Indirect rearview system with indexing geometry

Abstract

This invention relates to an indirect rearview system for automobiles, comprising a carrier element for fixing at least one reflective element, wherein the carrier element has a coupling region for positionally fixing / mounting on an adjustment element connectable to a vehicle, wherein the coupling region contacts a mating contact region of the adjustment element, wherein anti-torsion members are provided on the carrier element and on the adjustment element, wherein the anti-torsion members form a indexing geometry that, in a first operating state, allows the carrier element to be adjusted relative to the adjustment element about two rotation axes transverse to each other, and in at least one second operating state allows the carrier element to undergo a fundamental positional change relative to the adjustment element about a third rotation axis transverse to the other two rotation axes.

Description

Technical Field

[0001] This invention relates to an indirect rearview system for automobiles, such as commercial vehicles, agricultural / construction machinery like tractors, or trucks, buses, and / or transport vehicles, wherein the indirect rearview system has a carrier element for fixing at least one reflective element, such as a mirrored glass, wherein the carrier element forms a coupling region for positionally fixing / mounting on an adjustment element that can be connected to or connected to a vehicle, wherein the coupling region contacts a mating contact region of the adjustment element, wherein anti-torsional members that engage with each other, for example according to the tenon and mortise principle, are also provided on the carrier element and the adjustment element. Background Technology

[0002] Different adjustment units are known from the prior art. German patent DE 101 63 318 C1, traceable to the applicant, protects a joint arrangement, specifically for a rearview mirror with an adjustable mirror, for arranging two components at an angle to each other. This arrangement includes a first joint member comprising a ball-and-socket joint and a second joint member comprising a substantially truncated spherical protrusion fitted into the ball-and-socket joint, a sliding member, and a connecting device for establishing a clamping connection between the first joint member, the sliding member, and the second joint member. The ball-and-socket joint, the sliding member, and the protrusion each have a convex structure and a complementary concave structure on their respective sides, which define first and second axes of rotation between the sliding member, the ball-and-socket joint, and the protrusion. It has proven particularly advantageous that the concave structure has a greater curvature than the convex structure, at least in the unloaded state.

[0003] European Patent EP 3 335 938 B1 also traces back to the applicant. In this patent, a spherical joint device for adjustingably arranging first and second joint members around a fulcrum is protected. The patented spherical joint device has a spherical element on the first joint member and a first radius of curvature including a first center point, the outer side of which is part of the sphere. A locking device is also provided on the second joint member, which contacts the spherical element via a first contact surface. The device also has a concave spherical crown-shaped receiving portion disposed within the spherical element on either the first or second joint member, this receiving portion having a second radius of curvature including a second center point. The second or first joint member has a concave spherical crown. The second or first joint member has a convex spherical crown, this crown being supported in the spherical crown-shaped receiving portion via a second contact surface. In this case, the first radius of curvature is greater than the second radius of curvature. The insertion device connects the spherical element and the two joint members across each other in a button-operated manner. In the earlier patent, the spherical element was specifically protected as being constructed in segments with a spherical ring shape, and the spherical element having multiple spherical ring segments distributed over its circumference.

[0004] Other prior art is known from JP 2018-154287 A and US 5 755 526 A.

[0005] JP 2018-154287 A discloses a side mirror comprising a rod portion having a spherical section at its top; a housing having a recessed spherical surface section on its inherent inner side in a connecting section, the surface section being fixed thereon by means of a mirror body, and the spherical section being fitted into the surface section; a retaining plate having a recessed spherical surface section that mates with the recessed spherical surface section, the retaining plate being arranged opposite to the connecting section to surround the spherical section located between the two recessed spherical surface sections, and the spherical surface section vibratingly retaining the spherical section in the connecting section; and a vibration range adjustment plate being manually and rotatably held between a housing-side support groove constructed in the connecting section and a retaining plate-side support groove constructed in the retaining plate, and adjusting the vibration range of the housing from an unrestricted position to a maximum restricted position.

[0006] US 5,755,526 A discloses a ball joint comprising a socket having a cavity. A ball head bolt includes a spherical end. The spherical end is movable relative to the socket in a first direction into the cavity within the socket. The socket has a first section that engages with the spherical end to prevent rotation of the spherical end about a first axis as it is moved into the cavity. A resilient support deflects as the ball head is moved into the cavity. When the spherical end is in the cavity, this support extends to rotate the spherical end into an operating position within the cavity. The socket has a second section that engages with the ball head to prevent removal of the ball head from the cavity when it is in the operating position. Engagement of the support with a support opening in the socket prevents the spherical end from rotating out of the operating position. Summary of the Invention

[0007] The purpose of this invention is to improve or preferably eliminate the known disadvantages of the prior art.

[0008] The solution of the present invention to achieve the above-mentioned objective lies in that the anti-torsion member forms a indexing geometry, which, in a first operating state, allows the load-bearing element to be adjusted / pivoted relative to the adjusting element about two rotation axes transverse to each other, preferably orthogonal to each other, and in a second operating state allows the load-bearing element to undergo a basic position change / adjustment / pivoting relative to the adjusting element about a third rotation axis transverse to the other two rotation axes, preferably orthogonal to the other two rotation axes. It should be noted that in all operating states, including at least the second operating state, "normal" adjustment can still be made about the vertical axis and the first horizontal axis, precisely for left / right and up / down adjustment of the mirror.

[0009] Anti-torsion components refer to components that, in at least one particular operating state, particularly in the first operating state, prevent the load-bearing element from rotating relative to the rotating element about a particular axis of rotation, while still allowing rotation / pivot about two other axes orthogonal to this axis of rotation.

[0010] If there is an over-torque exceeding the predetermined limit torque, the element can leave the first basic position and occupy the second basic position after the sliding movement of the bearing element relative to the adjusting element. Engagement is preferably performed at this position, for example, as a latching action.

[0011] In these two basic positions, only "normal" adjustments can be made around the vertical axis and one of the two horizontal axes to allow for left / right and up / down adjustments of the mirror.

[0012] In more than two basic positions, these anti-torsional elements prevent pivoting about another axis, i.e., prevent pivoting about a second horizontal axis orthogonal to the vertical axis and the first horizontal axis.

[0013] The sheer number of geometrically necessary variations in rearview mirror systems installed on many different vehicles indicates the existence of different connection realities. This may, for example, mean that the load-bearing structure must be connected horizontally (on the left / right side) to the mirror head, while in other vehicles, a vertical connection (on the top / bottom side) is preferred. This results in multiple variations that must be provided. This can be easily achieved by the present invention. In particular, an indirect vision system for vehicles is provided, which has fewer geometric variations and achieves multiple connections with various vehicles or vehicle variations. While spherical adjustment is typically used, which prevents the mirror head from rotating about its (usually approximately horizontal) spherical central axis during adjustment (normal adjustment of the driver's field of vision), a solution based on requirements is proposed. The mortise and tenon connection can also be designed in different geometries, such as trapezoidal or wave-shaped.

[0014] In other words, the present invention relates to an indirect vision system for a vehicle, comprising at least one reflective element for indirect vision, at least one carrier element, and at least one adjusting element, wherein the carrier element houses the reflective element, and wherein the carrier element and the adjusting element can be deflected relative to each other via a fulcrum through a spherical contact area. A key feature is that different operating positions between the adjusting element and the carrier element can be predefined radially around the central axis of the sphere by means of a mortise and tenon joint, for example. The operating position can still be (freely) selected after the mirror head is installed because this mortise and tenon geometry is implemented in a flexible manner.

[0015] Advantageous implementation methods will now be described in detail.

[0016] Advantageously, for example, the load-bearing element and the adjusting element are coordinated in some way in terms of their geometry, material thickness, and material properties so as to release / force the transition from the first operating state to the second operating state when an over-torque greater than a predetermined limit torque exists. That is, to achieve at least one second operating position, an over-torque greater than the defined torque required to keep the load-bearing element stable in the indexing geometry is needed.

[0017] In this case, it is advantageous that the adjusting element has a spherical connecting region forming a mating contact area. This allows for easy adjustment in different directions (e.g., around three rotation axes).

[0018] In this case, it is particularly advantageous that the spherical connecting region has a truncated spherical segment.

[0019] Advantageously, at least one first operating position is rotated, for example, by 90°, 45°, or 30° via the central axis of the sphere (horizontally / vertically / diagonally) to reach at least one second operating position. This allows for the connection of load-bearing structures that are oriented almost horizontally or vertically. For example, horizontal or vertical pipe fittings can be simply connected. Offsets of the almost horizontal, vertical, or diagonal load-bearing structures can then be achieved. Any other angle can also be achieved.

[0020] If the contact area forms a shell that surrounds / encloses the spherical connection area, the button-like fixing principle can be achieved in a simple way. This facilitates the installation process and saves time.

[0021] Regarding the over-torque, it is also advantageous that the over-torque is preferably at least about 7.5%, about 10%, or about 25% higher than the defined torque used to keep the load-bearing element stable. This allows for collision protection through the damping and flexibility of the indexing geometry. Therefore, this over-torque is greater than the predefined limit torque. When the limit torque is exceeded, for example, the snap-fit ​​connection is released. After adjustment is complete, it self-holds itself back into the indexing geometry.

[0022] Also advantageous is that the indexing geometry is implemented in the form of a tenon-and-groove connection.

[0023] In this case, a demand-based solution can be achieved if the groove is integrated into the load-bearing element and the spring is integrated into the adjusting element, or vice versa.

[0024] It is also advantageous that the indexing geometry is implemented in a flexible manner or that at least one of the two components providing the indexing geometry is implemented in a flexible manner.

[0025] If a flexible implementation scheme is achieved by utilizing gaps in the spherical contact area, it offers advantages both during continuous operation and during installation.

[0026] Finally, the present invention also relates to a design scheme for an indirect (rear) vision system in the form of a mirror head.

[0027] The indirect (rear) vision system may in particular be a head adjuster or a glass adjuster.

[0028] An advantageous implementation is further characterized in that the bearing element and the adjusting element are specifically designed in such a way that the reset characteristics and elastic modulus of the two components are coordinated in a certain way with the contours of the indexing geometry components that engage with each other, so as to force at least a second operating state in the event of over-torque. In the presence of over-torque (greater than a predefined limit torque), the system departs from the previously occupied basic position and moves to a second basic position. Locking is then performed again at this position. The force required for automatic locking or latching can be provided by the reset force of at least one of the two components made of elastic material forming the indexing geometry.

[0029] In particular, it has been proven advantageous to design the first indexing geometry as a groove / slot / dent, for example, in the form of a mortise and tenon structure, and to design the second indexing geometry as a protrusion / rib / raise, for example, in the form of a tenon in the form of a mortise and tenon structure.

[0030] In terms of the improved design, it is advantageous that the groove / slot / dent is provided on the support element, particularly on the inner side of the support element facing the adjustment element, and the protrusion / rib / bulge is provided on the adjustment element, particularly on the outer side of the adjustment element facing the support element, and vice versa.

[0031] To also provide overload protection and allow downward folding in emergency situations, it is advantageous that the limiting torque is approximately 10%, 20%, 30%, or particularly preferably 33% greater than the (normal) torque required to keep the load-bearing element stable relative to the adjusting element in the first operating state. Here, it is advantageous to specifically align / coordinate the internal geometry, for example, the grooves / slots / dents.

[0032] In this case, precise adjustment can be achieved when the protruding joint fits seamlessly into or is installed within the groove / recess. However, a gap of a few tenths of a millimeter is acceptable for near-zero or almost zero gap. These factors must be taken into account, especially in the context of manufacturing tolerances and component deformation.

[0033] An advantageous embodiment is further characterized in that the protrusion has a chamfered side in a cross-section orthogonal to the longitudinal axis of the groove / ditch / recess, this chamfered side being profiled for linear contact with the material forming the groove / ditch / recess. This chamfered side and the elastic indexing geometry generate or predetermine a limiting torque. The chamfer must be overcome when leaving the first basic position. The ratio of the chamfer to the clamping force (predetermined by, for example, the resisting torque of the tongue) determines this limiting torque.

[0034] In this regard, it is particularly preferred that the protrusion has a tapered, truncated conical, truncated spherical, or spherical / elliptical profile, at least in the effective region, i.e., in the region where an angle is required to move away from the basic position and for moving away from this basic position. In this case, adjustment can be smoothly made in as many spatial directions as possible. This effective region can only exist within a specific angular range of the protrusion, and only then can the aforementioned angle be present there. This angle may not be present in other angular ranges. Where there is no angle, it is not an effective region. In other words, at least in the angular range where adjustment and "jumping out" are forced, there is an angle with an "effective profile". However, for symmetry and manufacturing reasons, this angle may also be set in angular ranges where there is no effective region.

[0035] Advantageously, the depth of the groove / trench / dent is between approximately 10% and approximately 45% of the thickness of the coupling region.

[0036] It has proven advantageous that the indexing geometry consists of two components, at least one of which is constructed in a flexible manner.

[0037] It is also advantageous that the coupling region is located, for example, approximately near the center / center point of the carrier element and is adapted to contact the spherical connection region of the adjustment element, for example, by applying pressure (such as in a manner to achieve dynamic coupling and / or form fit), in the form of a button structure.

[0038] Also advantageously, the coupling region has a first contact region and a second contact region offset from it axially, wherein the axial direction is defined by the insertion direction of the adjusting element into the bearing element or preferably by a horizontal axis passing through the fulcrum, the bearing element being pivotable about the fulcrum.

[0039] If the hypothetical separation surface extends planarly through the transition region from the body of the supporting element to the coupling region, other configurations can be used. This separation surface can be flat, and thus can be constructed as a separation plane. This separation surface extends on both sides of the fulcrum through the transition region from the body of the supporting element to the coupling region of this supporting element. Different spatial configurations of this separation surface can be used. For example, an open space design can be used. This separation surface can in particular be flat, i.e., planar, and subsequently form a separation plane in this particular case.

[0040] One of these configurations may be implemented, for example, when the first contact area extends along the hypothetical separation surface and the second contact area extends along the hypothetical separation surface.

[0041] Furthermore, advantageously, the first contact area is constructed as an internal contact area within the space defined by the carrier element and the reflective element, while the second contact area is constructed as an external contact area. This divides the force flow in the transition region from the body of the carrier element to the coupling region of the carrier element along two different, preferably opposite, directions. The overall force flow is distributed as uniformly as possible, thereby preventing breakage of the carrier element and better holding the carrier element on the spherical connection area of ​​the adjusting element.

[0042] Because the first contact area is located within the space defined by the load-bearing element and the reflective element, this contact area is also unaffected by dust and contamination, thus enabling long-term, reliable, and low-friction use and ensuring adjustment even under challenging frame conditions.

[0043] If both the first and second contact areas have truncated spherical inner contour segments, it is particularly effective to adapt one or both contact areas to the spherical connection area to ensure good adjustability.

[0044] An advantageous implementation is further characterized in that the inner side of the coupling region (of the load-bearing element) and the outer side of the connecting region (of the adjusting element) are matched to each other in a certain way so as to define a fulcrum by the two components, around which the load-bearing element can deflect relative to the adjusting element. In this case, when using the rearview system, the user can easily adjust the required angular position of the two components.

[0045] Advantageously, the connection region has a truncated spherical mating contact area. This simplifies deflection / pivot.

[0046] Furthermore, it is advantageous that the mating contact area is adapted to the contact area that comes into contact with the mating contact area, particularly in terms of its contour. This allows, for example, the integration of partitions that deviate from spherical geometry, or the use of elliptical partitions.

[0047] If the mating contact areas are connected by several flattening areas or one flattening area, it facilitates installation, facilitates unloading of the spring element, and avoids over-determination on the support surface.

[0048] For mass production purposes, it has proven advantageous that the load-bearing element is constructed as a rear wall and / or the adjusting element is constructed as a (pivot) pin preferably made of a plastic such as polyamide, for example as an integral / one-piece single material component.

[0049] Advantageously, the adjustment element is fixed to the support element, for example, by form fit and / or dynamic coupling.

[0050] If the adjusting element has a receiving part for connecting and fixing to a bracket / telescopic rod bracket, rod or (telescopic) tube on the vehicle, or is constructed accordingly, then it is ensured that the two components can fit together particularly well.

[0051] Furthermore, it has been proven advantageous that the receiving portion is constructed as a blind hole with a stepped bottom to achieve torsional resistance.

[0052] If the adjusting element has an indirect or direct connection area for the vehicle, the installation scheme can be designed in a variety of ways, such as having a blind hole.

[0053] If the two contact areas together form a truncated spherical shell that connects to the main body in the transition area, the weight can be optimized.

[0054] The compactness of the system is advantageous if the body encounters the housing in the transition region at an angle α of 15° to 125°+ / -5°, preferably 90°+ / -2.5°, wherein the angle α spans an imaginary straight line passing through the transition region from the body to the coupling region and an imaginary straight line extending axially through the (spherical) center point and / or fulcrum of the connecting region.

[0055] If the main body is pre-set with an imaginary azimuth line tangent to the theoretical sphere surrounding the fulcrum in the direction of the fulcrum, a particularly good force distribution can be achieved in the direction of the center of the connecting area. The diameter of this theoretical sphere is 50mm, 60mm or 70mm.

[0056] It has also proven advantageous that the glass element is attached to the carrier element, for example by means of form fit and / or dynamic coupling, particularly by means of a clip solution, and that the glass element is constructed as mirrored glass.

[0057] An advantageous embodiment is further characterized in that, in the installed state, an elastic force is applied to at least one of the two contact areas, preferably the first contact area, or both contact areas, which compresses the coupling area in at least each contact area toward the interior of the coupling area, preferably toward the fulcrum. This simplifies the self-fixation after adjustment, thereby achieving variability in the good reproduction of the driver's rearward visibility range.

[0058] Advantageously, the elastic force is provided by a spring element (e.g., a ring or clip). The spring element may have one or more coils.

[0059] The spring force can be adjusted specifically using this independent spring element. It has also proven advantageous that the ring has a closed or open (e.g., slit) cross-section. This improves installation, particularly in the second case, and enhances fatigue strength / long-term load capacity, particularly in the first case.

[0060] In order to ensure a longer service life without changing the technical framework conditions, it is advantageous that the spring element is made / constructed from a metal building material, such as iron alloy, for example, in the form of spring steel.

[0061] To ensure a simple, modular structure, it is advantageous to construct the spring element as a compression spring, which rests against the outside of the first or second contact area. This also facilitates subsequent applications.

[0062] To connect individual components together, and especially to prevent these components from being lost, it is advantageous to construct, for example, a recess, groove, or slot on the outer side of the (corresponding) contact area, in which the spring element rests / is / is arranged in the installed state.

[0063] To keep the sliding area between the carrier element and the adjusting element permanently clean / uncontaminated, it is advantageous to achieve a sealing function by means of the carrier element and / or the adjusting element, for example by a sealing lip formed on one or both components, between one of the contact areas and its corresponding mating contact area, preferably between the first contact area and its corresponding mating contact area, and / or by embedding / intermediately connecting an additional sealing element between the carrier element and the adjusting element.

[0064] In terms of installation, it is advantageous that the coupling region is constructed in a flexible manner, either entirely or at least segmented / partially.

[0065] It is advantageous to agree that the geometrical changes that cause elasticity are provided (primarily) only in the first contact area and / or (secondarily) only in the second contact area, such as thinning, slits, gaps, grooves, waves and / or similar designs.

[0066] In order to enable different operating positions, it is advantageous that the coupling region and the connection region are adapted to form a graduated geometry, by means of which certain predefined relative positions between the bearing element and the adjusting element can be assumed.

[0067] In this case, it is advantageous that the indexing geometry is formed by mortise and tenon engagement.

[0068] Here, it has proven advantageous that the coupling region has at least one or more grooves / slots / slots on its inner side, and wherein a protrusion on the outer side of the adjusting element engages in at least one or more of the grooves / slots / slots (each), or alternatively / supplementarily, the adjusting element has at least one or more grooves / slots / slots on its outer side, and wherein a protrusion on the inner side of the coupling region of the bearing element engages in at least one or more of the grooves / slots / slots (each).

[0069] If the groove / channel / slot and / or the protrusion has a V-shaped, U-shaped, canopy-shaped or polygonal profile in cross-section and / or both are formed in a way that fits together (almost) without gaps, the adjusting element can be adapted to the carrying element without wobbling, and vice versa.

[0070] In order to enable stepless adjustment, it is advantageous to embed / insert the device in a manner that allows it to move / slide (continuously / discontinuously) within the groove / channel / slot.

[0071] Furthermore, it has also proven advantageous that, from the perspective of the fulcrum, grooves / slots / grooves are provided on the opposite outer sides of the adjusting element, two of which, in at least one section, are respectively filled with a protrusion of the adjusting element, and at least two or an integer multiple of the grooves / slots / grooves remain without protrusions.

[0072] If these grooves / slots / grooves are evenly distributed on the inner periphery of the coupling area at intervals of 90°, 45°, 22.5°, 12.25° or 6.125°, they can be adjusted as needed.

[0073] The present invention ultimately relates to a technical solution in which a mirror head is constructed and / or includes a head adjuster or a glass adjuster.

[0074] If the internal and / or external contact areas are radially closed and preferably have flexible partitions, simple installation can be carried out while eliminating the possibility of contamination or providing protection against dirt.

[0075] The invention also relates to a method of mounting a carrier element of an indirect rearview system of the type according to the invention onto an adjusting element, wherein the carrier element is moved from the direction of the reflective element toward the direction of the adjusting element, for example by constructing a mating contact area thereon. This achieves a snap-fit ​​mechanism.

[0076] One improvement is that the coupling region forming the second contact area and / or the first contact area is first expanded when pushed onto the adjusting element, and then elastically rebounds.

[0077] In this case, it is advantageous to clamp the coupling region onto the spherical protrusion / spherical connection region of the adjusting element.

[0078] In other words, the present invention relates to an indirect vision system for a vehicle, wherein the angle α between the central axis of a horizontal sphere and the side of the center point of the sphere to the point of impact on the rear wall in the contact area is a minimum of 15° and a maximum of 125°.

[0079] An improvement can also be expressed in words, specifically in that the adjusting element has a connection area for the vehicle and is integrally formed in the working surface for the load-bearing element.

[0080] Furthermore, the orientation of the rear wall within the contact area can be designed in such a way that the rear wall passes through the theoretical sphere with a diameter of 60 mm in the theoretical extension toward the center point of the sphere.

[0081] Also considered advantageous is that the adjusting element is mounted relative to the supporting element from the inside out, from the direction of the reflective element, with the outer contact area and the inner contact area radially closed, or the outer contact area radially closed and the inner contact area having elastic partitions. Gap, void, groove, and wave-like features are provided here. This simplifies the segmentation or implementation of the button principle. In this case, these gaps cause a spring-like effect in the contact area.

[0082] In other words, the invention also relates to mounting the adjusting element relative to the carrier element from the inside out in the direction of the reflecting element, wherein the outer contact area and the inner contact area of ​​the carrier element are radially closed and the adjusting element has elastic partitions.

[0083] If pressure is applied to the contact area of ​​the adjusting element at the external or internal contact area of ​​the bearing element by means of a spring element, the frictional force is increased by means of the spring, thereby generating a greater adjusting force for adjustment.

[0084] Advantageously, pressure is applied to the contact area of ​​the bearing element at the outer or inner contact area of ​​the adjusting element by means of a spring element.

[0085] Advantageously, the spring element is a metal spring clip or an open or closed metal ring spring having one or more coils.

[0086] It is also advantageous to integrate the sealing function in the outer contact areas of the carrier element and the outer contact areas of the adjusting element. A molded sealing lip on the carrier element and an additional molded sealing lip made of a second material can also be used. An additional sealing element can also be installed.

[0087] If the indirect vision system is mounted directly or indirectly on the vehicle using a tube or the adjusting element, and the adjusting element is implemented in an integrated or composite manner to secure the tube, other alternative solutions can be implemented. Specifically, the tube can be mounted on the vehicle for direct mounting, or additional retaining elements, such as telescopic rod brackets, can be used for indirect mounting.

[0088] Advantageously, the fitting is clearly defined, positioned, and secured within the adjusting element through a form-fit, i.e., a corresponding geometry. This has the advantage of maintaining the desired field of view through the precise positioning of the indirect vision system, for example, to meet customer requirements or maintain the legal field of view required by standards such as UN / ECE-R46, ISO 5721-2, or ISO 5006. Furthermore, the mirror head with the adjusting element is mounted in a loss-proof manner, preventing it from "falling off" if the power coupling is lost or weakened.

[0089] It is also advantageous that the indirect vision system is directly mounted on the vehicle via the adjustment element, for example, via an adjustment element mounted on the vehicle, and the adjustment element is implemented in an integrated or composite manner.

[0090] Also advantageously, different operating positions can be radially adjusted about the horizontal spherical central axis between the adjusting element and the supporting element via a mortise-and-tenon type indexing geometry. The operating position can still be selected after the mirror head is installed because this indexing geometry is implemented in a flexible manner. This also allows for impact protection through the damping and elasticity of the indexing geometry.

[0091] As described above, it is advantageous that the indirect vision system is a mirror head and / or the indirect vision system is a head adjuster or a glass adjuster.

[0092] The solution according to the invention has many advantages. It achieves optimized force flow from the load-bearing element to the adjusting element because force transmission occurs between the inner and outer contact areas, thus better transferring force from the load-bearing element to the adjusting element. The number of components is also reduced because functional and geometric designs are integrated. The contact areas of the load-bearing element and the adjusting element are nested together, eliminating the need for additional sliding or engaging elements. Installation is simplified due to the fewer components required, thus reducing costs. In one embodiment, the adjusting mechanism is simply "clamped" together, eliminating the need for engaging elements such as screws or locking bolts.

[0093] The indexing geometry, in the form of a tenon-and-groove combination, allows for adjustment when a larger torque is applied, such as switching from a longitudinal mounting format to a lateral mounting format.

[0094] Another positive aspect involves cable guidance, which enables connections to electrical modules such as heating foil, for example, on the back of a mirror (i.e., within the space defined by the glass element and the supporting element), blind spots, and / or parking distance systems. In this case, such cables / power lines can be guided through the spherical connection area of ​​the regulating element or inside the sphere formed by the grooves of the regulating element.

[0095] Furthermore, this solution protects these components even in the event of a collision, as torsion is achieved through torque used to stabilize the load-bearing elements. Variations can also be manufactured after the mirror head is installed, for example, with the load-bearing structure tilted horizontally or vertically towards the vehicle. This results in a cost advantage.

[0096] The geometrically designed mirror heads can be used on both the left and right sides of a vehicle because the connector can rotate 180° between two operating positions. This allows for variations that reduce production, logistics, and warehousing costs at the manufacturer level and during the sales process (particularly for retailers and automakers). Attached Figure Description

[0097] The present invention will now be described in detail with reference to the accompanying drawings and several embodiments. Wherein:

[0098] Figure 1 An isometric view of an indirect rearview system for an automobile (i.e., a truck, bus, or transport vehicle) according to a first embodiment of the present invention is shown.

[0099] Figure 2 The rear-view system of the first embodiment is shown along Figure 1 The longitudinal section view of line II shown.

[0100] Figure 3 It shows Figure 1 and Figure 2 The rear view of the rearview system shown is shown.

[0101] Figure 4 It shows Figure 2 An enlarged view of region IV shown.

[0102] Figure 5 It shows Figure 4 The area shown is similar to Figure 3 The rear view shown in the diagram is as follows.

[0103] Figure 6 With similar Figure 5 The second embodiment is illustrated in the diagram.

[0104] Figure 7 The diagram illustrates the connection between the adjusting element included in both embodiments and the vertically extending pipe in the connection area.

[0105] Figure 8 Another embodiment of the connection with a pipe fitting oriented horizontally in the connection area is shown, and

[0106] Figures 9 to 23 Different views and cross-sectional / detailed views of different implementations are shown.

[0107] Wherein: 1: Indirect rearview system; 2: Bearing element; 3: Reflective element; 4: Upper mirror glass; 5: Lower mirror glass; 6: Adjustment element; 7: Spherical connection area; 8: Matching contact area; 9: First contact area; 10: Second contact area; 11: Coupling area; 12: Transition area; 13: Main body; 14: Recess; 15: Fusel point; 16: Flat component; 17: Gap; 18: Indexing geometry; 19: Anti-torsion component; 20: Groove; 21: Protrusion / rib / ridge; 22: Connection system; 23: Tubing; 24: Imaginary separation surface; 25: First rotation axis; 26: Second rotation axis; 27: Third rotation axis Detailed Implementation

[0108] These drawings are purely illustrative and intended only to understand the invention. The same elements are represented by the same reference numerals. Features of the various embodiments are interchangeable.

[0109] exist Figure 1 In the indirect rearview system, reference numeral 1 is provided. This indirect solid system has a supporting element 2 for fixing at least one reflective element 3. There are two reflective elements 3, namely an upper mirror glass 4 and a lower mirror glass 5.

[0110] exist Figure 4 In the figure, the first rotating shaft is equipped with reference numeral 25, the second rotating shaft is equipped with reference numeral 26, and the third rotating shaft is equipped with reference numeral 27.

[0111] exist Figure 2 As can be seen, the adjusting element 6 is centrally located within the supporting element 2. The adjusting element 6 has a spherical connecting region 7. The spherical connecting region 7 has mating contact regions 8, which correspond to the first contact region 9 and the second contact region 10 of the coupling region 11. The coupling region 11 is located at the center / center of the transition region 12 of the supporting element 2. The transition region 12 is the area where the main body 13 transitions into the coupling region 11.

[0112] A recess 14 is provided in the first contact area 9, into which a spring element can be inserted. A fulcrum 15 is provided, about which the bearing element 2 can rotate. The connecting area 7 has at least one flat member 16 located between the axially separated mating contact areas 8. Figure 3 As shown, both the coupling region 11 and the connecting region 7 can be constructed in a flexible manner, especially with the gap 17.

[0113] According to the indexing geometry 18 of the present invention, Figure 4 The enlarged view shows the indexing geometry 18 providing anti-torsional elements 19. This indexing geometry is specifically composed of components that realize the mortise and tenon principle.

[0114] Imaginary separation surface at Figure 4 The middle part is marked with reference numeral 24.

[0115] The coupling region 11, for example, has a groove / slot / recess 20 in particular, which is a material that does not extend completely through the coupling region 11. It also extends only within a portion of the coupling region 11, but at least from the opening end of the adjusting element 6 toward the reflecting element 3. The indexing geometry 18 also has a protrusion / rib / ridge 21 that extends radially outward from the connecting region 7 toward the coupling region 11. The protrusion / rib / ridge 21 engages in this groove / slot / recess in a manner that is as gapless as possible (ideally even completely gapless).

[0116] from Figure 5 and Figure 6 It can also be clearly seen that two different positions / basic positions of two embodiments or a single embodiment are shown, with the groove / ditch / dent 20 having a polygonal / trapezoidal / parallelogram cross-section. The protrusion / rib / ridge 21 itself has a frustoconical outer contour with an angle of approximately 45°, 30°, 20°, 15°±2.5°.

[0117] Carrying element 2 in Figure 5 The middle is in the first basic position relative to the adjusting element 6, and in Figure 6 The system is in the second basic position. A first operating state exists in both the first and second basic positions. In this case, rotation can still be performed only around two axes orthogonal to each other, namely the vertical axis and the first horizontal axis.

[0118] If excessive torque is applied, the protrusion 21 will jump out of the slot 20 because the tongue of the adjusting element 6 is elastic inward and / or the tongue of the bearing element 2 is elastic outward. This achieves the second operating state.

[0119] During this second operating state, the bearing element 2 is pivoted relative to the adjusting element 6 about another / second horizontal axis. Then, Figure 5 The upper protrusion 21 in the middle completes a 90° rotation and as Figure 6 As shown, it is then inserted into another slot 20. Only then does it occupy the second basic position and re-enter the first operating state.

[0120] The desired over-torque is preset by the slope of the outer contour of the protrusion / rib / ridge 21 and the reset characteristics of the bearing element 3 and / or adjusting element 6 in the region of the indexing geometry 18.

[0121] Therefore, the reset characteristics of the bearing element 2 and the adjusting element 6, as well as the angle of the truncated cone protrusion 21, are coordinated in a certain way to ensure linear contact between the bearing element 2 and the protrusion 21 of the adjusting element 6; wherein this selection is specifically made so that when the over-torque (exceeding the limit torque) is exceeded, the protrusion / rib / ridge 21 can disengage from the groove / slot / dent 20 and the bearing element 2 can move, for example, 30°, 60° or 90° as shown.

[0122] The connection system 22 thus realized is used for Figure 7 and Figure 8 In order to enable connection with the vehicle. The connection system 22 also has a fitting 23.

[0123] Figure 9 and Figure 10 Another embodiment is shown, in which the supporting element 2 is constructed with grooves horizontally and vertically in a closed manner. The adjusting element 6 is constructed with protrusions in an open manner and is particularly elastic or equipped with an optional spring element. This differs from the embodiment shown. Figure 4 In this embodiment, the spring element is integrated into the bearing element 2 from above.

[0124] Figures 11 to 15 Another embodiment is shown, in which the supporting element 2 adopts a shell-like design with a single-sided protrusion. The shell-like adjusting element 6 is provided with horizontal and vertical grooves. A pressure member is provided for absorbing elastic force. A connecting element is provided for pre-tightening the spring and locking all components.

[0125] Figure 16 and Figure 17 Another embodiment is shown, in which the supporting element 2 is closed and (respectively) provided with horizontally and vertically oriented slots. The adjusting element 6 is slit, constructed with protrusions, and in particular, is elastic or provided with an optional spring element. This differs from the embodiment shown. Figure 4 In this implementation, the spring element is arranged in a built-in manner. Unlike... Figure 10 In the embodiment shown, the connector contact area is engaged from above into the carrier element 2 in such a way that it is offset to one side into the edge region of the mating contact area 8.

[0126] Figure 18 and Figure 19 Another embodiment is shown, in which the supporting element 2 is closed, i.e., has a groove (horizontal and vertical). The adjusting element 6 is provided with a protrusion in a slit manner, thus possessing its own elasticity or being equipped with an optional spring element. This differs from the embodiment shown. Figure 4 The object, this spring element, is arranged in a built-in manner. Unlike... Figure 10The object shown is joined from above to the carrier element 2 in such a way that the joint contact area is offset to the edge area of ​​the mating contact area 8 on one side.

[0127] Figure 20 and Figure 21 Another embodiment is shown, in which the supporting element 2 is closed, i.e., has a groove (horizontal and vertical). The adjusting element 6 is provided with a protrusion in a slit manner, thus possessing its own elasticity or being equipped with an optional spring element. This differs from the embodiment shown. Figure 4 The object, this spring element, is arranged in a built-in manner. Unlike... Figure 10 The object shown has its contact area joined to the carrier element 2 from below in a manner that offsets to the edge region of the mating contact area 8 on one side.

[0128] Figure 20 and Figure 21 Another embodiment is shown, in which the supporting element 2 is closed and has a protrusion. The adjusting element 6 is provided with a slot (horizontal and vertical) in a slit manner, and is itself elastic or equipped with an optional spring element. This differs from the embodiment shown. Figure 4 In this implementation, the spring element is integrated into the load-bearing element from above. Unlike... Figures 9 to 21 All embodiments shown have an opposite arrangement of "protrusions and grooves".

Claims

1. An indirect rearview system (1) for an automobile, comprising a carrier element (2) for fixing at least one reflective element (3), wherein the carrier element (2) has a coupling region (11) for positionally mounting on an adjustment element (6) connectable to a vehicle, wherein the coupling region (11) contacts a mating contact region (8) of the adjustment element (6), wherein anti-torsion members (19) engaging with each other are provided on the carrier element (2) and on the adjustment element (6), characterized in that, The anti-torsion member (19) forms an indexing geometry (18) that allows the load-bearing element (2) to be adjusted relative to the adjusting element (6) about two rotation axes (25, 26) transverse to each other in a first operating state, and allows the load-bearing element (2) to undergo a basic position change relative to the adjusting element (6) about a third rotation axis (27) transverse to the other two rotation axes (25, 26) in at least one second operating state.

2. The indirect rear-view system (1) according to claim 1, characterized in that, The load-bearing element (2) and the adjusting element (6) are coordinated in some way in terms of their geometry, material thickness and material properties so as to release / force the transition from the first operating state to the second operating state when there is an over-torque greater than a predetermined limit torque.

3. The indirect rear-view system (1) according to claim 2, characterized in that, The adjusting element (6) has a spherical connection area (7) that forms the mating contact area (8).

4. The indirect rear-view system (1) according to claim 3, characterized in that, The load-bearing element (2) and the adjusting element (6) are specifically designed in such a way that the reset characteristics and elastic modulus of the load-bearing element (2) and the adjusting element (6) are coordinated in a way with the contours of the indexing geometry members that engage with each other, so as to force at least a second operating state when the over-torque occurs.

5. The indirect rear-view system (1) according to claim 4, characterized in that, The first indexing geometry component is designed as a groove (20), and the second indexing geometry component is designed as a protrusion (21).

6. The indirect rear-view system (1) according to claim 5, characterized in that, The groove (20) is provided on the bearing element (2) and the protrusion (21) is provided on the adjusting element (6), and vice versa.

7. The indirect rear-view system (1) according to claim 6, characterized in that, The limiting torque is at least 10% greater than the torque required to keep the load-bearing element (2) stable relative to the adjusting element (6) in the first operating state.

8. The indirect rear-view system (1) according to claim 7, characterized in that, The protrusion (21) fits into the groove (20) without gap.

9. The indirect rear-view system (1) according to claim 8, characterized in that, The protrusion (21) has a chamfered side in a cross section orthogonal to the longitudinal axis of the groove (20), the chamfered side being profiled to make linear contact with the material forming the groove (20).

10. The indirect rear-view system (1) according to claim 9, characterized in that, The protrusion (21) has a tapered profile, a truncated tapered profile, a truncated spherical profile, or a spherical / elliptical profile at least in the effective area.

11. The indirect rear-view system (1) according to claim 10, characterized in that, The indexing geometry (18) consists of two components, at least one of which is constructed in an elastic manner.

Images