Connectors and Connector Systems

Abstract

To provide more compact connector coupling, especially for a connector system with high coupling force.SOLUTION: In a connector including an inner shell 3, an outer shell 5, and a gear wheel, the gear wheel is arranged in a rack-and-pinion arrangement together with a first linear gear 29, the gear wheel is connected to the inner shell through a hinge so as to be rotatable about a hinge axis perpendicular to a mating direction. The gear wheel includes a first set of external gear teeth 41 configured to engage with the first linear gear in the rack-and-pinion arrangement, and a second set of external gear teeth 45 configured to engage with a second linear gear 105 of a mating connector 100, the first and second sets of external gear teeth being arranged in the same plane.SELECTED DRAWING: Figure 3A

Description

[Technical Field]

[0001] The present invention relates to a connector configured to mate with a mating connector, the connector comprising an inner shell, an outer shell, and a gear wheel. The present invention also relates to a connector system comprising the connector. [Background technology]

[0002] Connector systems are known in the art that include a connector, a mating connector, and a mating system designed to facilitate mating of the connector and the mating connector, which reduces the force, precision, and / or skill required to successfully mate the connectors, thereby improving user comfort and reliability of the connector system.

[0003] A typical coupling system incorporated into a high coupling force connector system is a lever system, in which one connector is provided with an external lever hingedly connected to the connector housing, and the mating connector is provided with a structure configured to hook onto the action side of the lever. An alternative solution is disclosed in patent document U.S. Pat. No. 9,917,402 (B1), in which the coupling system includes a conventional circular gear and a cam gear with a variable pitch radius, the cam gear and the circular gear communicating with each other to form a stacked gear.

[0004] At the same time, many modern technological environments are becoming increasingly space constrained, with reduced room for connector placement and access, making proposed large coupling systems unsuitable. Summary of the Invention [Problem to be solved by the invention]

[0005] SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a more compact connector coupling solution, especially for connector systems with high coupling forces. [Means for solving the problem]

[0006] This object is achieved by a connector according to the present disclosure. The connector is configured to mate with a mating connector in a mating direction and includes an inner shell, an outer shell, and a gear wheel. The outer shell at least partially surrounds the inner shell and is configured to move relative to the inner shell in the mating direction. The outer shell includes a first linear gear disposed on an inner surface of the outer shell along the mating direction. The gear wheel is disposed in a rack-and-pinion configuration with the first linear gear and is hingedly connected to the inner shell to be rotatable about a hinge axis perpendicular to the mating direction.

[0007] The connector is characterized in that the gear wheel has a first set of external gear teeth configured to engage with a first linear gear in a rack and pinion arrangement and a second set of external gear teeth configured to engage with a second linear gear of the mating connector, the first and second sets of external gear teeth being arranged in the same plane.

[0008] In this configuration, the gear wheel facilitates coupling of the connector with the mating connector in a more compact arrangement. Because the first and second sets of external gear teeth are arranged in one plane, the gear wheel itself is kept smaller in size and mass than those known in the prior art. Furthermore, because the first and second sets of external gear teeth are configured to engage with the linear gear of the outer shell and the second linear gear of the mating connector, respectively, the linear gears can also be arranged therein, thereby reducing the overall cross-sectional size of the connector.

[0009] Additional optional features and various aspects of the connector are described below, which features and aspects may be freely combined with one another to provide further possible embodiments or aspects of the connector of the present invention.

[0010] In one aspect of the connector, a first pitch radius of the first set of external gear teeth can be different from a second pitch radius of the second set of external gear teeth. The pitch radius of a gear wheel is the distance between the center of the gear wheel and the gear's pitch point, i.e., the contact point of the meshing gear teeth. The different pitch radii can provide advantageous leverage and facilitate mating.

[0011] In one aspect of the connector, the first pitch radius may be larger than the second pitch radius, such that, according to the law of leverage, the coupling force applied to the second linear gear by the second set of external gear teeth, i.e., the output force of the gear wheel, is increased relative to the force applied to the outer shell, i.e., the input force of the gear wheel.

[0012] In one embodiment of the connector, the first pitch radius may be 1.2 to 5 times, particularly 1.5 to 3 times, larger than the second pitch radius, so that the output force can be increased by the factor of 1.2 to 5, particularly 1.5 to 3. This factor provides an advantageous balance between force multiplication, compactness of the gear wheel, and structural stability of the gear wheel.

[0013] In one embodiment of the connector, the first set of teeth and the second set of teeth may have the same pitch angle and / or tooth thickness and / or tooth width. The pitch angle is the angle included between the pitch points of two consecutive gear teeth of the gear wheel. The tooth thickness is the thickness of the gear teeth at the pitch point in a plane perpendicular to the hinge axis. The tooth width is the width or extension of the gear teeth along a direction parallel to the hinge axis. This improves torque transmission between the first set of external gear teeth that engages with the linear gear of the outer shell and the second set of external gear teeth that engages with the second linear gear of the mating connector.

[0014] In one embodiment of the connector, the first set of teeth and the second set of teeth may have the same dimensions, which simplifies manufacturing, e.g., injection molding, of the gear wheels and linear gears of the connector and mating connector, making the components more cost-effective.

[0015] In one aspect of the connector, the inner shell may be configured to mate with a housing element of a mating connector, the inner shell including a recess extending along the mating direction, the recess configured to receive the second linear gear of the mating connector when the inner shell is mated with the housing element such that the second set of external gear teeth can engage with the second linear gear. Thus, the connector can receive the second linear gear of the mating connector in a configuration suitable for engagement with the second set of external gear teeth without increasing the cross-sectional size of the connector.

[0016] In one aspect of the connector, the gear wheel may include at least one gear tooth flap, which is a radial protrusion that extends beyond the gear wheel circumference along the same angular region of the gear wheel circumference as the gear teeth but is axially offset with respect to the hinge axis so as not to interfere with engagement of the gear teeth. The gear tooth flap reinforces the structural integrity of the gear teeth, which may be at risk when high mating forces are required.

[0017] In one aspect of the connector, the gear wheel may include a first gear tooth flap in an angular region of the gear wheel corresponding to the first set of external gear teeth and a second gear tooth flap in an angular region of the gear wheel corresponding to the second set of external gear teeth, thereby structurally reinforcing both the first and second sets of external gear teeth relative to the gear wheel.

[0018] In one embodiment of the connector, the second flap is positioned opposite the first flap, i.e., the first and second flaps are positioned on opposite sides of the gear wheel along the hinge axis, which improves axial balance of the gear wheel.

[0019] In one embodiment of the connector, the first flap may be positioned on a side of the first set of external gear teeth opposite the inner surface of the outer shell, and the second flap may be positioned on a side of the second set of external gear teeth opposite the outer surface of the inner shell. This configuration improves guidance of engagement between the first set of external gear teeth and the linear gear of the outer shell and provides protection from interference by the first flap. Correspondingly, guidance of engagement between the second set of external gear teeth and the second linear gear can be improved and protected from external interference by the second flap.

[0020] In one aspect of the connector, the outer shell may be configured to move relative to the inner shell from a first, uncoupled position to a second position in which the connector couples with a mating connector, the inner shell including a protrusion formed on an outer surface of the inner shell to which the gear wheel is hingedly connected, the gear wheel including a recess configured to mate with the protrusion and receive the protrusion in the first position. According to this aspect, the outer shell can be stabilized relative to the inner shell in the first position by frictional engagement of the protrusion of the inner shell with the recess of the gear wheel. This improves operability of the connector because frictional resistance must be overcome to move the outer shell relative to the inner shell and initiate coupling with the mating connector.

[0021] In one aspect of the connector, the gear wheel may include at least one cut-out area, which allows for a reduction in the mass and material costs of the gear wheel, especially in angular areas around the gear wheel center that are not structurally necessary, in other words, in the "pie slices."

[0022] In one embodiment of the connector, at least one cutout area is included in the angular region of the gear wheel between the first and second sets of teeth, which allows for an angular movement path for the protrusion (formed on the outer surface of the inner shell) on the gear wheel when the protrusion is disengaged from the recess and coupling is initiated. In other words, friction between the gear wheel and the protrusion is reduced, facilitating rotation of the gear wheel.

[0023] In one aspect of the connector, the cutout area may be a completely hollowed out area, which further reduces the mass and material costs of the gear wheel.

[0024] In one aspect of the connector, the gear wheel may be disposed between the inner shell and the outer shell, such that the gear wheel is enclosed by the outer shell and is not externally accessible, thereby reducing the risk of mishandling or damage to the gear wheel, thereby increasing the reliability of the coupling system.

[0025] In one aspect of the connector, the gear wheel may be disposed between the inner shell and the outer shell in a plane parallel to the mating direction, thereby reducing the minimum distance between the outer surface of the inner shell and the surface of the outer shell, further increasing compactness.

[0026] In one embodiment of the connector, the connector may include a connector position assurance device (CPA) configured to lock the relative position of the outer shell in the mating direction with respect to the inner shell in the second position. The CPA is arranged to be movable relative to the outer shell from an unlocked position to a locked position. The CPA is arranged on the outer shell such that one distal end of the CPA is disposed in a receiving pocket formed in the outer shell of the connector and the other distal end opposite the one distal end is disposed outside the receiving pocket. The CPA includes a locking nose. A corresponding locking notch is formed in the outer surface of the inner shell and configured to receive the locking nose when the outer shell is in the second mating position with respect to the inner shell and the CPA is moved to the locked position with respect to the outer shell. The CPA configured in this manner provides a locking function for the connector when mated with a mating connector while maintaining a compact assembly.

[0027] In one aspect of the connector, the ratio of the first pitch radius to the second pitch radius corresponds to the ratio of the number of external gear teeth in the first set to the number of external gear teeth in the second set, which allows for better distribution of the coupling force across the engagement of each gear tooth, thereby smoothing the force transmission by avoiding inappropriately high loads on individual teeth.

[0028] In one aspect of the connector, the inner shell or the outer shell may include a linear cam extending along the mating direction, and the other of the inner shell or outer shell may further include a protrusion configured as a corresponding cam follower for the linear cam, and movement of the outer shell relative to the inner shell includes sliding of the protrusion along the linear cam. The linear cam and corresponding protrusion can provide a sliding motion that advantageously guides and stabilizes movement of the outer shell relative to the inner shell.

[0029] In one embodiment of the connector, the connector may be an electrical connector. Further, the inner shell of the electrical connector may house at least one electrical terminal, particularly an electrical terminal configured for a voltage of 400 V or higher. The electrical connector benefits from the aforementioned compactness and can therefore fit into electrical applications in tight spaces, particularly for charging inlet connections or battery connections in electric vehicles.

[0030] The present invention also relates to a connector system including a connector according to any one of the above-described aspects and a mating connector. The mating connector includes a housing element configured to mate with the inner shell, the housing element including a second linear gear formed on an outer surface of the housing element, the second linear gear configured to engage with the second set when the connector and the mating connector are mated. The connector system of the present invention benefits from the compactness and structural simplicity of the above-described connector having a gear wheel-based mating system in which the two sets of teeth are arranged in the same plane. Because the sets of teeth are arranged in the same plane, the mating connector does not require any additional components. This reduces the risk of increasing the cross-sectional size of the connector defined by the outer shell, making the connector system more compact and more suitable, especially for tight spaces, than prior art connectors with cumbersome coupling solutions such as levers.

[0031] The foregoing aspects, objects, features and advantages of the present invention will be more fully understood and appreciated by careful consideration of the following more detailed description of the presently preferred exemplary embodiments of the invention in conjunction with the accompanying drawings, in which: [Brief explanation of the drawings]

[0032] [Figure 1] 1 illustrates a connector according to an embodiment of the present invention prior to mating with a mating connector. [Figure 2A] FIG. 2 shows a gear wheel of the connector of FIG. 1. [Figure 2B]10A-10C illustrate alternative gear wheels for a connector according to another embodiment of the present invention. [Figure 3A] 2 shows the connector of FIG. 1 during mating with a mating connector. [Figure 3B] FIG. 2 shows the connector of FIG. 1 in a mated but unlocked state. [Figure 3C] FIG. 2 shows the connector of FIG. 1 in a mated and locked state. DETAILED DESCRIPTION OF THE INVENTION

[0033] Unless otherwise indicated, the structural features of objects shown in Figures 1-3C are not drawn to scale, either individually with respect to their Cartesian dimensions or relative to each other along a Cartesian direction. Furthermore, the same reference numbers used in different figures refer to the same elements.

[0034] In the following detailed description of Figures 1-3C, a connector 1 according to one embodiment of the present invention and a connector system 200 according to another embodiment of the present invention will both be described.

[0035] Figure 1 shows a connector system 200 comprising a connector 1 and a mating connector 100. In the view of Figure 1, the connector 1 and the mating connector 100 are shown in a pre-condition prior to mating and locking of the connectors.

[0036] Connector 1 comprises an inner shell 3, an outer shell 5, and a gear wheel 7. For illustrative purposes, in Figure 1, a portion of the cross section of outer shell 5 has been removed (or made transparent) to allow for the visualization of area A, which includes gear wheel 7 and further elements described below.

[0037] In this embodiment, connector 1 is an electrical connector and mating connector 100 is an electrical header mating connector. Connector 1 includes four electrical terminals (not shown) housed in four respective terminal cavities 9. Connector 1 and mating connector 100 are power connectors for electric vehicles and are configured for high-voltage electrical connections, for example, having a voltage of 400V or greater.

[0038] The connector 1 is configured to mate with a mating connector 100 in a mating direction M parallel to a first Cartesian direction X. In this embodiment, the connector 1, including the inner shell 3 and the outer shell 5, and the mating connector 100 have a square cross section in a plane YZ perpendicular to the mating direction M. An edge 11 of the inner shell 3 parallel to the mating direction M is rounded, while an edge 13 of the outer shell 5 parallel to the mating direction M is chamfered.

[0039] The outer shell 5 partially surrounds the inner shell 3. In particular, the outer shell 5 surrounds the entire periphery of the inner shell 3 in a plane YZ perpendicular to the fitting direction M along an extension range D1 along the fitting direction M that is smaller than the extension range D2 of the inner shell 3. Thus, the outer shell 5 has an inner surface 15 that at least partially faces an outer surface 17 of the inner shell 3.

[0040] The connector 1 further includes a connector position assurance device (CPA) 19 for locking the connector 1 in place when the connector 1 is fully and properly mated with the mating connector 100. The CPA 19 is disposed in a pocket 21 formed in the outer shell 5 and extending along the mating direction M so as to be movable relative to the outer shell 5 in the pocket 21 between an unlocked position and a locked position. In the view of Figure 1, the connector 1 has not yet mated with the mating connector 100, and therefore the CPA 19 is also in the unlocked position.

[0041] CPA 19 has a first distal end 23 and a second distal end (not visible) opposite first distal end 23 in mating direction M. CPA 19 is positioned in pocket 21 such that first distal end 23 remains outside pocket 21 and second distal end remains inside pocket 21 in both the unlocked and locked positions.

[0042] The first distal end 23 of the CPA 19 includes an actuation grip 25. The actuation grip 25 is configured to facilitate manual movement of the CPA 19 in the pocket 21 and is formed to protrude outwardly relative to the inner shell 3. A locking nose (not visible) is formed at the second distal end of the CPA 19 to protrude inwardly and face the outer surface 17 of the inner shell 3. A corresponding locking notch 27 is formed in the outer surface 17 and configured to receive the locking nose when the mated connectors 1, 100 are locked (see FIGS. 3B, 3C).

[0043] Region A shown in FIG. 1 indicates that the outer shell 5 includes a first linear gear 29. The first linear gear 29 is formed on the inner surface 15 of the outer shell 5 and extends along the mating direction M. Specifically, the first linear gear 29 is formed such that the teeth 31 of the first linear gear 31 are oriented parallel to the inner surface 15 of the outer shell 5 and the outer surface 17 of the inner shell 3, such that the first linear gear 29 is disposed parallel to or sandwiched between the inner shell 3 and the outer shell 5. This will be further described with reference to FIGS. 3A-3B.

[0044] The housing element 101 of the mating connector 100 includes a similarly disposed second linear gear 105 extending along the mating direction M. The second linear gear 105 is formed on the outer surface 107 of the housing element 101 such that the teeth 109 of the second linear gear 105 are oriented parallel to the outer surface 107 of the housing element 101.

[0045] Region A also shows that the gear wheel 7 is hingedly connected to a hinge shaft 33 formed on the outer surface 17 of the inner shell 3 and extending along a hinge axis H perpendicular to the mating direction M. The gear wheel 7 is hingedly connected to the hinge shaft 33 so as to be rotatable relative to the hinge shaft 33 and the hinge axis H, and so that the teeth of the gear wheel 7 are engageable with the first linear gear 29 and the second linear gear 105, as will be further explained below.

[0046] As will be further described and illustrated below, the outer shell 5 is movable relative to the inner shell 3 along the mating direction M between an uncoupled position and a coupled position. In FIG. 1 of this description, the connector 1 has been moved adjacent to the mating connector 100, and the inner shell 3 has been mated with a matching housing element 101 of the mating connector 100. Specifically, the inner shell 3 has been inserted over the housing element 101 such that the second linear gear 105 is received in a recess 35 formed in the inner shell 3 that extends along the mating direction M.

[0047] However, the distal edge 37 of the inner shell 3 that houses the terminals in the mating direction M is still separated by a distance D3 from the corresponding abutment portion 103 of the mating connector 100. Therefore, until the distance D3 is overcome, the terminals of the connector 1 and the mating connector 100 are not in the intended contact position, and the connector system 200 is not mated.

[0048] The gear wheel 7 of the connector system 200 described above will now be described with reference to FIG. 2A. FIG. 2A shows the gear wheel 7 alone in a perspective view. In this embodiment, the gear wheel 7 is a one-piece injection-molded part having a central through-hole 39. The central through-hole 39 is configured to receive the hinge shaft 33 and extends along a central axis corresponding to the hinge axis H when assembled to the connector 1. The gear wheel 7 has a first set 41 of external gear teeth 43 and a second set 45 of external gear teeth 47. The teeth 43 of the first set 41 are configured to engage with the first linear gear 29, and the teeth 47 of the second set 45 are configured to engage with the second linear gear 105.

[0049] The first set 41 of external gear teeth 43 is arranged along a first circumferential surface P1 with a first pitch radius R1, which defines a first semicircle C1 about the hinge axis H. Similarly, the second set 45 of external gear teeth 47 is arranged along a second circumferential surface P2 with a second pitch radius R2, which defines a second semicircle C2 about the hinge axis H. The first semicircle C1 and the second semicircle C2 correspond to two opposite halves of the gear wheel 7.

[0050] According to a distinctive feature of the present invention, the first set 41 of external gear teeth 43 and the second set 45 of external gear teeth 47 are arranged in the same plane, for example the plane defined by the midline L, which is the line dividing the gear wheel 7 along the hinge axis H into two halves of equal thickness.

[0051] In other words, the plane in which the first set 41 of teeth 43 is arranged coincides with the plane in which the second set 45 of teeth 47 is arranged, i.e. all gear teeth 43, 47 of the gear wheel 7 extend along the same extent along the hinge axis H. The first set 41 of teeth 43 and the second set 45 of teeth 47 are arranged in the same axial region of the gear wheel 7.

[0052] This characteristic gear wheel 7 allows a single device to ensure advantageous torque transmission for facilitating coupling, which device has a particularly compact and lightweight structure compared to prior art coupling solutions.

[0053] In this embodiment, the value of the first pitch radius R1 is twice the value of the second pitch radius R2. Furthermore, the first set 41 includes six external gear teeth 43 arranged along a first circumferential surface P1 in a first angular region α1 about the hinge axis H. The second set 45 includes three external gear teeth 47 arranged along a second circumferential surface P2 in a second angular region α2 about the hinge axis H. In addition, the teeth 43, 47 of the first set 41 and the second set 45 have the same dimensions, in particular the same pitch angle β, the same arc tooth thickness T, and the same face width W.

[0054] In variants, the first pitch radius R1 may be 1.2 times larger than the second pitch radius R2, or 5 times larger than the second pitch radius R2, or any value therebetween. Preferably, the first pitch radius R1 is 1.5 to 3 times larger than the second pitch radius R2. However, for improved torque transmission and compactness, it is advantageous for the ratio of the first pitch radius to the second pitch radius to correspond to the ratio of the number of external gear teeth in the first set to the number of external gear teeth in the second set.

[0055] The gear wheel 7 comprises a first gear tooth flap 49 and a second gear tooth flap 51. The first flap 49 projects outward from the first peripheral surface P1 along a first angular region α1 adjacent to the teeth 43 of the first set 41. Correspondingly, the second flap 51 projects outward from the second peripheral surface P2 along a second angular region α2 adjacent to the teeth 47 of the second set 45.

[0056] The first flap 49 is positioned adjacent to the teeth 43 on the side opposite the inner surface 15 of the outer shell 5. The second flap 51 is positioned adjacent to the teeth 43 on the side opposite the outer surface 17 of the inner shell 3. The flaps 49, 51 cover at least one side of each gear tooth set 41, 45, thereby improving the structural stability and guidance of the respective engagement with the linear gears 29, 105.

[0057] A recess 53 is formed in the gear wheel 7 in the first angular region α1 and is configured to receive a corresponding protrusion 65 formed on the outer surface 17 of the inner shell 3. The protrusion 65 is not visible in Figures 1 and 2A but is visible in Figures 3A and 3B. The function of the recess 53 and the corresponding protrusion 65 will become clearer in light of Figures 3A-3C and their description.

[0058] In order to reduce the mass and material costs of the gear wheel 7, some radial areas between the central through-hole 39 and the first circumferential surface P1 are cut out, i.e. hollowed out. In this embodiment, the gear wheel 7 comprises three cut-out radial areas 55a, 55b, 55c in the first semicircle C1. In this embodiment, the cut-out areas 55a, 55b, 55c are completely hollowed out, i.e. they extend across the body of the gear wheel 7. In a variant, some or all of the cut-out areas 55a, 55b, 55c may be only partially hollowed out.

[0059] The radial regions 55a and 55b are included in the first angular region α1. The radial region 55c is substantially included in the angular region α3 of the gear wheel 7 between the first angular region α1 and the second angular region α2. The region 55c is configured to receive the protrusion 65 removed from the recess 53 and facilitates rotation of the gear wheel 7 relative to the inner shell 3 by avoiding excessive friction with the protrusion 65.

[0060] As an optional feature, the gear wheel 7 may comprise wheel spoke elements 57 having a predetermined shape in the radial direction of the wheel 7, for example a stepped shape 57a, which is located in the area of ​​initial engagement with the second linear gear 105. If the predetermined shape is adapted to the shape of the tip 105a (see FIG. 3A) of the second linear gear 105 received in the recess 35 and the inner shell 3, an additional foolproof mechanism for initiation of engagement by rotation of the gear wheel can be obtained.

[0061] An alternative gear wheel 7' is shown in FIG. 2B. The gear wheel 7' is a gear wheel suitable for a connector according to another embodiment of the present invention and / or a connector system according to another further embodiment of the present invention. For example, the gear wheel 7' may be a gear wheel for a connector that differs from the connector 1 only in terms of the configuration of the gear wheel. The gear wheel 7' may also be a gear wheel for a connector system that differs from the connector system 200 only in terms of the configuration of the gear wheel. Compared to the gear wheel 7, the gear wheel 7' requires more material, but is also denser and more mechanically robust. Therefore, it has higher reliability and durability.

[0062] The gear wheel 7' differs from the gear wheel 7 only with respect to the cutout radial areas. Thus, the gear wheel 7' also comprises the central through-hole 39, the recess 53, the flaps 49, 51 and the sets of teeth 41, 45. However, the gear wheel does not comprise the same cutout radial areas 55a, 55b, 55c as the gear wheel 7. In particular, instead of the cutout radial areas 55a and 55b, the gear wheel 7' comprises a solid area 55a' that is integral with the rest of the gear wheel 7'. Instead of the cutout radial area 55c, the gear wheel 7' comprises a cutout area 55c'.

[0063] The cutout region 55c' has a reduced, particularly significantly reduced, area in a plane perpendicular to the hinge axis H compared to the cutout radial region 55c. Specifically, the cutout region 55c' has an area in a plane perpendicular to the hinge axis H that corresponds to the minimum area required to accommodate a protrusion, such as the protrusion 65 removed from the recess 53, and to facilitate rotation of the gear wheel 7' relative to the inner shell of the connector. The coupling and locking of the connector system 200 will now be described with reference to Figures 3A, 3B, and 3C. The views of Figures 3A-3C are perspective views of Figure 1, differing in that the outer shell 5 has been partially cut along the midline L of the gear wheel 7 shown in Figure 2A.

[0064] 3A shows the connector system 200 at an intermediate stage in the mating sequence between the connector 1 and the mating connector 100. After the inner shell 3 has mated with the housing element 101 of the mating connector 100 and is in the position shown in FIG. 1, the outer shell 5 is moved, preferably manually pushed, in the mating direction M.

[0065] To facilitate movement of the outer shell 5 relative to the inner shell 3, linear protrusions 59 extending along the fitting direction M are provided on the outer surface 17 of the inner shell 3 over at least half of the extension range D2 along the fitting direction M of the inner shell 3. The linear protrusions 59 are arranged on corresponding linear cams 61 formed on the inner surface 15 of the outer shell 5. Thus, when the outer shell 5 moves relative to the inner shell 3, the outer shell 5 can slide smoothly and guided along the outer surface 17 of the inner shell 3.

[0066] As the outer shell 5 slides along the cam 61 relative to the inner shell 3 in the mating direction M, the first linear gear 29 also moves in the mating direction M and engages with the first set of external gear teeth 41. As the outer shell 5 moves in the mating direction M, the gear wheel 7 rotates in a clockwise direction O about its hinge shaft 33 in a rack-and-pinion configuration in which the first linear gear 29 is configured as a rack and the gear wheel 7 is configured as a pinion follower. The clockwise rotation O of the gear wheel 7 causes the second set of external gear teeth 45 to engage with the second linear gear 105 on the other side of the gear wheel 7. Thus, as the gear wheel 7 rotates in the clockwise direction O, the second set of teeth 45 applies a coupling force to the second linear gear 105 in a direction opposite to the mating direction M, pulling the mating connector 100 toward the connector 1. The large first pitch radius R1 relative to the second pitch radius R2 (see FIG. 2A) provides advantageous force transmission of the coupling force applied to the outer shell 5 to the mating connector 100.

[0067] Advantageous force transfer is particularly important in electrical connector applications requiring multiple electrical terminals where the required mating force is cumulative with respect to the number of electrical terminals. However, advantageous force transfer may also be important in alternative embodiments where the connector is not an electrical connector, but is instead, for example, a hydraulic connector. In the case of a hydraulic connector system, the mating system must overcome the sealing force of a sealing structure configured to make the connector system watertight.

[0068] Figure 3A (as well as Figures 3B and 3C) shows the gear teeth of both the first set 41 and second set 45 of gear wheel 7, their respective engagement with first linear gear 29 and second linear gear 105, as well as cutout regions 55a, 55b, 55c of gear wheel 7. In addition, Figure 3A shows the underside 63 of recess 53 formed in gear wheel 7 and partially shows protrusion 65 formed on outer surface 17 of inner shell 3 that is configured to be received in recess 53 in the default, unattached shipping state. Protrusion 65 is more clearly visible in Figures 3B and 3C.

[0069] In Figure 3A, the indentation of the outer shell 5 overcomes the initial frictional resistance caused by the friction fit of the protrusions 65 in the recesses 53. The gear wheel 7 has been removed from the stable shipping state and is rotating clockwise O.

[0070] 3B, the distal edge 37 of the connector 1 abuts the abutment 103 of the mating connector 100. Thus, the movement of the outer shell 5 relative to the inner shell 3 and the movement of the gear wheel 7 acting as a pinion relative to the first linear gear 29 acting as a rack have reached their limits. With the outer shell 5 in the mated position and all electrical contacts in place as intended, the connector system 200 is fully mated.

[0071] However, connector 1 may be decoupled from mating connector 100 by simply pulling outer shell 5 in the direction opposite mating direction M or even by excessive vibration. Thus, the connector system is unlocked in FIG. 3B . CPA 19 is in an unlocked position relative to outer shell 5. To lock connector system 200, CPA 19 is moved from the unlocked position deeper into pocket 21 along mating direction M, for example by manually pressing actuation grip 25, until locking nose (not visible) can lock with or behind locking notch 27 to establish a form fit. Once the form fit is established, CPA 19 is in the locked position. FIG. 3C shows the connector of FIG. 1 in a mated and locked state, with CPA 19 in the locked position.

[0072] The connector 1 and connector system 200 described herein embody the present invention by providing an improved connector mating solution at a reduced size. The greater compactness of the disclosed inventive mating solution makes it particularly suitable for space-constrained or tight environments. [Explanation of symbols]

[0073] 1 connector 3 Inner shell 5 outer shell 7 Gear Wheel 9 Terminal Cavity 11 Edge of inner shell 13 Edge of outer shell 15 Inner surface of outer shell 17 Outer surface of inner shell 19 CPA 21 Outer shell pocket 23 First distal end of CPA 25 CPA operating grip 27 Lock notch formed in inner shell 29 First straight gear 31 First straight gear tooth 33 Hinge shaft 35 Inner shell recess 37 Distal edge of connector 39 Center through hole 41 First set of external gear teeth 43 First set of external gear teeth 45 Second set of external gear teeth 47 Second set of external gear teeth 49 First gear tooth flap 51 Second gear tooth flap 53 Depression 55a, 55b, 55c Cutout radial area 57 Wheel spoke elements 57a Radial step shape 59 Straight process 61 Straight Cam 63 Back of the recess 65 Inner shell protrusion 100 Mating connector 101 Mating connector housing element 103 Contact part of mating connector 105 Second straight gear 105a Tip of second straight gear 107 Outer surface of housing element 109 Second straight gear tooth 200 Connector System A. Area visible in Figure 1 C1 First semicircle C2 Second semicircle D1: Extension range along the mating direction of the outer shell D2: Extension range along the fitting direction of the inner shell D3 distance to bond state H hinge axis L Median line of cross section M Mating direction P1 First circumferential surface of gear wheel P2 Second circumferential surface of gear wheel R1 First pitch circle radius R2 Second pitch radius T Tooth arc thickness W tooth face width X, Y, Z Cartesian Direction α1 First angular direction region α2 Second angular direction region α3 Angular direction region between the first angular direction region and the second angular direction region β Tooth pitch angle

Claims

1. A connector configured to mate with a mating connector (100) in a mating direction (M). The connector (1) comprises an inner shell (3), an outer shell (5) and a gear wheel (7), The outer shell (5) at least partially surrounds the inner shell (3). , configured to move in the fitting direction (M) relative to the inner shell (3), The outer shell (5) has an inner surface (15) of the outer shell (5) in the fitting direction ( M), The gear wheel (7) and the first linear gear (29) are in a rack and pinion configuration. The gear wheel (7) is arranged on a hinge axis (H) perpendicular to the mating direction (M). The connector is hinged to the inner shell (3) so as to be rotatable relative to the hand, The gear wheel (7) is connected to the first linear gear in the rack and pinion configuration. a first set (41) of external gear teeth (43) configured to engage with the gear (29); , configured to engage with the second linear gear (105) of the mating connector (100). and a second set (45) of external gear teeth (47) having the external gear teeth (43). The first set (41) and the second set (45) of external gear teeth (47) are the same It is arranged in a plane (L), the gear wheel (7) comprises a first flap (49) in an angular region (α1) of the gear wheel (7) corresponding to the first set (41) and a second flap (51) in an angular region (α2) of the gear wheel (7) opposite to the first flap (49) and corresponding to the second set (45), connector.

2. The first pitch radius (R1) of the first set (41) of external gear teeth (43) is The second pitch radius (R2) of the second set (45) of external gear teeth (47) is different from 2. The connector according to claim 1 .

3. The first pitch radius (R1) is greater than the second pitch radius (R2); The connector according to claim 2 .

4. The first pitch circle radius (R1) is 1.2 to 1.2 times smaller than the second pitch circle radius (R2). 5 times larger. The connector of claim 2.

5. The first set (41) of external gear teeth (43) and the second set (45) of external gear teeth (44) The gear external teeth (47) have the same pitch angle (β) and / or arc tooth thickness (T) and / or 2. The connector of claim 1, wherein the connector has a tooth width (W).

6. The first set (41) of external gear teeth (43) and the second set (45) of external gear teeth (44) The connector of claim 1 , wherein the external gear teeth (47) have the same dimensions.

7. The gear wheel (7) is provided with at least one cut-out area (55c), At least one cutout area (55c) is provided in the first set (41) of the external gear teeth (43). ) and the gear wheel between the second set (45) of external gear teeth (47).

2. A connector according to claim 1, which is included in the angular direction area (α3) of the coil (7).

8. said at least one cutout area (55c) is a completely hollowed area. Item 8. The connector according to item 7.

9. The inner shell (3) is a housing element (10) of the mating connector (100). The inner shell (3) is configured to fit into the inner shell (1) along the fitting direction (M). The recess (35) extends along the second outer gear tooth (47), so that the set (45) can engage with the second linear gear (105). When the inner shell (3) is fitted to the housing element (101), The second linear gear (105) of the actuator (100) is configured to receive the second linear gear (105).

2. The connector according to claim 1.

10. The outer shell (5) is configured to move from a first position where the connector (1) is uncoupled to a second position where the connector (1) is uncoupled. The inner shell (3) is moved to a second position where it is coupled to the mating connector (100). configured to move relative to The inner shell (3) is the inner shell to which the gear wheel (7) is hinged. a protrusion (65) formed on the outer surface (17) of the inner shell (3); The gear wheel (7) is aligned with the protrusion (65) and is in the forward position in the first position. a recess (33) configured to receive the protrusion (65); The connector according to claim 1 .

11. The ratio of the first pitch radius (R1) to the second pitch radius (R2) is The ratio of the number of the external gear teeth (47) in the first set (45) to the number of the external gear teeth (47) in the second set (45) 3. The connector of claim 2, wherein the ratio of the number of external gear teeth (43) in the number of external gear teeth (41) corresponds to the ratio of the number of external gear teeth (43) in the number of external gear teeth (41).

12. Either the inner shell (3) or the outer shell (5) is The inner shell (3) and the linear cam (61) extending along the mating direction (M) are provided. Either of the outer shells (5) has a corresponding cam for the linear cam (61). The inner shell (3) is provided with a protrusion (59) configured as a follower. The movement of the outer shell (5) is caused by the protrusion (59) along the linear cam (61). The connector of claim 1 , further comprising:

13. The connector (1) according to any one of claims 1 to 12 and a mating connector (1 00), a connector system comprising: The mating connector (1) is configured to fit into the inner shell (3). a housing element (101) The housing element (101) has an outer surface (107) of the housing element (101). The second linear gear (105) is formed on the front When the connector (1) and the mating connector (100) are coupled, the second set configured to engage with the Connector system.

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