part 26. The overload coupling 14 preferably has a plurality of radially elastic spring elements 48, which are preferably evenly spaced apart from one another in the circumferential direction 32 and which press against radially opposite friction surfaces (here 42).

[0058] As an example only, Figure 2 In the exemplary embodiment shown, the spring elements 48 are molded onto the hub portion 28. They can also be molded onto the gear portion 26 in a variant not shown. In this case, the annular friction surface 42 is not as good as Figure 2 The annular friction surface 42 is not located on the gear part 26 as in the embodiment of the present invention, but on the hub part 28. In particular, the annular friction surface 42 can be formed directly by the hub 30, which is then clamped in the gear part 26.

[0059] Likewise, just as an example, in Figure 2 3 spring elements 48 following one another in the circumferential direction are shown in FIG. This number is arbitrary, but preferably there are two to six spring elements 48 .

[0060] The spring element 48 has a section 50, in particular a leaf spring, which extends in a curved manner in the circumferential direction 32. The section 50 abuts against the opposing friction surface 42 at least in the region of the friction surface 44 in order to produce the largest possible bearing surface. If the spring element 48 is located radially inside the opposing friction surface, the section 50 preferably has a greater curvature than the friction surface 42 located opposite it.

[0061] The arc segment 50 can be connected to the hub 30 via at least one spoke 52, or to the gear portion 26 in the case where the spring element 48 is arranged on the gear portion 26. If there are two spokes 52 in the case of the spring element 48, the spring element 48 can form a ring 54 protruding in the radial direction. The ring can be configured in a lens-like or elliptical manner in an axial view, but can also be configured in a circular manner. The ring 54 forms a channel 56 together with the hub 30, which is closed in the radial direction and open axially.

[0062] The spring element 48 has at least one base point 58 at which it is connected to the gear part 26 or to the hub part 28 , depending on whether the ring is formed by the gear part 26 or by the hub part 28 .

[0063] If the spring element 48 forms a ring 54 together with the hub 18, the spring element has two base points 58. In this case, the two base points 58 of the ring are spaced further apart from each other in the circumferential direction 32 than two adjacent base points 58 of two spring elements 48 or rings 54 following each other in the circumferential direction 32.

[0064] At least one curved or heavily curved region 60 may be located in the region between the base point 58 of the spring element 48 and the section of the spring element 48 that bears against the opposing friction surface 42 , ie, the friction surface 44 .

[0065] The curved section 50, at least one spoke 52 and / or the ring 54 can be formed by a band section 62 of the hub portion 28 or the gear portion 26. In this case, the depth 64 of the band 66 forming the band section 62 is greater than the material thickness 68 of the band 66 perpendicular to the depth 64, for example two or three times greater.

[0066] The radial elastic band 66 initially extends away from the base point 58 in the radial direction, and may also have a component in the circumferential direction 32. This area forms the spoke 52. It can be bent back in the radial direction at its other end. The other end can be a free end, or, as shown in the figure, can end in another base point 58.

[0067] To enable simple manufacturing in an injection molding method, at the hub portion 28, a portion of the profile of the channel 56 can extend in the axial direction 20 over an axial depth 70 of the gear 26, which preferably corresponds to the depth 64 of the band 66, and can terminate in a shoulder 72, which is located between the hub 30 and the pinion 22. The preferably continuous circumferential shoulder 72 can represent a parting plane of the injection molding tool.

[0068] The hub part 28 finally has two further axially projecting journals 74 in order to be able to rotatably position the drive element 8 in the electrical connector 1 .

[0069] Reference numerals list

[0070] 1 Electrical connector

[0071] 2 Drivers

[0072] 4 Driven element

[0073] 6 Locking bolt

[0074] 8 Drive components

[0075] 10 Gear Unit

[0076] 12 Stopper

[0077] 14 Overload connector

[0078] 16 Gear

[0079] 18 Hub

[0080] 20 Axial direction

[0081] 22 Small gear

[0082] 24 Axis Segment

[0083] 26 Gear part

[0084] 28 Hub section

[0085] 30 Hub

[0086] 32 Circumferential direction

[0087] 34 Rotation axis

[0088] 36 Form-fitting elements

[0089] 38 Ribs or protrusions

[0090] 40 Depression

[0091] 42 Friction surface at the gear section

[0092] 44 Friction surface at hub part

[0093] Partial surface of 46 44

[0094] 48 Spring element

[0095] 50 Bending section of spring element

[0096] 52 spokes

[0097] 54 rings

[0098] 56 channels

[0099] 58 basis points

[0100] 60 Bend or heavy bend area

[0101] 62 Strip segments

[0102] 64 Belt Depth

[0103] 66 belt

[0104] 68 Belt material thickness

[0105] 70 Depth of gear section

[0106] 72 Shoulder

[0107] 74 Journal

Claims

1. A drive element (8) for an electrical connector, wherein the drive element (8) has a gear (16), characterized in that: The drive element (8) has an overload coupling (14) between the gear (16) and the hub (30), The gear (16) is part of a gear section (26), into which a hub section (28) is inserted, and the hub section (28) is held in the gear section (26) in a friction-locked manner in a circumferential direction (32), The hub part (28) is held in the gear part (26) in a form-fitting manner in the axial direction (20), The overload coupling (14) has a plurality of radially elastic spring elements (48) which are spaced apart from one another in the circumferential direction (32) and which press against radially opposing friction surfaces (42, 44), At least one spring element (48) has a section (50) extending in a curved manner in the circumferential direction (32) which bears against the radially opposing friction surfaces (42, 44).

2. The drive element (8) according to claim 1, characterized in that The overload coupling (14) does not protrude axially beyond the gear.

3. The drive element (8) according to claim 2, characterized in that The gear part (26) or the hub part (28) has a radially inwardly directed circular friction surface (42) which is part of the overload coupling (14).

4. The drive element (8) according to any one of claims 1 to 3, characterized in that The hub portion (28) is axially latched in the gear portion (26).

5. The drive element (8) according to claim 4, characterized in that For a form-fitting connection of the hub part (28) and the gear part (26), the overload coupling (14) has at least one radially projecting protrusion and a recess (40) complementary to the protrusion, in which the protrusion is received movably in the circumferential direction (32) and is fixed in the axial direction when the drive element (8) is assembled.

6. The drive element (8) according to claim 1, characterized in that The curved section (50) is formed by a leaf spring-shaped band (66) which is pressed into the section between its two ends (58) against the radially opposed friction surfaces (42, 44).

7. The drive element (8) according to claim 1, characterized in that The at least one spring element (48) extends radially away from a base point (58) at the gear portion or at the hub portion, and at least one curved or heavily curved region (60) is located between the base point and a section of the spring element (48) that abuts the radially opposing friction surfaces (42, 44).

8. The driving element (8) according to any one of claims 1, 6-7, characterized in that: At least one of the spring elements (48) forms a ring (54).

9. The drive element (8) according to claim 8, characterized in that The ring (54) is lenticular, elliptical or circular in axial view, at least in the undeformed state or at least in the deformed state.

10. The driving element (8) according to any one of claims 1, 6-7, characterized in that: The components of the drive element are injection moulded.

11. An electrical connector (1) comprising a driven element (4) and a driver (2) for driving the driven element, characterized in that: A drive element (8) according to any one of claims 1 to 10 between the driver (2) and the driven element (4).

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