Cylindrical mount for adjustable optical and mechanical components

Abstract

A cylindrical mount (1) for an adjustable optical and mechanical component has a sleeve (2) fixed relative to the mount; three sliding drive elements arranged dispersedly on the cylindrical inner circumferential surface of the sleeve for operative connection with corresponding grooved cams of a cam carrier (5) which is rotatably and axially displaceably mounted in the sleeve (2) and which has a slotted linear guide (6); and a rotating ring (7), which is fixed in the axial direction, is supported on the outer surface of the sleeve and can be actuated from the outside, said rotating ring having at least one transmission element (8) for engaging in a slotted linear guide (6) of the cam carrier (5), the angle (W1-2) between the radii of the first (G1) and second (G2) sliding transmission elements of the three sliding transmission elements (G1, G2, G3) is smaller than the respective angle (W1-3, W2-3) thereof from the third sliding transmission element (G3).

Description

Technical Field

[0001] The invention relates to a cylindrical mount for optical and mechanical components according to the preamble of claim 1, in particular a lens mount for lenses for viewfinder cameras that are adjustable for different object distances, the mount having a distance adjustment ring and a device coupled to the distance adjustment ring for transmitting the adjusted distance to an adjustment lever of a movable optical element of a profile rangefinder arranged on the camera side. Profile rangefinders are also known as hybrid image viewfinders, coincidence viewfinders or, more colloquially, rangefinders. Viewfinder cameras are, for example, cameras of the M system of the applicant, which have been known for decades for their compatibility with lenses of different focal lengths belonging to the M system. Background Art

[0002] In such photographic lenses, it is known that one or more of the imaging lenses are moved along the optical axis in order to image the object to be photographed correspondingly clearly in the image acquisition plane of the camera, and it is also known that a movable optical element built into the rangefinder of the camera is coupled to the focus movement mechanisms of different objectives or lenses via an adjustment lever in the camera.

[0003] A worm screw with or without a linear guide is often used as a displacement mechanism in a lens, which can be actuated from the outside via a distance adjustment ring provided with an internal thread.

[0004] In lenses of normal focal length (such as, for example, 50 mm lenses / objectives for small image formats), a rotation at the distance adjustment ring, which is limited to a rotation angle range of less than 95°, causes, on the one hand, an axial displacement of the worm screw sleeve for focusing and, on the other hand, a rotation of the worm screw sleeve about the system optical axis. The adjustment lever is coupled to the focusing movement mechanism of the lens in this way by abutting against the end side of the worm screw sleeve. In this way, it is achieved that, when the adjustment lever moves 4.5 mm in a coupled manner, a visual focusing is performed in a distance range of 0.7 m to infinity. The distance-dependent adjustment distance difference and the possible nonlinearity between the axial adjustment movement of the optical imaging system required for focusing and the coupled movement of the adjustment lever for the distance meter are compensated, for example, in a supplementary manner by milling a slope (as a linear or nonlinear axial cam, if necessary) on the end face of the worm screw sleeve. The mechanical complexity for this is very high and additionally a great deal of work is required for milling.

[0005] Depending on the lens design and the focal length of the lens, the adjustment distances of the focus movement mechanisms of the optical devices or optical components required for focusing on object distances from infinity to close distances often vary significantly, while due to structural limitations, the adjustment range in rangefinders is mechanically limited ("calibrated") to an object distance from 0.7 m to infinity, since the adjustment distance of the adjustment lever available for this purpose is always 4.5 mm.

[0006] In terms of distance adjustment, the compatibility of the lens and the camera is achieved in that any differences in the adjustment distances of the focus mechanism are converted into the adjustment lever adjustment distance in the rangefinder predetermined by the camera for the distance range from 0.7 m to infinity.

[0007] This conversion must be done with high precision and therefore requires a great deal of additional mechanical effort. Usually, a reduction gear or a speed-increasing gear (Unter-oder) is used with a worm thread and a threaded sleeve having multiple nested barrels. ) to convert the working mode.

[0008] A complex lens mount of this type is known from DE 2 040 227 A1. The lens mount comprises a plurality of imaging lenses which can be moved along the optical axis of the system by means of a distance adjustment ring in order to image the object to be photographed correspondingly clearly in the image acquisition plane. To this end, the distance adjustment ring is connected to an externally threaded tube (as a drive device) which is configured as a worm. An internally threaded tube, which is also configured as a worm, is inserted into the tube and is guided linearly in the lens mount, so that the rotation of the externally threaded tube is converted into a movement of the internally threaded tube along the optical axis of the system. The imaging lens is inserted into the internally threaded tube in a fixed position and therefore participates in this axial movement along the optical axis of the system.

[0009] Furthermore, on the camera side, a cam ring is rotatably inserted into the internally threaded tube, which cam ring is driven by a driving pin connected to the externally threaded tube. For this purpose, the cam ring rests on a shoulder that is machined into the inner wall of the internally threaded tube and is held by a pre-screwed ring that is screwed onto the internally threaded tube. The driving pin is connected to the cam ring through a radial cutout in the internally threaded tube. The cam ring has an axial cam on its end face on the camera side. A push rod that is supported in a swingable manner about an axis perpendicular to the optical axis of the system rests against this axial cam via a roller. The push rod is coupled to an adjustment lever of the rangefinder.

[0010] Thus, when the distance adjustment ring is rotated, the cam ring is displaced axially on the one hand and rotated about the optical axis of the system on the other hand. By carrying out these two movements together, the relatively large axial movement of the threaded tube is converted or reduced into the smaller push rod movement required for the adjustment distance of the adjustment lever in the distance meter. In this way, focal length-dependent adjustment distance differences and nonlinearities between the axial adjustment movement of the optical imaging system and the movement of the adjustment lever for the distance meter linked thereto can be compensated to a limited extent by the inclination of the axial cam.

[0011] For adjusting the adjustment lever and the focusing element, so-called cylindrical threads are also known in lens construction, in which three grooved cams of a cam carrier are arranged in a symmetrically distributed manner on the circumference of a fixed sleeve and rise linearly in the axial direction, and a sliding transmission element engaged in the grooved cam cooperates with a linear guide to convert the rotational movement of the distance adjustment ring into an axial displacement. On the one hand, the maximum rotation angle available for focusing from infinity to close range is limited by the 120° range between the grooved cams or the sliding transmission element, and on the other hand, it is also limited that within this range, a transmission element for the distance adjustment ring engaged in the linear guide of the cam carrier must also be arranged.

[0012] In this way, the adjustment accuracy of the focus is limited, since for relatively large axial displacements of the threaded tube of the focus mechanism, only a rotation angle range of the distance adjustment ring of less than 95° is available. This proves to be particularly disadvantageous both in lenses with large focal lengths, which require large adjustment distances for focusing, and in lenses with large apertures, since in these lenses the depth of field on the image side becomes smaller and in this way it is no longer possible to compensate for focus inaccuracies resulting from operator adjustments.

[0013] It has been shown that a rotation angle of 95° is just sufficient for the focus adjustment accuracy requirements for a 50 mm focal length lens in the range of 0.7 m to infinity. However, modern lens designs enable focus adjustment at object distances less than 0.7 m (e.g. up to 0.45 m). However, for such adjustment, a rotation angle of about 175° is required.

[0014] However, in the known cam carriers, it has proven to be effective to arrange the slotted cams in an axial plane in a manner distributed symmetrically over the circumference, since in this way tilting moments and instabilities are avoided. In this case, the guide rails or the slotted cams have the same axial inclination. In this case, the rotation angle of the distance adjustment ring is also limited by the start and end points of the slotted cams. At a maximum rotation angle of 95°, a small axial displacement can be achieved by a small axial inclination. In this way, there is just enough cylindrical side surface between the end point of one slotted cam and the start point of the adjacent slotted cam to ensure the mechanical stability of the cam carrier.

[0015] If a greater rotation angle is to be achieved in the known 120° arrangement, this can only be achieved if the axial inclination of the guide track is selected to be large enough that the start and end points of adjacent grooved cams have a sufficient axial offset. However, the minimum width of the grooved cams required for a reliable mechanical movement does not allow for small axial displacements, such as the 4.5 mm provided for the adjustment lever of a distance meter.

[0016] EP 2 693 247 A1 discloses a cylindrical mounting with a cam carrier and a curved track with an axial offset, wherein the cam carrier can realize large rotation angles. The curved track extending in an axially offset manner requires a large space requirement and requires a large cylinder side surface. Small axial adjustment distances cannot be realized. In addition, due to the multiple closely spaced notches for the curved track, the material of the cylinder is mechanically weakened and is unstable under loads in the axial direction.

[0017] Other cylindrical mounts for optical components having a cam carrier and a cylindrical curve thread are known, for example, from US 2015 / 0205068 A1 and US Pat. No. 3,951,522. Summary of the invention

[0018] The object of the present invention is to improve existing disadvantages associated with rangefinder cameras in the lens in terms of converting the adjustment distance for the focus element into the adjustment distance of the rangefinder, in particular to improve the adjustment accuracy of the axial positioning of the focus element in the lens when the focus element moves a large distance, and at the same time to ensure the transmission accuracy required for focusing, coupled to the adjustment lever of the camera rangefinder and the preset adjustment distance of the adjustment lever. Another object of the present invention is to achieve focusability at an object distance of less than 0.7 m, i.e. from infinity to 0.4 m, in a lens having a rotation-axial conversion mechanism for operating the adjustment lever of the camera rangefinder.

[0019] This object is achieved by a cylindrical mount for adjustable optical and mechanical components having the features of claim 1 , advantageous embodiments and improvements being the subject matter of the dependent claims.

[0020] In the cylindrical mounting according to the invention, a sleeve is provided which is fixed relative to the mounting and which has three sliding transmission elements arranged in a distributed manner on the cylindrical inner circumference of the sleeve for operative connection with three corresponding slotted cams of a cam carrier rotatably supported in the sleeve. In this case, exactly one slotted cam is associated with each of the three sliding transmission elements. The sliding transmission element has a shape that matches the slotted cam, in particular as a plastic round sleeve. For simple assembly, the sliding transmission element has the shape of a cylindrical tenon with two different outer diameters.

[0021] The correspondingly larger diameter is used for simple insertion into a pocket hole (Bohrsackloch), which is introduced as a through hole at the outer cylindrical circumference of the sleeve and has an inner edge for supporting the cylindrical part with the larger diameter. The smaller diameter is guided through the through hole into the slotted cam, adapted to the width of the slotted cam, and is advantageously implemented as a hollow cylinder. In this case, in order to compensate for possible groove width fluctuations of the slotted cam, the diameter of the smaller cylindrical part engaged in the slotted cam can have a slight excess compared to the corresponding groove width, but a precisely matched processing is advantageous. A cylindrical ring that can be manipulated from the outside and fixed in the axial direction is rotatably supported on the outer surface of the sleeve. At the rotating ring, at least one transmission element, for example in the form of a tongue, is provided for engaging in a corresponding, axially acting cut-out guide. For this purpose, the cut-out guide is arranged as a linear guide on the cam carrier in a manner parallel to the cylinder axis, advantageously on the outer circumference, so that the transmission element fastened to the rotating ring can engage in the cut-out guide in a simple manner and establish an active connection. The rotation of the rotating ring then causes not only a rotation of the cam carrier in the sleeve but also an axial displacement thereof.

[0022] Of course, the same functionality is also ensured if the fixed sleeve is designed as a cam carrier with a grooved cam formed on its cylindrical inner circumference, and the cylindrical sleeve supported axially movably in the cam carrier has a sliding transmission element on its outer circumference for operative connection with the corresponding grooved cam of the cam carrier. In this case, the linear guide must be introduced into the cylindrical sleeve with the sliding transmission element / sliding sleeve, while the rotating ring is supported axially fixedly on the fixed cam carrier. This embodiment is the subject of the parallel claim 15, and advantageous designs are derived from the dependent claims.

[0023] According to the present invention, the angle between the radii of the first and second sliding transmission elements of the three sliding transmission elements is smaller than the corresponding angle of the third sliding transmission element. In this way, on the one hand, the rotation angle of only 120°, which is common or possible in the case of the rotating ring, is increased, and the design of the curved track or grooved cam according to the present invention can be realized. The basic idea of ​​the present invention is, on the one hand, to create space for an increased rotation angle of the rotating ring in the cylindrical mounting seat to improve the axial adjustment accuracy of the optical and mechanical components movably supported in the mounting seat, and on the other hand, to realize the rotation-axial conversion of the small axial stroke of the cam carrier caused by the rotation of the rotating ring and the notched linear guide.

[0024] For this purpose, it is particularly advantageous to arrange exactly two of the three sliding transmission elements at a narrow radial angle of less than 90° to one another. The third sliding transmission element is arranged at the circular circumference in an angle range diagonally opposite to the first and second sliding transmission elements in order to avoid mechanical instabilities and tilting moments. Surprisingly, it has been shown that the special arrangement of the sliding transmission elements at the circumference according to the invention does not cause instabilities and tilting moments, and in this way it is possible to achieve a rotation angle of the rotating ring of more than 100°, up to a maximum of 185°. Thus, a slotted cam can be introduced into the cam carrier, which, although it has a small axial inclination, has at the same time an extended length of more than 1 / 3 of the circumference of the cam carrier.

[0025] Advantageously, the first and the third sliding transmission element are arranged in one plane in the axial direction and the diameter of the second sliding transmission element is smaller than the diameter of the adjacently arranged first sliding transmission element. In this way, an overlap of two slotted cams of different widths for the first and second sliding sleeves is achieved while the guidance of all sliding sleeves in their associated slotted cams is not disrupted.

[0026] In another embodiment of the invention, the second sliding transmission element with a smaller diameter is arranged with an offset in the axial direction relative to the plane of the first and third sliding transmission elements. In this case, the grooved cam associated with the second sliding transmission element may have an axial offset preferably in the direction of the slope of the other two grooved cams. In this way, the narrower grooved cam of the second sliding transmission element at least partially overlaps the wider grooved cam of the first sliding transmission element in order to reserve the required structural space for the desired large rotation angle and the possibly necessary additional linear guide on the cam carrier.

[0027] In order to ensure that the sliding sleeves of the first and second sliding transmission elements are guided as reliably, independently and without interference in the two partially overlapping grooved cams, the radial distance of the first sliding transmission element to the column axis is particularly advantageously greater than the radial distance of the second sliding transmission element to the column axis. It is important for the invention that the two sliding transmission elements, which are arranged close to each other within a narrow angular range and differ in the sliding sleeve diameter, differ in their radial distance.

[0028] Preferably, the radial distance of the sliding transmission element with the sleeve of the smaller diameter is always smaller than the radial distance of the sliding transmission element with the sleeve of the larger diameter. In order to be able to optimally utilize the limited space available for the slotted cam at the cylindrical side, the third sliding element arranged at the periphery in a manner opposite to the other two sliding elements has a small diameter, for example, a diameter corresponding to the smaller sleeve diameter of the first or second sleeve. In this way, the space requirement for the width of the slotted cam of the third sliding transmission element is reduced, so that the slotted cams that overlap partially with the first and second sliding transmission elements do not intersect. Particularly advantageously, in this way, at the cam carrier, the end point of the slotted cam of the third sliding transmission element can be guided to the starting point of the slotted cam of the second sliding transmission element in a manner with an axial offset, and at this time extends further at the periphery than the starting point of the slotted cam of the first sliding transmission element.

[0029] In another embodiment of the present invention, a so-called cylindrical curved thread is introduced into the outer surface of the grooved cam associated with the sliding transmission element in the cam carrier and is configured. The radial distance of the groove bottom of the grooved cam is adapted to the radial distance of the corresponding sliding transmission element in a sliding manner. As already explained, for the sake of simple assembly, the sliding transmission element inserted into the sleeve has the shape of a cylindrical tenon, which has two different sizes of outer diameters, wherein the corresponding larger diameter is used for simple and centered insertion in the pocket hole of the sleeve. In the radial direction, the centering of the cam carrier can be achieved advantageously by the depth of the smaller diameter of the sliding element into the grooved cam. In this way, in addition to the cam carrier being axially movable and slidingly supported in the fixed sleeve, the cam carrier is further guided, which effectively prevents possible cam carrier shaft from swinging around the mounting seat or sleeve axis. According to the present invention, it is important for this function that the grooved cam at least partially has a groove bottom or at least one groove bottom edge and is not composed of an open curve that penetrates the cylindrical side of the cam carrier and simultaneously forms a cut.

[0030] Particularly advantageously, the grooved cam has a slope extending in the axial direction at the outer circumference, which slope is adapted to a predetermined or desired axial travel of the cam carrier. Due to the above-described special design according to the invention, a linearly or nonlinearly extending grooved cam is achieved.

[0031] Advantageously, the slotted cams of different depths associated with the first and second sliding transmission elements at least partially overlap. The thinner slotted cams are introduced deeper into the cam carrier and the wider ones are shallower.

[0032] In another embodiment of the invention, the grooved cam has a first region with an inclination that causes an axial stroke, which transitions into a second region without an inclination as the grooved cam further progresses on the circumference of the cam carrier. This region does not cause an axial stroke despite the angular adjustment at the rotating ring. In an advantageous manner, the axial stroke of the cam carrier generated by the inclination region is adapted to the maximum adjustment distance of the adjustment lever in the rangefinder of the camera and is 4.5 mm. According to the required compatibility of the lens with the rangefinder camera mentioned in the introduction to the description, the axial stroke caused by the inclination corresponds in this way to the maximum distance adjustment range from 0.7 m to infinity in the rangefinder of the camera. At the transition from the inclination region to the inclination region, a tactile indicator can advantageously be provided to indicate to the camera user that the close adjustment limit of the focus adjustment has been reached by the rangefinder. The tactile indicator can be formed by a locking pin under spring pressure, which slides over a perceptible slope at the transition from the inclination region to the inclination region. In this way, it is shown to the user that further focus adjustment of the focus element can no longer be performed by the optical rangefinder integrated into the camera, but can only be achieved by alternative devices. For example, in digital cameras, an electronic viewfinder (EVF) can be used, so that the close-range focusing between 0.7m and, for example, 0.45m must be achieved by the electronic viewfinder. Therefore, the rotation angle of the area without slope is used in an advantageous manner for the extended close-range focusing of less than 0.7m. In this case, the curve section without slope advantageously corresponds to a close-range focusing range of 0.7m to 0.4m. Due to the compatibility restrictions of rangefinder cameras, lenses with a possible maximum optical focus range of 0.4m or closer to infinity could previously only be adjusted within a range of 0.7m to infinity. In the lens configured by the present invention, focusing in an extended close-range range is also achieved.

[0033] In order to use the cylindrical mount according to the invention on a camera, preferably a rangefinder camera, a bayonet connection for snap-in locking on the camera system is provided on the fixed sleeve of the lens. For anchoring in a rotationally oriented manner on the camera lens holder, the lens has an optical marking on its outer side, which is arranged at a distance from the latching recess in the end face of the bayonet connection, as viewed in the anchoring rotation direction. Advantageously, the first and second sliding transmission elements are arranged in an angular range spaced apart from the latching recess, so that, as viewed in the axial direction relative to the camera, the two sliding transmission elements are arranged behind the anchoring in the region of an adjustment lever of the rangefinder, advantageously as viewed from the left and right.

[0034] In a particularly advantageous manner, the first and second sliding transmission elements are arranged at an angle of 28° to one another, or, looking at the bayonet, are arranged in an angle range of 45° to 135° counterclockwise from the latching recess. In this way, despite the asymmetrical distribution of the three sliding transmission elements on the cylindrical circumference of the cam carrier, a stable contact on the adjustment lever of the camera's rangefinder and a play-free transmission of the axial movement of the cam carrier to the adjustment lever are ensured.

[0035] In another design of the present invention, a worm screw sleeve with a slotted linear guide is arranged on the fixed sleeve to axially move the other optical component. The worm screw sleeve is operatively connected to the rotating ring, thereby converting the rotation into the axial movement of the other optical component.

[0036] Advantageously, the functional connection with the worm thread sleeve can be realized by a worm internal thread molded on the inside of the rotating ring, while the cylindrical inner sleeve has a corresponding worm external thread meshing with the worm internal thread of the rotating ring. In order to prevent rotation, the cylindrical inner sleeve has a cut-out linear guide, in which a transmission element in the form of a tongue connected to the fixed sleeve of the cylindrical mounting seat engages. In this way, the rotational movement of the rotating ring is converted into a linear movement of the cylindrical inner sleeve. Advantageously, the focusing element or so-called floating element of the lens is axially moved by the cylindrical inner sleeve. It is advantageous for the optical calculation of the lens that the pitch of the worm thread can be adapted to the desired focusing accuracy according to the large rotating ring rotation angle provided by the invention, regardless of the axial movement preset for the movement of the adjustment lever of the rangefinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] An exemplary embodiment of a cylindrical mount according to the invention is schematically shown in the drawings and is explained in more detail below with reference to the drawings.

[0038] in:

[0039] Figure 1 The cylindrical mount is shown in a manner viewed in the axial direction and with sections (section AA and section BB),

[0040] Figure 2 Shown along Figure 1 The cross-sectional view of section AA in

[0041] Figure 3 Shown along Figure 1 Cross-sectional view of the offset section BB,

[0042] Figure 4 Shows a top view of a cylindrical mount with a bayonet connection Figure X (and Figure 1 The same section AA and section BB),

[0043] Figure 5 The cross section along AA and BB and the latching recess are shown. Figure 4 The same overlook Figure X ,

[0044] Figure 6 Shows that along with Figure 4 The cross-sectional view of the same section AA,

[0045] Figure 7 Shows that along with Figure 4 The same offset cross-section of section BB,

[0046] Figure 8 A top view Y with a cross section is shown (with Figure 6 and 7 same),

[0047] Fig. 9 The cam carrier is shown in a perspective view, and the transmission element is also shown.

[0048] Fig.10 The cam carrier is shown in a perspective view, without showing the transmission elements,

[0049] Fig.11 shows an expanded view of the cam carrier,

[0050] Fig.12 A side view of the cam carrier is shown with a section. DETAILED DESCRIPTION

[0051] exist Figure 1, a cylindrical mount 1 for optical and mechanical components that can be adjusted in the direction of the optical axis or cylindrical axis 10 is shown. The top view looking into the section along the section lines AA and BB shows the cross-section of the sliding transmission elements G1, G2 and G3 inserted into the fixed sleeve 2. The sliding transmission elements G1, G2 and G3 have the shape of cylindrical tenons, which have two different sizes of outer diameters. The corresponding larger diameter engages in a pocket hole introduced at the outer cylindrical circumference of the sleeve 2. The pocket hole is introduced into the sleeve 2 as a through hole and is implemented to have an inner edge for supporting the corresponding cylindrical part with a larger diameter. Relative to their radius at the circumference of the sleeve 2, the sliding transmission elements G1 and G2 are arranged in an angular range of less than 90° with an angular distance W1-2 from each other. As a result, the angular distance W1-2 between the sliding transmission elements G1 and G2 is smaller than the angular distance W1-3 between the sliding transmission elements G1 and G3, and is also smaller than the angular distance W2-3 between the sliding transmission elements G2 and G3. Figure 1 In the example shown in , the angle W1-2 is 28°, the angle W1-3 is 168°, and the angle W2-3 is 164°. The axial distances of the cylindrical parts with smaller diameters of the sliding transmission elements G2 and G1 guided through the through hole from the cylinder axis 10 are referred to as radial distances 9 and 11. The radial distance 11 of the first sliding transmission element G1 is greater than the radial distance 9 of the second sliding transmission element G2. Correspondingly, the outer diameter of the cylindrical part with smaller diameter of the sliding element G1 guided through the through hole is greater than the outer diameter of the cylindrical part with smaller diameter of the sliding element G2 guided through the through hole.

[0052] exist Figure 2 It is shown along Figure 1 The cam carrier 5 is supported in the sleeve 2 in a rotatable and movably manner along the cylinder axis 10. The cam carrier has grooved cams N1, N2 and N3 introduced into its cylindrical outer surface. The sliding transmission element G1 engaged in the grooved cam N1 and the sliding transmission element G3 engaged in the grooved cam N3 are arranged in the axial direction in a plane marked by the dotted line 16. It is schematically shown that the rotating ring 7 is supported on the sleeve 2 in a rotatable and non-axially movably manner. For the axial movement of the cam carrier 5, Figure 2 The transmission element (not shown) is fastened to the rotating ring 7 and engages in a linear guide (also not shown). Fig. 9 The transmission element and the linear guide are described in more detail in .

[0053] Figure 3 Shown along the Figure 1, which has an axial offset on the column axis 10. The sliding transmission element G2 is arranged axially spaced apart relative to the sliding transmission element G3. For illustration, the dashed line 17 has a lateral offset in the axial direction on the column axis 10. The dashed line guided through the sliding transmission element G3 corresponds to Figure 2 The dashed line 16 in FIG. 1 extends to the column axis 10 .

[0054] exist Figure 4 Looking down from China Figure X A cylindrical mount 1 is shown with a bayonet connection 3 for locking the mount 1 to a camera system (not shown). For locking by snapping, the bayonet connection 3 has a latching recess 4 in its contact surface. The latching recess 4 is arranged in an angular range of between 45° and 135°, viewed counterclockwise. Figure 4 The sections AA and BB in Figure 1 .

[0055] This is achieved through Figure 5 The section in , in which the sliding transmission elements G1 , G2 and G3 and their angular positions relative to the latching recess 4 are shown in cross section.

[0056] An optical marking 15 is arranged counterclockwise on the outer side of the cylindrical receptacle 1 between the latching recess 4 and the position of the sliding transmission element G1 .

[0057] Figure 6 Shown along Figure 4 The optical mount 18 with the lens 19 is supported in the rotating ring 7 in such a way that it can be axially moved by the worm thread 20. Figure 2 Similarly, the sliding elements G1 and G3 are arranged in a plane indicated by the dashed line 16 .

[0058] exist Figure 7 It is shown along Figure 4 The cross section of the offset profile BB in . Figure 2 Similarly, the sliding transmission elements G2 and G3 are arranged with an axial offset along the dashed line 17 .

[0059] Figure 8 Shows the corresponding Figure 6 and 7 A top view Y with a section looking at the lens 19 and the mounting seat part 18. In this section, the transmission element 8 fastened to the rotating ring 7 in the linear guide 6 of the cam carrier 5 is shown. The mounting seat part 18 shown in section has an axially extending groove 21 on its inner cylindrical side, in which a transmission element 22 fastened to the sleeve 2 for axially moving the mounting seat 18 engages.

[0060] Fig. 9 A perspective view of a cam carrier 5 is shown with the sliding transmission elements G1 and G2, which engage in the start of their associated slotted cams N1 and N2, arranged side by side and without the sleeve 2. The end of the slotted cam N3 is shown axially offset relative to the sliding transmission element G1. The sliding transmission element G3 is schematically shown partially obscured by the cam carrier 5 and is located on the outside of the cam carrier 5 in the start of the slotted cam N3, which is not visible at this time.

[0061] In order to explain the positions of the grooved cams N1, N2 and N3 and the notched linear guide 6 at the periphery, Fig.10 The figure shows the method without the sliding transmission elements G1, G2 and G3. Fig. 9 The cam carrier 5 in.

[0062] Fig.11 The outer side of the cam carrier is shown in an expanded view, which further illustrates the design and positioning of the slotted cams N1, N2 and N3. The sliding transmission elements G1, G2 and G3 are shown at positions such that these positions represent the starting areas of the corresponding subordinate slotted cams N1, N2 and N3. The axial stroke of the cam carrier 5 is formed by a region 13 of the slotted cams N1, N2 and N3 with an axial slope starting from the starting point, and a region 14 without a slope and without an axial stroke adjoins this region to the end point of the slotted cams. The sliding transmission element G1 is arranged in the same axial plane as the sliding transmission element G3. Therefore, in Fig.11 , the sliding transmission elements G1 and G3 are arranged on the same imaginary line extending parallel to the edge of the cam carrier 5. The starting areas of the associated grooved cams N1 and N3 are implemented to be open in the axial direction towards the edge of the cam carrier 5, and the sliding transmission element G1 has a larger diameter compared to the sliding transmission element G3. Compared with the sliding transmission element G2, the sliding transmission element G1 also has a larger diameter, so that the width of the subordinate grooved cam N1 is also greater than the width of the grooved cam N2 of the sliding transmission element G2. The grooved cam N1 extends in its starting area to the starting area of ​​the grooved cam N2 in a non-overlapping manner. In order to make the grooved cams N1 and N2 overlap in the area 13 with the axial inclination, the thinner grooved cam N2 is introduced deeper into the cam carrier 5, and the wider grooved cam N1 is shallower. The grooved cam depth of the wider and shallower grooved cam N1 corresponds to the grooved cam depth in Figure 1 The larger radial distance 11 of the first sliding transmission element G1 shown and described in FIG. The grooved cam depth of the narrower and deeper grooved cam N2 corresponds to the grooved cam depth of the first sliding transmission element G1 shown and described in FIG. Figure 1 The smaller radial distance 9 of the sliding transmission element G2 shown in FIG. Fig.11In the region 13 with the axial inclination, the axial offset between the sliding transmission elements G1 and G2 corresponds to the radius of the sliding transmission element G2. In this way, in the region 13 with the inclination, narrow bearing edges for the wider grooved cam N1 are respectively left and right of the deeper introduced grooved cam N2. In combination with the grooved cam N2 which is introduced deeper than the grooved cam N1 but is designed to be narrower, the two can overlap without interference, while the sliding transmission element G1 is reliably guided in the grooved cam N1 and the narrower sliding transmission element G2 is reliably guided in the grooved cam N2. Advantageously, after the transition from the region 13 with the axial inclination to the region 14 without the inclination, a lateral bearing edge of the radius width of the sliding transmission element G2 is left for the wider grooved cam N1 for radial guidance of the cam carrier 5 in the sleeve 2 or in the mounting seat 1 and for additional coaxial alignment. In the region 14 without the axial inclination, the cam carrier no longer moves axially, but only rotates at this point. The area at the end point of the grooved cam N2 is arranged to be offset from the start point of the grooved cam N3 by the amount of the axial stroke 12 without intersecting the grooved cam N1 .

[0063] exist Fig.12 , the cam carrier 5 is shown in a side view looking toward the outer surface of the cylinder. In the inclined region 13 shown above the cylinder axis 10, the starting region of the wide slotted cam N1 is shown next to the end point of the narrow slotted cam N3. The starting region of the slotted cam N1 extends shallower in the cam carrier 5 than the likewise narrow slotted cam N2 without intersecting the slotted cam N2, but is wider than the adjacent and overlapping slotted cam N2. Fig.12 In the lower region of the embodiment, a section is shown in a sectional view in the region 14 of the grooved cams N1 and N2 without a slope. The sliding element G2, not shown, projects completely into the groove base of the grooved cam N2, while the groove base for the sliding element G1 with a wider diameter is formed by the grooved cam edge N1, which corresponds in width to half the grooved cam N2.

[0064] The subject matter of claim 15 is an alternative cylindrical mount using the same basic inventive idea, wherein the same object is achieved by the features of this claim, and the subject matter of the dependent claims referring to claim 15 are advantageous embodiments and improvements.

[0065] In the cylindrical mounting 101, the grooved cams N'1, N'2, N'3 in the cam carrier 102 associated with the sliding transmission elements G101, G102 and G103 are advantageously configured as cylindrical curved threads and are introduced into the inner face of the cam carrier 102. The axial distance of the groove bottom from the cylinder axis 110 is referred to as the radial distance 109, 111 and is adapted to the outwardly facing axial distance / radial distance of the respective sliding transmission element G101, G102.

[0066] In an advantageous embodiment of the cylindrical seat 101 , the grooved cams N′1 , N′2 , N′3 have an inclination in the axial direction adapted to a predetermined axial stroke of the sleeve 105 , wherein the grooved cams N′1 , N′2 , N′3 are designed to be linear or non-linear.

[0067] In a further design of the cylindrical mount 101 according to the invention, the grooved cams N'1, N'2 of different depths or different radial distances 109, 111 associated with the first and second sliding transmission elements G101, G102 at least partially overlap.

[0068] Furthermore, in this cylindrical seat 101 , the grooved cam can advantageously have a first region with a slope 13 which causes an axial travel 12 of the sleeve 105 , and a second region without a slope 14 which does not cause an axial travel 12 .

[0069] In another advantageous design, a bayonet connection having a latching recess for locking on a camera system not described in detail is provided on the fixed cam carrier 102, and the first and second sliding transmission elements G101, G102 are arranged in an angular range spaced apart from the latching recess.

[0070] Particularly advantageously, the first and second sliding transmission elements G101 , G102 are arranged in an angular range of 45° to 135° spaced apart from the latching recess 4 , viewed counterclockwise toward the bayonet connection 3 .

[0071] In the cylindrical mount 101 designed according to the invention, a worm screw sleeve 18 operatively connected to a rotating ring 107 is arranged on the fixed cam carrier 102 , the worm screw sleeve having a slotted linear guide for axial displacement of a further optical component 19 .

[0072] In an advantageous manner, the axial displacement distance 12 of the worm thread sleeve 18 can be implemented to be greater or smaller than the axial displacement distance 12 of the sleeve 105, wherein a further transmission element 22 is provided which is connected to the fixed cam carrier 102 and engages in the notched linear guide 21 of the worm thread sleeve 18 to prevent rotation. In this way, a reduction transmission or a speed increase transmission between the axially movable sleeve 105 and the worm thread sleeve 18 can be realized by a focusing element such as a lens.

[0073] The rotation angle of the rotating ring 107 is particularly advantageously between 100° and a maximum of 185° in order to ensure a particularly sensitive adjustment of the focus by the focusing element.

[0074] An embodiment of a cylindrical mount according to the invention according to claim 15 is schematically shown in the figure by means of alternative features having the same effect and according to Figures 13 to 19 Describe in more detail.

[0075] exist Fig.13 An alternative cylindrical mount 101 for optical and mechanical components that can be adjusted in the direction of the optical axis or cylindrical axis 110 is shown in FIG. A top view along the section lines CC and DD looking into the section shows a cross-sectional view of the sliding transmission elements G101, G102 and G103 inserted into the fixed cam carrier 102. The sliding transmission elements G101, G102 and G103 have the shape of a cylindrical tenon with two different sizes of outer diameters. The corresponding larger diameter is inserted into a pocket hole introduced at the cylindrical inner circumference of the cam carrier 102. The pocket hole is introduced into the cam carrier 102 as a through hole and is implemented with an inner edge for supporting the corresponding cylindrical part with a larger diameter. Relative to their radius at the outer periphery of the cam carrier 102, the sliding transmission elements G101 and G102 are arranged in an angular range of less than 90° in a manner with an angular distance W'1-2 from each other. Thus, the angle between the radii on which the sliding transmission elements G101 and G102 are located, or the angular distance W'1-2 between the sliding transmission elements G101 and G102 is smaller than the angular distance W'1-3 between the sliding transmission elements G101 and G103, and is also smaller than the angular distance W'2-3 between the sliding transmission elements G102 and G103. In this way, the distance between the first sliding transmission element G101 and the second sliding transmission element G102 among the three sliding transmission elements at the periphery of the sleeve 105 is smaller than the corresponding distance from the third sliding transmission element G103 at the periphery. The implementation scheme according to the present invention that is different from the usual 120° symmetrical arrangement scheme can also be defined according to the angle between the radius vectors or the angle between the radii on which the sliding transmission elements are located. Fig.13 In the example shown in , the angle W'1-2 is 30°, the angle W'1-3 is 165°, and the angle W'2-3 is 165°. The axial distances of the cylindrical portions with smaller diameter of the sliding elements G101 and G102 guided through the through hole from the cylinder axis 110 are referred to as radial distances 109 (for G101) and 111 (for G102). The radial distance 111 of the second sliding transmission element G102 is smaller than the radial distance 109 of the first sliding transmission element G101. The outer diameter of the cylindrical portion with smaller diameter of the sliding element G102 guided through the through hole is larger than the outer diameter of the cylindrical portion with smaller diameter of the sliding element G101 guided through the through hole.

[0076] Fig.14 Shown along the Fig.13, which has an axial offset on the column axis 110. The sliding transmission element G101 is arranged axially spaced apart relative to the sliding transmission element G103. For illustration, the dashed line 117 has a lateral offset in the axial direction on the column axis 110. The dashed line guided through the sliding transmission element G103 corresponds to Fig.15 The dashed line 116 in FIG. 1 extends to the column axis 10 .

[0077] exist Fig.15 In the figure, it is shown that Fig.13 1 . The sleeve 105 is supported in the cam carrier 102 in a rotatable and axially movable manner along the column axis 110. The cam carrier 102 has grooved cams N'1, N'2 and N'3 introduced into its cylindrical inner surface. The sliding transmission element G101 engaged in the grooved cam N'1 and the sliding transmission element G103 engaged in the grooved cam N'3 are arranged in the axial direction in the plane marked by the dotted line 16. It is schematically shown that the rotating ring 107 is supported on the cam carrier 102 in a rotatable and non-axially movable manner. For the axial movement of the sleeve 105, the transmission element 108 is fastened to the rotating ring 107 and engaged in the cut-out linear guide 106.

[0078] exist Fig.16 , a cross-sectional view of the inner side of the cam carrier 102 is shown, which further illustrates the design and relative positioning of the grooved cams N′1 , N′2 and N′3 .

[0079] Above the column axis 110, the overlapping, axially linearly rising regions of the grooved cams N'1 and N'2 are shown. Fig.16 In the case of a rotation of the sleeve 105 (not shown), this region causes an axial travel of the sleeve 105. Below the column axis 110, the grooved cams N'1 and N'2 extend in a manner with an axial offset, which corresponds to the axial offset at Fig.14 The dashed line 117 in Fig.15 116 in FIG. However, in this region, the grooved cams N'1 and N'2 extend parallel to each other and no longer rise linearly axially. If the sliding transmission elements G101 and G102 of the sleeve 105 (not shown) engage in this region, then despite the rotation of the sleeve 105, an axial movement of the sleeve 105 along the column axis 110 in the cam carrier 102 no longer takes place.

[0080] exist Fig.17 and 18The perspective view in illustrates the geometric arrangement of the grooved cams N'1, N'2 and N'3 at the inner periphery of the cam carrier 102. The sliding transmission elements G101, G102 and G103 engaged in the grooved cams are schematically shown here, and the sleeve 105 is not shown.

[0081] exist Fig.19 , an alternative linear guide 106' is shown, which is designed as a raised molded part on the sleeve 105 and extends parallel to the column axis 110. The linear guide 106' is surrounded by a transmission element 108' fastened to the rotating ring 107 (not shown). In this way, the rotational movement carried out on the rotating ring 107 can be transmitted to the sleeve 105 via the transmission element 108' and converted into an axial displacement of the sleeve 105 due to the active connection between the grooved cam of the cam carrier 102 and the sliding transmission element of the sleeve 105.

[0082] List of Reference Numerals

[0083] 1. 101 column mounting seat

[0084] 2. 105 fixed sleeve

[0085] 3 bayonet connection

[0086] 4 locking recesses

[0087] 5. 102 cam carrier

[0088] 6. 106 cut-out linear guide

[0089] 106' linear guide (external)

[0090] 7.107 rotating ring

[0091] 8. 108 Transmission element (rotation)

[0092] 9 Radius distance of sliding transmission element G2

[0093] 109 Radius distance of sliding transmission element G101

[0094] 10, 110 column axis

[0095] 11 Radius distance of sliding transmission element G1

[0096] 111 Radius distance of sliding transmission element G102

[0097] 12Axial travel

[0098] 13 Grooved cam area with axial inclination

[0099] 14 Slotted cam area without axial inclination

[0100] 15 Optical Marking

[0101] 16 Dashed line - plane G1 G3

[0102] 116 dotted line-plane G102 G103

[0103] 17 dotted line - axial offset G2 G3

[0104] 117 dotted line - axial offset G101 G103

[0105] 18 Mounting seat with worm thread and worm thread sleeve

[0106] 19 lenses

[0107] 20 Worm thread

[0108] 21 Axially extending groove

[0109] 22 Transmission element (fixed)

[0110] G1, G2, G3 sliding transmission elements

[0111] G101, G102, G103 sliding transmission element (alternative)

[0112] N1, N2, N3 Cam with groove

[0113] N'1, N'2, N'3 Cam with groove (alternative)

[0114] W1-2 is the angle between the sliding transmission elements G1 and G2

[0115] W1-3 is the angle between the sliding transmission elements G1 and G3

[0116] W2-3 is the angle between the sliding transmission elements G2 and G3

[0117] W'1-2 is the angle between the sliding transmission elements G101 and G102

[0118] W'1-3 is the angle between the sliding transmission elements G101 and G103

[0119] W'2-3 is the angle between the sliding transmission elements G102 and G103

Claims

1. A cylindrical mounting seat (1) for adjustable optical and mechanical components, the mounting seat comprising: a sleeve (2) fixed relative to the mounting seat; three sliding transmission elements dispersedly arranged on the cylindrical inner circumference of the sleeve for being operatively connected to corresponding grooved cams of a cam carrier (5) supported in a rotatable and axially movable manner in the sleeve (2), the cam carrier having a notched linear guide (6); and a rotating ring (7) fixed in the axial direction, supported on the outer surface of the sleeve and operable from the outside, the rotating ring having at least one transmission element (8) for engaging in the notched linear guide (6) of the cam carrier (5), characterized in that The angle (W1-2) between the radius where the first sliding transmission element (G1) and the second sliding transmission element (G2) among the three sliding transmission elements (G1, G2, G3) are located is smaller than the corresponding angle (W1-3) between the radius where the first sliding transmission element and the third sliding transmission element (G3) are located and the corresponding angle (W2-3) between the radius where the second sliding transmission element and the third sliding transmission element are located.

2. The cylindrical mounting seat (1) according to claim 1, characterized in that: The angle (W1-2) between the radii on which the first sliding transmission element (G1) and the second sliding transmission element (G2) are located is less than 90°.

3. The cylindrical mounting seat (1) according to claim 2, characterized in that: The first sliding transmission element (G1) and the third sliding transmission element (G3) are arranged in a plane in the axial direction, and the diameter of the second sliding transmission element (G2) is smaller than the diameter of the first sliding transmission element (G1).

4. The cylindrical mounting seat (1) according to claim 3, characterized in that: The second sliding transmission element (G2) having a smaller diameter is arranged to be spaced apart from the plane of the first sliding transmission element (G1) and the third sliding transmission element (G3) in the axial direction.

5. The cylindrical mounting seat (1) according to claim 3 or 4, characterized in that: Compared with the first sliding transmission element (G1), the second sliding transmission element (G2) having a smaller diameter has a smaller radial distance (9) from the column axis (10) than the radial distance (11) from the first sliding transmission element (G1) to the column axis.

6. The cylindrical mounting seat (1) according to claim 5, characterized in that: The grooved cams (N1, N2, N3) associated with the sliding transmission elements (G1, G2, G3) in the cam carrier (5) are constructed as cylindrical threads and are introduced into the inner surface of the cam carrier (5), wherein the radial distance of the groove bottom is adapted to the radial distance (9, 11) of the corresponding sliding transmission elements (G2, G1).

7. The cylindrical mounting seat (1) according to claim 6, characterized in that: The grooved cams (N1, N2, N3) have an inclination in the axial direction adapted to a predetermined axial stroke (12) of the cam carrier (5), wherein the grooved cams (N1, N2, N3) are designed to be linear or non-linear.

8. The cylindrical mounting seat (1) according to claim 7, characterized in that: The grooved cams (N1, N2) of different depths associated with the first sliding transmission element (G1) and the second sliding transmission element (G2) at least partially overlap.

9. The cylindrical mounting seat (1) according to claim 8, characterized in that: The grooved cam has a first region (13) with an inclination which causes an axial stroke (12) and a second region (14) without an inclination which does not cause the axial stroke (12).

10. The cylindrical mounting seat (1) according to any one of the preceding claims, characterized in that A bayonet connection having a latching recess for locking on a camera system is provided on the fixed sleeve (2), and the first sliding transmission element and the second sliding transmission element are arranged in an angular range spaced apart from the latching recess.

11. The cylindrical mounting seat (1) according to claim 10, characterized in that: Looking counterclockwise toward the bayonet connection (3), the first sliding transmission element and the second sliding transmission element (G1, G2) are arranged in an angular range of 45° to 135° from the latching recess (4).

12. The cylindrical mounting seat (1) according to claim 11, characterized in that: In order to axially displace the further optical component (19), a worm screw sleeve (18) operatively connected to the rotating ring (7) and having a slotted linear guide is arranged on the fixed sleeve (2).

13. The cylindrical mounting seat (1) according to claim 12, characterized in that: The axial displacement distance (12) of the worm screw sleeve (18) is greater than or less than the axial displacement distance (12) of the cam carrier (5), wherein another transmission element (22) is provided which is connected to the fixed sleeve (2) and simultaneously engages in the notched linear guide (21) of the worm screw sleeve (18) to prevent rotation.

14. The cylindrical mounting seat (1) according to any one of claims 2 to 13, characterized in that: The rotation angle of the rotating ring (7) is between 100° and a maximum of 185°.

15. A cylindrical mounting seat (101) for adjustable optical and mechanical components, the mounting seat comprising: a cam carrier (102) fixed relative to the mounting seat; three grooved cams (N'1, N'2, N'3) dispersedly arranged on the cylindrical inner circumference of the cam carrier for being operatively connected to corresponding sliding transmission elements (G101, G102, G103) of a sleeve (105) supported in a rotatable and axially movable manner in the cam carrier (102), the sleeve having a notched linear guide (106); and a rotating ring (107) fixed in the axial direction, supported on the outer surface of the cam carrier (102) and operable from the outside, the rotating ring having at least one transmission element (108) for engaging in the notched linear guide (106) of the sleeve (105), characterized in that The angle (W101-102) between the radii on which the first sliding transmission element (G101) and the second sliding transmission element (G102) of the three sliding transmission elements (G101, G102, G103) are located is smaller than the corresponding angle (W101-103) between the radii on which the first sliding transmission element and the third sliding transmission element (G103) are located and the corresponding angle (W102-103) between the radii on which the second sliding transmission element and the third sliding transmission element (G103) are located, or the distance between the first sliding transmission element (G101) and the second sliding transmission element (G102) of the three sliding transmission elements (G101, G102, G103) at the periphery of the sleeve (105) is smaller than the corresponding distance between them and the third sliding transmission element (G103) at the periphery.

16. The cylindrical mounting seat (101) according to claim 15, characterized in that: The angle (W101-102) between the radii at which the first sliding transmission element (G101) and the second sliding transmission element (G102) are located is less than 90°, or the distance between the first sliding transmission element (G101) and the second sliding transmission element (G102) at the periphery of the sleeve (105) is less than 25% of the total circumference of the sleeve (105).

17. The cylindrical mounting seat (101) according to claim 16, characterized in that: The second sliding transmission element (G102) and the third sliding transmission element (G103) are arranged in a plane in the axial direction, and the diameter of the first sliding transmission element (G101) is smaller than the diameter of the second sliding transmission element (G102).

18. The cylindrical mounting seat (101) according to claim 17, characterized in that: The first sliding transmission element (G101) having a smaller diameter is arranged to be spaced apart from the planes of the second sliding transmission element (G102) and the third sliding transmission element (G103) in the axial direction.

19. The cylindrical mounting seat (101) according to claim 17 or 18, characterized in that: Compared with the second sliding transmission element (G102), the first sliding transmission element (G101) having a smaller diameter has a radial distance (109) from the column axis (110) greater than the radial distance (111) from the second sliding transmission element (G102) to the column axis.

Images