Cylindrical holder for adjustable optical and mechanical structural elements - Patents.com

Abstract

To improve a drawback regarding conversion of a position adjustment path of a focusing element in an objective lens to a position adjustment path of a range finder. A cylindrical holder for position-adjustable optical and mechanical structural elements. The holder has a sleeve (2) whose position is fixed relative to the holder, three sliding transmission elements distributed on the cylindrical inner circumference of the sleeve (2) for operatively connecting with corresponding groove cams of a cam carrier (5) that is supported rotatably and axially shiftably in the sleeve (2) and has a slot-shaped linear guide (6), and a rotating ring (7) having at least one transmission element (8) that is axially position-fixed, supported on the outer circumferential surface of the sleeve, operable from the outside, and fitted into the slot-shaped linear guide (6) of the cam carrier (5). An angle (W1-2) between the radius of the first sliding transmission element (G1) and the radius of the second sliding transmission element (G2) of the three sliding transmission elements (G1, G2, G3) is smaller than the respective angles (W1-3, W2-3) with respect to the third sliding transmission element (G3).

Description

[Technical field]

[0001] The invention relates to a cylindrical holder for optical and mechanical components according to the preamble of claim 1, in particular to an objective holder for an objective lens which can be adjusted to different object distances for a viewfinder camera, which has a distance adjustment ring and a device connected to said ring for transmitting the adjusted distance to an adjustment lever of a movable optical element of a split-image rangefinder arranged on the camera side. Split-image rangefinders are also known as double-image viewfinders, coincident viewfinders or in the common language rangefinders. The viewfinder camera is, for example, a camera of the Applicant's M system, which has been known for several decades due to its compatibility with corresponding objective lenses of different focal lengths of the M system. [Background technology]

[0002] In such photographic objectives, it is known to shift one or more imaging lenses along the optical axis in order to sharply image the object to be imaged on the imaging plane of the camera in each case, and it is further known to couple (connect) a movable optical element integrated in the camera's range finder with a shiftable objective lens or a focus shift mechanism of the objective lens within the camera via an adjustment lever.

[0003] As a shift mechanism in the objective lens, a helicoid threaded sleeve with or without a linear guide is usually used, which can be externally actuated by means of a distance adjustment ring with an internal thread.

[0004] In the case of objectives with standard focal lengths, such as for example 50 mm objectives for Leica format (35 mm), a rotation limited to less than 95° in the distance adjustment ring causes, on the one hand, an axial shift of the helicoid threaded sleeve for focusing, and, on the other hand, a rotation of the helicoid threaded sleeve around the optical axis of the system. The adjustment lever abuts against the front face of the helicoid threaded sleeve and in this way couples with the focus shift mechanism of the objective. With a linkage of only 4.5 mm of the adjustment lever, optical sharpness adjustment over a distance range from 0.7 m to infinity is possible in this way. The different position adjustment paths, which depend on the distance between the axial adjustment movement required for focusing of the optical imaging system and the associated movement of the adjustment lever for the range finder, and the possible nonlinearities are compensated for, for example, via an upslope which is subsequently additionally produced by milling on the front surface of the helicoid thread sleeve, as a possibly linear or nonlinear axial curve. The mechanical costs for this are very high and, moreover, a high effort is required for the application of the milling.

[0005] Depending on the objective lens design and the focal length of the objective lens, the adjustment path of the focus shift mechanism of the optical system or optical assembly (structure) required for focusing from an object distance at infinity to the close range is often significantly different, while the adjustment range in a rangefinder is mechanically limited ("adapted") to an object distance from 0.7 m to infinity depending on the design, since the adjustment path (stroke) of the adjustment lever available for this purpose is still 4.5 mm.

[0006] The adaptation of the objective lens to the camera in terms of distance adjustment is achieved by performing a conversion independently of the various position adjustment paths of the focusing mechanism into the position adjustment paths of the adjustment lever predefined by the camera in the range finder for the distance range from 0.7 m to infinity.

[0007] This conversion needs to be performed with high precision and therefore entails additional high mechanical costs (complexity). Usually, the conversion follows the function of a reduction or increase gear with multiple intermeshed helicoid threads and threaded sleeves. [Prior art documents] [Patent documents]

[0008] Summary of the Invention [Problem to be solved by the invention]

[0009] Such a type of large objective lens holder is known from DE 2 040 227 A1. The objective lens holder contains a number of imaging lenses which can be shifted along the optical axis of the system by means of a distance adjustment ring in order to respectively sharply image the object to be imaged in the imaging plane. The distance adjustment ring is connected to an outer threaded barrel as a drive device configured as a helicoid. An inner threaded barrel, which is likewise configured as a helicoid, is inserted into this threaded barrel. The inner threaded barrel is guided in a straight line in the objective lens holder in such a way that a rotation of the outer threaded barrel is converted into a shift of the inner threaded barrel along the optical axis of the system. The imaging lenses are fixedly inserted into the inner threaded barrel and are therefore involved in this axial longitudinal shift.

[0010] A cam ring is rotatably fitted into the inner threaded barrel on the camera side, which is driven by a drive pin connected to the outer threaded barrel. The cam ring is supported by a fixing ring which is placed on an annular shoulder on the inner wall of the inner threaded barrel and is screwed onto the outer circumference of the inner threaded barrel. The drive pin passes through a radial slot in the inner threaded barrel and is connected to the cam ring. The cam ring has an axial cam on its front face on the camera side. A tappet, which is supported so as to be rotatable around an axis perpendicular to the optical axis of the system, engages with the axial cam (top) via a roller. The tappet is connected to an adjustment lever of the rangefinder.

[0011] Thus, when a rotation is made on the distance adjustment ring, the cam ring is shifted axially on the one hand and rotated around the optical axis of the system on the other hand. By combining both movements, the relatively large axial shift of the threaded barrel is accelerated or decelerated (i.e. shifted) to the small tappet movement required for the position adjustment path of the adjustment lever in the range finder. Through the ramp of the axial cam, different position adjustment paths and nonlinearities depending on the focal length between the axial adjustment movement of the optical imaging system and the movement of the adjustment lever for the range finder associated therewith can thus be compensated (adjusted) to a limited extent.

[0012] For the position adjustment of the adjustment lever and the focusing elements, so-called cylinder cam screws are also known in the objective lens construction. The cylinder cam screws are provided with three grooved cams that are distributed symmetrically around the circumference of the fixed (stationary) sleeve of the cam carrier and increase linearly in the axial direction, into which sliding transmission elements that engage (engage) convert the rotational movement in the distance adjustment ring into an axial shift in cooperation with the linear guide. The maximum available rotation angle for focusing from infinity to close range is limited on the one hand by the range of 120° between the grooved cams or the sliding transmission elements and on the other hand by the fact that a transmission element of the distance adjustment ring must also be arranged in this range due to the engagement of the cam carrier in the linear guide.

[0013] The focusing adjustment accuracy is thus limited, because due to the relatively large axial shift of the threaded barrel of the focusing mechanism, only a rotation angle range of less than 95° is available at the distance adjustment ring. This proves to be particularly disadvantageous, on the one hand, in the case of objectives with large focal lengths, which require large position adjustments for focusing, and on the other hand, in the case of objectives with high numerical apertures, because in these cases the depth of field on the image side is reduced and thus the inaccuracies (errors) of the focusing adjusted by the user can no longer be compensated for.

[0014] It turns out that a rotation angle of 95° barely meets the requirements for focusing accuracy in the range from 0.7 m to infinity for an objective lens with a focal length of 50 mm. Modern objective lens designs, however, allow sharpness adjustment (focusing) for object distances less than 0.7 m, for example down to 0.45 m. However, for this adjustment a rotation angle of approximately 175° would be required.

[0015] However, a symmetrical distribution in the axial plane on the circumference of the grooved cams has been demonstrated in the known cam carriers, since in this way tilting moments (torques) and instabilities are avoided. The guide tracks or grooved cams have in this case the same axial rise. The rotation angle of the distance adjustment ring is also limited in this case by the start and end of the grooved cams. Small axial shifts are possible with small axial rises for a maximum rotation angle of 95°. Between the end of one grooved cam and the start of the next grooved cam, in this way there is in this case just enough cylinder shell material to ensure the mechanical stability of the cam carrier.

[0016] If it is desired to realize larger rotation angles in the known 120° arrangement, this is only possible if the axial rise of the guide tracks is selected so large that the beginning and end of adjacent grooved cams have a sufficient axial offset. The minimum width of the grooved cams required for a reliable mechanical movement makes even small axial shifts such as the 4.5 mm provided for the adjustment lever of a rangefinder impossible.

[0017] From EP 2 693 247 A1, a cylindrical holder with a cam carrier and axially offset cam tracks is known, which allows large angles of rotation. The axially offset cam tracks have high spatial requirements and require a large cylinder circumference. Smaller axial position adjustments cannot be realized. Furthermore, the material of the cylinder is mechanically weakened and unstable under axial loads due to the many times narrower adjacent running gaps for the cam tracks.

[0018] Further cylindrical holders for optical components having a cam carrier and a cylindrical cam screw are known, for example, from US 2015 / 0205068 A1 and US 3,951,522.

[0019] The object of the invention is to overcome the drawbacks of objectives, which exist in connection with rangefinder cameras, with regard to the conversion of the adjustment paths of the focusing element into the adjustment paths of the rangefinder, to increase the adjustment accuracy of the axial alignment of the focusing element in the objective, in particular in the case of large shift paths of the focusing element, and at the same time to ensure the transmission accuracy of the connection to the adjustment lever of the camera rangefinder and its predefined adjustment path, which are required for focusing.A further object of the invention is to realize a focusing ability for object distances of less than 0.7 m, i.e. from infinity down to 0.4 m, in the case of objectives with a rotary axis converter for operating the adjustment lever of the camera rangefinder. [Means for solving the problem]

[0020] The above object is achieved by a cylindrical holder for position-adjustable optical and mechanical components having the features of claim 1. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0021] Advantageous configurations and developments are the subject of the dependent claims.

[0022] In the cylindrical holder according to the invention, a sleeve is provided which is fixed relative to the holder and which has three sliding transmission elements distributed on the cylindrical inner circumference of the sleeve for an operational connection with three corresponding grooved cams of a cam carrier rotatably supported in the sleeve. Exactly one grooved cam is assigned to each of the three sliding transmission elements. The sliding transmission elements have a shape adapted to the grooved cams and are in particular configured as plastic circular sleeves. For easy assembly, the sliding transmission elements have a cylinder stud shape (or a short cylinder shape) with two differently sized outer diameters.

[0023] The respective larger diameters serve for simple insertion into the counterbore formed in the sleeve cylinder outer circumference as through-holes with an inner edge on which the cylinder parts with the larger diameter rest. The smaller diameters are guided through the through-holes up to the groove cams, adapted to the width of the groove cams and preferably constructed as hollow cylinders. The diameters of the smaller cylinder parts which insert into the groove cams can have a small oversize in relation to the respective groove width in order to compensate for possible variations in the groove width of the groove cams, but are preferably manufactured exactly. A cylindrical ring which can be actuated from the outside and is axially stationary is supported rotatably on the outer circumference of the sleeve. This rotating ring is provided with at least one transmission element, for example in the form of a lug for inserting into a corresponding axially acting slot guide. The slot guide is arranged on the cam carrier as a linear guide parallel to the cylinder axis, preferably on the outer periphery, so that the transmission elements fixed to the rotating ring can simply slide into the slot guide and form an operational connection. The rotation of the rotating ring then causes a rotation and axial shift of the cam carrier in the sleeve.

[0024] Obviously, the same functionality is ensured if the stationary sleeve is configured as a cam carrier with cam grooves formed on its cylindrical inner circumference and if a cylindrical sleeve supported in an axially shiftable manner in the cam carrier has sliding transmission elements on its outer circumference for operative connection with corresponding cam grooves of the cam carrier. In this case, the linear guide has to be formed as a cylindrical sleeve with sliding transmission elements / sleeves, while the rotating ring is supported stationarily in the axial direction on the stationary cam carrier. This embodiment is the subject of the corresponding claim 15, advantageous embodiments of which are evident from the dependent claims.

[0025] According to the invention, the angle between the radius of the first sliding transmission element and the radius of the second sliding transmission element of the three sliding transmission elements is smaller than the respective angle for the third sliding transmission element, which on the one hand increases the rotation angle of the otherwise usual or barely possible 120° of the rotating ring and on the other hand also makes possible the inventive configuration of the cam track or groove cam. The basic idea of ​​the invention is, on the one hand, to create space in the cylindrical holder for an increased rotation angle of the rotating ring in order to increase the axial adjustment accuracy of the optical and mechanical structural elements shiftably supported in the holder, and on the other hand to allow a rotation axis translation of a small axial stroke of the cam carrier caused by the rotation of the rotating ring and the slotted linear guide.

[0026] Particularly advantageously, two or exactly three sliding transmission elements are arranged within a narrow radial angle of less than 90° relative to one another. The third sliding transmission element is arranged in a circumferential angular range diametrically opposite to the first and second sliding transmission elements in order to avoid mechanical instabilities and torque moments. Surprisingly, it has been found that this special inventive arrangement of the sliding transmission elements on the circumference causes small instabilities and torque moments, so that rotation angles of the rotating ring of more than 100°, up to a maximum of 185°, can be realized. In this case, the cam carrier can be formed with a groove cam that has a small axial rise but at the same time has a development length that is greater than 1 / 3 of the circumference of the cam carrier.

[0027] It is furthermore advantageous that the first and third sliding transmission elements are arranged in one plane in the axial direction, the diameter of the second sliding transmission element being smaller than the diameter of the adjacent first sliding transmission element, so that a superposition of two grooved cams with different widths for the first and second sliding sleeves is possible when all sliding sleeves are guided simultaneously in the respectively assigned grooved cams without any problems (without mutual interference).

[0028] In a further embodiment of the invention, the second sliding transmission element having a smaller diameter is arranged axially spaced apart from the face of the first and third sliding transmission elements. The groove cam assigned to the second sliding transmission element can then have an axial offset, advantageously in the direction of the ascending gradient of the other two groove cams. This allows the narrower groove cam of the second sliding transmission element to at least partially overlap the wider groove cam of the first sliding transmission element in order to free up the required construction space for the desired large rotation angle and possibly for the further linear guide required in the cam carrier.

[0029] In order to ensure the most reliable, independent and unhindered guidance of the sliding sleeves of the first and second sliding transmission elements in the two overlapping grooved cams, in a particularly advantageous manner, the radial distance of the first sliding transmission element relative to the cylinder axis is greater than that of the second sliding transmission element. In this case, what is important for the invention is that the radial distances of two sliding transmission elements that are closely arranged side by side in a narrow angular range and have different diameters of sliding sleeves are different from each other. Preferably, the radial distance of the sliding transmission element with the smaller diameter sleeve is always smaller than the radial distance of the sliding transmission element with the larger diameter sleeve. In order to make adequate use of the limited space available for the grooved cams in the cylinder shell, the third sliding transmission element, which is arranged circumferentially opposite the other two sliding transmission elements, has a smaller diameter, for example a diameter corresponding to the smaller diameter of the first or second sleeve. The spatial requirements for the width of the groove cam of the third sliding transmission element are thus reduced, so that there is no intersection with the partially overlapping groove cams of the first and second sliding transmission elements. Particularly advantageously, this allows the end of the groove cam of the third sliding transmission element on the cam carrier to be axially offset close to the start of the groove cam of the second sliding transmission element and, in so doing, to reach further in the circumference than the start of the groove cam of the first sliding transmission element.

[0030] In an advantageous embodiment of the invention, the grooved cams assigned to the sliding transmission elements are formed on the cam carrier on the outer periphery and are configured as so-called cylinder cam threads. The radial distance of the groove base of the grooved cams is slidably adapted to the radial distance of the respective sliding transmission element. As already mentioned, the sliding transmission elements which are inserted into the sleeve have the shape of a cylinder stud with two differently sized outer diameters for easy assembly, the respective larger diameters serving for a simple and centered insertion into the (deep) counterbores of the sleeve. In the radial direction, the penetration depth of the sliding (transmission) elements into the grooved cams of the smaller radius can advantageously provide for centering of the cam carrier. In this way, in addition to the sliding bearing (support) of the axial shift of the cam carrier in the position-fixed sleeve, a further guidance of the cam carrier is provided, which effectively prevents possible deflections (tilts) of the axis of the cam carrier around the axis of the holder or sleeve. What is important in the present invention for this function is that the grooved cams have at least partially one groove bottom or at least one groove bottom edge and do not consist of open cams which penetrate the cylinder shell of the cam carrier and thereby form a slit.

[0031] Particularly advantageously, the grooved cam has an axially extending ascending slope at its outer periphery that is adapted to the predetermined or desired axial stroke of the cam carrier. Due to the special configuration according to the invention already described, linearly (straightforward) or non-linearly (non-linearly) extending grooved cams are possible.

[0032] Further advantageously, the grooved cams respectively assigned to the first and second sliding transmission elements and having different depths at least partially overlap, the thinner (shallower) grooved cam being formed deeper in the cam carrier and the wider grooved cam being formed shallower.

[0033] In a further embodiment of the invention, the grooved cam has a first region with an upward gradient which provides an axial stroke, which transitions further along the circumference of the grooved cam into a second region without an upward gradient. The latter region (second region) does not provide (generate) an axial stroke, despite the angular adjustment at the rotating ring. Advantageously, the axial stroke of the cam carrier generated by the upward gradient region (region with upward gradient) is adapted to the maximum adjustment path of the adjustment lever in the camera range finder and amounts to 4.5 mm. Depending on the required compatibility of the objective lens with the range finder camera described in the introduction of this document, the axial stroke provided by the upward gradient in this way corresponds to the maximum distance adjustment range of the camera range finder from 0.7 m to infinity. At the transition from the area with an incline to the area without an incline (area without an incline), a tactile indicator can advantageously be provided to show the camera user that the minimum focusing distance for the sharpness adjustment (focusing) by the range finder has been reached. The tactile indicator can be formed by a spring-loaded plunger pin that operates via a perceptible slope at the transition from the area with an incline to the area without an incline. In this way, it is possible to show the user that further sharpness adjustment of the focusing element is no longer possible by the optical range finder integrated in the camera, but is only just possible by alternative means. For example, in the case of a digital camera, an electronic viewfinder (EVF) can be used, which in this case has to perform close-range focusing between 0.7 m and, for example, 0.45 m. Advantageously, in this case, a rotation angle of the area without an incline is used for extended close-range focusing of less than 0.7 m. The cam section without an upward incline advantageously corresponds in this case to a proximal focusing range of 0.7 m to 0.4 m.Objective lenses, which have the maximum optically possible focusing range of less than 0.4 m to infinity, have traditionally only been adjustable in the range from 0.7 m to infinity due to compatibility limitations imposed by rangefinder cameras. With objective lenses constructed with the present invention, focusing at extended close distances is also possible.

[0034] For the use of the cylindrical holder according to the invention in a camera, preferably in a rangefinder camera, the stationary (immovable) sleeve of the objective lens is provided with a bayonet connection for a claw-type locking fixation to the camera system. For a twist determined by the rotation angle to the camera-objective lens connection, the objective lens has an optical marking on its outer periphery, which is arranged on the front (end) part of the bayonet connection, spaced from the locking recesses in the circumferential direction of the twisting rotation. Advantageously, the first and second sliding transmission elements are arranged at an angular distance from the locking recesses, so that they are arranged in the axial direction towards the camera in the region of the adjustment lever of the rangefinder after said twisting, advantageously on the left and right sides.

[0035] In a particularly advantageous embodiment, the first and second sliding transmission elements are arranged at an angle of 28° to each other, or they are arranged counterclockwise at an angle range of 45° to 135° from the locking recess, as viewed towards the bayonet. In this way, despite the asymmetric distribution of the three sliding transmission elements around the circumference of the cylinder of the cam carrier, a stable abutment on the adjustment lever of the camera rangefinder and a play-free transmission of the axial movement of the cam carrier to the adjustment lever are ensured.

[0036] In a further embodiment of the invention, the stationary sleeve is provided with a helicoid threaded sleeve with a slotted linear guide for axial shifting of the further optical structural element, which is operatively coupled to a rotating ring such that a rotation is converted into an axial shifting movement of the further optical structural element.

[0037] The operative connection to the helicoidal thread sleeve can be advantageously achieved by a female helicoidal thread formed on the inner circumference of the rotating ring, while the cylindrical inner sleeve has a corresponding male helicoidal thread that meshes with the female helicoidal thread of the rotating ring. For the prevention of rotation, the cylindrical inner sleeve has a slotted linear guide into which a transmission element in the form of a tongue fits, which is connected to a stationary sleeve of the cylindrical holder. In this way, the rotational movement of the rotating ring is converted into a linear movement of the cylindrical inner sleeve. By means of the cylindrical inner sleeve, the focusing element or the so-called floating element of the objective lens can advantageously be shifted axially. Advantageously for the optical calculation of the objective lens, the ramp (or pitch) of the helicoidal thread for the desired focusing accuracy, which depends on the large rotation angle in the rotating ring, which is possible according to the invention, is made possible without depending on the axial shift that is predetermined for the movement of the adjustment lever of the range finder.

[0038] Embodiments of a cylindrical holder according to the invention are depicted diagrammatically in the drawings and are explained in more detail below with the aid of the drawings. [Brief description of the drawings]

[0039] [Figure 1] An example of a cylindrical holder in axial view with partial cross sections (sections AA and BB). [Diagram 2] FIG. 2 is a cross-sectional view taken along the partial cross-section (cutting line) AA of FIG. 1 (cross-sectional view taken along the line AA). [Diagram 3]A cross-sectional view taken along the displaced partial cross-section (cutting line) BB in FIG. 1 (cross-sectional view taken along the arrow BB) [Figure 4] FIG. 1B is a plan view X of an example of a cylindrical holder having a bayonet coupling (with cut lines AA and BB similar to FIG. 1). [Diagram 5] 4 with partial sections along the sections AA and BB and with the locking recesses. [Figure 6] 5 is a cross-sectional view taken along the same partial cross-section (cutting line) AA as in FIG. 4. [Figure 7] 5 is a cross-sectional view taken along the offset partial cross-section (cutting line) BB similar to FIG. 4. [Figure 8] Plan view Y with partial cross section (similar to Figures 6 and 7). [Figure 9] FIG. 2 is a perspective view of an example cam carrier with transmission elements. [Figure 10] FIG. 2 is a perspective view of an example cam carrier excluding the transmission elements. [Figure 11] FIG. 2 is a (partial) exploded view of an example of a cam carrier. [Figure 12] FIG. 2 is a side view of an example cam carrier with a partial cross section. [Figure 13] [Figure 14] [Figure 15] [Figure 16] [Figure 17] [Figure 18] [Figure 19] EXAMPLES

[0040] In FIG. 1, an example of a cylindrical holder (frame) 1 for optical and mechanical components, whose position can be adjusted in the direction of the optical or cylinder axis 10, is shown. The plan view of the partial section (cut-away) along the section lines AA and BB shows a cross-section of an example of sliding transmission elements G1, G2 and G3, which are fitted into a fixed sleeve 2. The sliding transmission elements G1, G2 and G3 have a cylindrical stud shape with two differently sized outer diameters. The larger diameter of each is fitted into a counterbore formed in the outer cylindrical part of the sleeve 2. The counterbore is formed in the sleeve 2 as a through hole and is provided with an inner edge for supporting the respective cylinder part with the larger diameter. The sliding transmission elements G1 and G2 are arranged with respect to each other with an angular distance W1-2 within an angular range of less than 90° on the circumference of the sleeve 2 with respect to their radii. The angular distance W1-2 between the sliding transmission elements G1 and G2 is therefore smaller than the angular distance W1-3 between the sliding transmission elements G1 and G3 and smaller than the angular distance W2-3 between the sliding transmission elements G2 and G3. In the example depicted in FIG. 1, the angle W1-2 is 28°, the angle W1-3 is 168° and the angle W2-3 is 164°. The axial distances of the cylinder parts of the sliding (transmission) elements G2 and G1 with smaller diameters guided through the through holes to the cylinder axis 10 are shown 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 (cylinder diameter) of the cylinder part of the sliding (transmission) element G1 with smaller diameters guided through the through hole is likewise greater than the outer diameter (cylinder diameter) of the cylinder part of the sliding (transmission) element G2 with smaller diameters guided through the through hole.

[0041] FIG. 2 shows a cross section along the line AA in FIG. 1. The sleeve 2 supports the cam carrier 5 so that it can rotate (around the cylinder axis 10) and can shift axially along the cylinder axis 10. The cam carrier has cam grooves N1, N2 and N3 formed on its cylindrical outer circumferential surface. The sliding transmission element G1, which fits into the cam groove N1, and the sliding transmission element G3, which fits into the cam groove N3, are arranged in the axial direction in a plane represented by a dashed line. The rotating ring 7 is shown diagrammatically and is supported on the sleeve 2 so that it can rotate but cannot shift axially. For the axial shift of the cam carrier 5, a transmission element, not shown in FIG. 2, is connected to the rotating ring 7 and engages in a linear guide, also not shown. The transmission element and the linear guide are explained in more detail below with reference to FIG. 9.

[0042] 3 shows a cross-section along the section line BB shown in FIG. 1. The section line BB has an axial offset at the cylinder axis 10. The sliding transmission element G2 is arranged axially spaced (displaced) with respect to the sliding transmission element G3. For clarity, the dashed line 17 has an axial lateral offset at the cylinder axis 10. The dashed line drawn through the sliding transmission element G3 corresponds to the dashed line 16 in FIG. 2 up to the cylinder axis 10.

[0043] 4 shows, in plan view X, an example of a cylindrical holder 1 having a bayonet coupling 3 for locking the holder 1 to a camera system (not shown). The bayonet coupling 3 has a locking recess (notch) 4 on its mounting surface for a claw-type locking. As viewed counterclockwise from the locking recess 4, an angular range between 45° and 135° is provided. The cut planes AA and BB in FIG. 4 correspond to the cut planes AA and BB in FIG. 1.

[0044] 5, in which the sliding transmission elements G1, G2 and G3 are shown in cross section and in their angular position relative to the locking recess 4. Between the locking recess 4 and the position of the sliding transmission element G1, an optical marking 15 is provided on the outer periphery of the cylindrical holder 1 counterclockwise (from the locking recess 4).

[0045] Figure 6 shows a cross-sectional view along the line AA in Figure 4. In the rotating ring 7, an optical holder 18 with a lens 19 is supported so as to be axially shiftable via a helicoid screw 20. As in Figure 2, the sliding (transmission) elements G1 and G3 are arranged in (one) plane represented by the dashed line (dotted line) 16.

[0046] Figure 7 shows a cross section along the offset partial section (cutting line) BB of Figure 4. As in Figure 2, the sliding transmission elements G2 and G3 are arranged axially offset along the dashed line (dotted line) 17.

[0047] 8 shows a plan view Y corresponding to the description of FIGS. 6 and 7 of the holder part 18 with the lens 19 and a partial section (cutaway). The partial section shows the transmission element 8 fixed to the rotating ring 7 in the linear guide 6 of the cam carrier 5. The holder part 18, shown cut away in the partial section, has an axially extending groove 21 on its cylindrical inner circumferential surface. Into the groove 21 fits a transmission element 22 fixed to the sleeve 2 for the axial shift of the holder (part) 18.

[0048] 9 shows a perspective view of an example of a cam carrier 5 with sliding transmission elements G1 and G2 arranged next to each other and depicted without (removing) the sleeve 2. The sliding transmission elements G1 and G2 shown fit into the beginning of the grooved cams N1 and N2 assigned to them. The end of the grooved cam N3 is depicted at a position axially offset with respect to the sliding transmission element G1. The sliding transmission element G3 is depicted diagrammatically partially hidden by the cam carrier 5 and is located on the outer periphery of the cam carrier 5 at the beginning of the grooved cam N3, which is not visible in the figure.

[0049] In order to clearly show the positions of the groove cams N1, N2 and N3 and the slot-like linear guide 6 in the circumference, the cam carrier 5 of FIG. 9 is depicted in FIG. 10 without the sliding transmission elements G1, G2 and G3.

[0050] FIG. 11 shows the outer circumference of the cam carrier in a developed view, which more clearly shows the shape and arrangement of the grooved cams N1, N2 and N3. The sliding transmission elements G1, G2 and G3 are respectively depicted in positions which characterize the start regions of the respectively assigned grooved cams N1, N2 and N3. The axial stroke or hub 12 of the cam carrier 5 is formed by a region 13 which starts from the start of the grooved cams N1, N2 and N3 and has an axial upslope. The upslope region 13 is joined by a region 14 which has no upslope and no axial stroke up to the end of the grooved cam. The sliding transmission element G1 is arranged in the same axial plane as the sliding transmission element G3. In FIG. 11, the sliding transmission elements G1 and G3 are therefore arranged on the same dashed line [solid line] which runs parallel to the edge of the cam carrier 5. The start end regions of the assigned grooved cams N1 and N3 are configured to be open (open) in the axial direction against the edge of the cam carrier 5, and the sliding transmission element G1 has a larger diameter (tube diameter) than the sliding transmission element G3. The sliding transmission element G1 also has a larger diameter than the sliding transmission element G2, so that the width of the assigned grooved cam N1 (to the sliding transmission element G1) is also larger than the width of the grooved cam N2 of the sliding transmission element G2. In its start end region, the grooved cam N1 extends without overlapping up to the start end region of the grooved cam N2. In order to overlap the grooved cams N1 and N2 in the axially upwardly inclined region 13, the thinner grooved cam N2 is formed deeper in the cam carrier 5, and the wider grooved cam N1 is formed shallower. The grooved cam depth of the wider but smaller grooved cam N1 corresponds to the larger radial distance 11 of the first sliding transmission element G1 depicted and described in FIG. 1. The groove cam depth of the narrower and deeper groove cam N2 corresponds to the smaller radial distance 9 of the sliding transmission element G2 depicted and explained with respect to Fig. 1. The axial offset between the sliding transmission elements G1 and G2 corresponds to the radius of the sliding transmission element G2 in Fig. 11. In this way, in the uphill region 13, there are (are) narrow support edges for the wider groove cam N1 on the left and right (in the width direction) of the deeper groove cam N2.In combination with the grooved cam N2, which is deeper but narrower than the grooved cam N1, the two elements can overlap without interference, while the sliding transmission element G1 is guided reliably in the grooved cam N1 and the narrower sliding transmission element G2 in the grooved cam N2. Advantageously, after the transition from the region with axial upslope 13 to the region without upslope 14 for the wider grooved cam N1, there is a radially wide lateral support edge of the sliding transmission element G2 for the radial guidance and additionally coaxial alignment of the cam carrier 5 in the sleeve 2 or holder 1. In the region without axial upslope 14, the cam carrier no longer shifts axially but only rotates in its position. The region at the end of the grooved cam N2 does not overlap with the grooved cam N1 and is axially offset by the magnitude of the axial stroke 12 from the beginning of the grooved cam N3.

[0051] In FIG. 12, an example of the cam carrier 5 is shown in a side view on the cylinder outer circumference. In the region with an upward slope 13 shown on the upper side of the cylinder axis 10 (on the paper), the start region of the wide grooved cam N1 is shown next to the end of the narrow grooved cam N3. The start region of the grooved cam N1 extends without overlapping with the grooved cam N2 in the cam carrier 5 and is also smaller in depth than the narrower grooved cam N2, but is wider than the connected (communicated) and overlapping grooved cam N2. In the lower region of FIG. 12, an example of a partial cross section (cutaway) is shown as a cross section in the region without an upward slope 14 of the grooved cams N1 and N2. The sliding (transmission) element G2, not shown, penetrates completely to the groove bottom of the grooved cam N2, while the groove bottom for the sliding (transmission) element G1 with a larger diameter is formed by the grooved cam edge N1, the width of which corresponds to half the grooved cam N2.

[0052] An example of an alternative cylindrical holder based on the same basic idea of ​​the invention is the subject of claim 15, the same problem being solved by the features of this claim, advantageous configurations and developments being the subject of the dependent claims referring back to claim 15.

[0053] In the cylindrical holder 101, the grooved cams N'1, N'2, N'3 assigned to the sliding transmission elements G101, G102, G103 in the cam carrier 102 are advantageously configured as cylinder cam screws (grooved cams arranged in a screw-like manner) and formed on the inner circumferential surface of the cam carrier 102. The axial distances of the groove bottoms from the cylinder axis 110 are shown as radial distances 109, 111 and are adapted to the outwardly directed axial / radial distances of the respective sliding transmission elements G101, G102.

[0054] In one advantageous embodiment of the cylindrical holder 101, the grooved cams N'1, N'2, N'3 have an ascending gradient in the axial direction adapted to a predetermined axial stroke of the sleeve 105, in which case the grooved cams N'1, N'2, N'3 are configured linearly or non-linearly.

[0055] In one example of a cylindrical holder 101 further configured according to the invention, the grooved cams N'1, N'2 assigned to the first sliding transmission element G101 and the second sliding transmission element G102, respectively, and having different depths or different radial distances 109, 111 at least partially overlap.

[0056] Furthermore, the groove cams in the cylindrical holder 101 advantageously have a first region 13 having an upward slope and causing an axial stroke 12 of the sleeve 105 and a second region 14 having no upward slope and not causing an axial stroke 12.

[0057] In a further advantageous embodiment, the fixed position cam carrier 102 is provided with a bayonet coupling having a locking recess for locking to a camera system not described further, and the first sliding transmission element G101 and the second sliding transmission element G102 are arranged at a distance from the locking recess within a certain angular range.

[0058] Particularly advantageously, the distance between the first sliding transmission element G101 and the second sliding transmission element G102 as viewed counterclockwise from the locking recess 4 to the bayonet coupling portion 3 is in the angular range of 45° to 135°.

[0059] In one example of a cylindrical holder 101 configured according to the present invention, the position-fixed cam carrier 102 is provided with a helicoidal threaded sleeve 18 which is operatively connected to a rotating ring 107 and has a slotted linear guide for axial shifting of a further optical element 19.

[0060] In an advantageous embodiment, the axial shift (stroke) 12 of the helicoidal threaded sleeve 18 can be configured to be greater or smaller than the axial shift (stroke) 12 of the sleeve 105, in which case a further transmission element 22 is provided which fits into a slotted linear guide 21 of the helicoidal threaded sleeve 18 to prevent rotation and is connected to the positionally fixed cam carrier 102. In this way, a speed reduction or speed increase (i.e. a speed change) between the axially shiftable sleeve 105 and the helicoidal threaded sleeve 18 with, for example, a focusing element of an objective lens can be realized.

[0061] In order to ensure a particularly sensitive (highly accurate) adjustment of the focusing via the focusing element, the rotation angle of the rotating ring 107 is particularly advantageously between 100° and a maximum of 185°.

[0062] Embodiments of the inventive cylindrical holder according to claim 15 are illustrated diagrammatically in the drawings with alternative features which operate similarly and are explained in more detail with the aid of figures 13 to 19.

[0063] In Fig. 13, an example of an alternative cylindrical holder 101 for optical and mechanical structural elements, the position of which can be adjusted in the direction of the optical or cylinder axis 110, is described. The plan view in partial section along the section lines CC and DD shows a cross-section of the sliding transmission elements G101, G102 and G103, which are fitted into the position-fixed cam carrier 102. The sliding transmission elements G101, G102 and G103 (respectively) have a cylindrical stud shape (short cylindrical shape) with two different sizes of outer diameter. The respective larger diameter parts are fitted into (deep) counterbore holes formed in the inner circumference of the cylinder of the cam carrier 102. The (deep) counterbore holes are formed in the cam carrier 102 as through holes and are configured with an inner edge for supporting the respective cylinder parts with the larger diameter. The sliding transmission elements G101 and G102 are arranged relative to each other with an angular distance W'1-2 within an angular range of less than 90° on the outer circumference of the cam carrier 102 with respect to their radii. The angle between the radii of the sliding transmission elements G101 and G102 or the angular distance W'1-2 between the sliding transmission elements G101 and G102 is therefore smaller than the angular distance W'1-3 between the sliding transmission elements G101 and G103 and also smaller than the angular distance W'2-3 between the sliding transmission elements G102 and G103. In this way, the distance in the circumference of the sleeve 105 between the first sliding transmission element G101 and the second sliding transmission element G102 of the three sliding transmission elements is smaller than the respective distance in the circumference to the third sliding transmission element G103. The configuration of the present invention, which differs from the usual 120° symmetrical arrangement, can also be defined using the angles between the radius vectors or between the radii of the sliding transmission elements. In the example depicted in FIG. 13, 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 cylinder parts of the sliding (transmission) elements G101 and G102 with smaller diameters guided through the through holes to the cylinder axis 110 are shown as radial distance 109 (for G101) and radial distance 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 (cylinder diameter) of the cylinder portion of the sliding (transmission) element G102 having a smaller diameter guided through a through hole is larger than the outer diameter (cylinder diameter) of the cylinder portion of the sliding (transmission) element G101 having a smaller diameter guided through a through hole.

[0064] Figure 14 shows a cross-section along the section line DD shown in Figure 13 with an axial shift in the cylinder axis 110. The sliding transmission element G101 is arranged axially spaced apart from the sliding transmission element G103. For clarity, the dashed line 117 has an axial lateral shift in the cylinder axis 110. The dashed line drawn through the sliding transmission element G103 corresponds to the dashed line 116 in Figure 15 up to the cylinder axis 10

[0110] .

[0065] FIG. 15 shows a cross-sectional view along CC in FIG. 13. The sleeve 105 is supported on the cam carrier 102 so as to be rotatable (around the cylinder axis 110) and axially shiftable along the cylinder axis 110. The cam carrier 102 has grooved cams N'1, N'2, and N'3 formed on its cylinder inner peripheral surface. The sliding transmission element G101 [G102] that fits into the grooved cam N'1 [N'2] and the sliding transmission element G103 that fits into the grooved cam N'3 are arranged on (one) surface represented by a dashed line (dotted line) 116 in the axial direction. The rotating ring 107 is shown diagrammatically and is supported on the cam carrier 102 so as to be rotatable but not shiftable in the axial direction. For the axial shift of the sleeve 105, a transmission element 108 is connected to the rotating ring 107 and fits into a slit-shaped linear guide 106.

[0066] In Fig. 16, a cross-section of the inner circumference of the cam carrier 102 is shown, which more clearly shows the shape of the grooved cams N'1, N'2 and N'3 and their arrangement relative to one another. On the upper side (in the plane of the paper) of the cylinder axis 110, linearly rising and overlapping areas of the grooved cams N'1 and N'2 in the axial direction are shown, which cause an axial stroke of the sleeve 105, not shown in Fig. 16, when the sleeve 105 is rotated. On the lower side (in the plane of the paper) of the cylinder axis 110, the grooved cams N'1 and N'2 extend with an axial offset corresponding to the offset between the dashed line 117 in Fig. 14 and the dashed line 116 in Fig. 15. The grooved cams N'1 and N'2 extend parallel to one another in this area, but no longer extend linearly (straight line) in an axially upward direction. When the sliding transmission elements G101 and G102 (not shown) of the sleeve 105 fit into this region, axial shift of the sleeve 105 along the cylinder axis 110 inside the cam carrier 102 no longer occurs even if the sleeve 105 rotates.

[0067] 17 and 18 clearly show the geometric arrangement (structure) of the grooved cams N'1, N'2 and N'3 on the inner circumference of the cam carrier 102. The sliding transmission elements G101, G102 and G103 that fit into the grooved cams are shown in the figures only diagrammatically and without sleeves 105.

[0068] 19 shows an example of an alternative linear guide 106' formed on the sleeve 105 as a protruding addition extending parallel to the cylinder axis 110. A transmission element 108' connected to a rotating ring 107 (not shown) engages the linear guide 106' in a surrounding manner. In this way, the rotational movement performed in the rotating ring 107 can be transmitted to the sleeve 105 via the transmission element 108' and converted into an axial shift of the sleeve 105 by the operational connection between the grooved cams of the cam carrier 102 and the sliding transmission elements of the sleeve 105.

[0069] [Explanation of symbols]

[0070] 1,101 Cylindrical holder 2,105 Fixed position sleeve 3 Bayonet joint 4 Locking recess 5,102 Cam carrier 6,106 Slit-shaped linear guide 106' Linear Guide Outer 7,107 Rotating Ring 8,108 Transmission elements Rotation 9 Radial distance Sliding transmission element G2 109 Radial distance Sliding transmission element G101 10,110 Cylinder shaft 11 Radial distance sliding transmission element G1 111 Radial distance Sliding transmission element G102 12 Axial stroke 13 Grooved cam area with axial upward gradient 14 Groove cam area with no axial upward gradient 15 Optical Marking 16 Dashed line (dotted line) Surface G1 G3 116 Dashed line (dotted line) Surface G102 G103 17 Dashed line (dotted line) Axial shift G2 G3 117 Dashed line (dotted line) Axial shift G101 G103 18 Holder with helicoid screw, helicoid screw sleeve 19 Lenses 20 Helicoid screw (Screw) 21 Axially extending groove 22 Transmission element Fixed G1, G2, G3 sliding transmission elements G101, G102, G103 sliding transmission element alternative N1,N2,N3 Groove cam N'1, N'2, N'3 Groove Cam Alternative W1-2 Angle between sliding transmission elements G1 and G2 W1-3 Angle between sliding transmission elements G1 and G3 W2-3 Angle between sliding transmission elements G2 and G3 W'1-2 Angle between sliding transmission elements G101 and G102 W'1-3 Angle between sliding transmission elements G101 and G103 W'2-3 Angle between sliding transmission elements G102 and G103

Claims

1. A cylindrical holder for position-adjustable optical and mechanical structural elements, comprising: The holder has a sleeve (2) whose position is fixed relative to the holder, three sliding transmission elements distributed on the cylinder inner circumference of the sleeve (2) for operatively connecting with corresponding groove cams of a cam carrier (5) which is supported rotatably and axially shiftably in the sleeve (2) and has a slot-shaped linear guide (6), and a rotating ring (7) which is axially positionally fixed, is supported on the outer circumferential surface of the sleeve, is operable from the outside, and has at least one transmission element (8) which fits into the slot-shaped linear guide (6) of the cam carrier (5), Among the three sliding transmission elements (G1, G2, G3), an angle (W1-2) between a radius of the first sliding transmission element (G1) and a radius of the second sliding transmission element (G2) is smaller than the respective angles (W1-3, W2-3) with respect to the third sliding transmission element (G3). A cylindrical holder comprising:

2. 2. The cylindrical holder according to claim 1, The angle (W1-2) between the radius of the first sliding transmission element (G1) and the radius of the second sliding transmission element (G2) is configured to be less than 90°. A cylindrical holder comprising:

3. 3. The cylindrical holder according to claim 2, The first sliding transmission element (G1) and the third sliding transmission element (G3) are arranged on one surface 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). A cylindrical holder comprising:

4. 4. The cylindrical holder according to claim 3, the second sliding transmission element (G2) having a smaller diameter is arranged axially spaced apart from the faces of the first sliding transmission element (G1) and the third sliding transmission element (G3); A cylindrical holder comprising:

5. 5. The cylindrical holder according to claim 3, The radial distance (9) of the second sliding transmission element (G2) having a smaller diameter than the first sliding transmission element (G1) to the cylinder axis (10) is smaller than the radial distance (11) of the first sliding transmission element (G1). A cylindrical holder comprising:

6. 6. The cylindrical holder according to claim 5, the grooved cams (N1, N2, N3) assigned to the sliding transmission elements (G1, G2, G3) are configured as cylinder cam screws in the cam carrier (5) and are formed on the outer circumferential surface of the cam carrier (5); The radial distance of the groove bottom is adapted to the radial distance (9, 11) of each sliding transmission element (G2, G1). A cylindrical holder comprising:

7. 7. The cylindrical holder according to claim 6, the grooved cams (N1, N2, N3) have an ascending gradient in the axial direction adapted to a predetermined axial stroke (12) of the cam carrier (5); The grooved cams (N1, N2, N3) are configured linearly or non-linearly. A cylindrical holder comprising:

8. 8. The cylindrical holder according to claim 7, The grooved cams (N1, N2) having different depths and assigned to the first sliding transmission element (G1) and the second sliding transmission element (G2), respectively, at least partially overlap each other. A cylindrical holder comprising:

9. 9. The cylindrical holder according to claim 8, The grooved cam has a first region (13) that provides an axial stroke (12) and has an upward gradient, and a second region (14) that does not provide an axial stroke (12) and does not have an upward gradient. A cylindrical holder comprising:

10. The cylindrical holder according to any one of claims 1 to 9, the fixed sleeve (2) is provided with a bayonet connection having a locking recess for locking the same to the camera system; The first sliding transmission element and the second sliding transmission element are disposed in an angle range spaced apart from the locking recess. A cylindrical holder comprising:

11. The cylindrical holder according to claim 10, The first sliding transmission element (G1) and the second sliding transmission element (G2) are disposed in an angular range of 45° to 135° counterclockwise from the locking recess (4) when viewed toward the bayonet coupling portion. A cylindrical holder comprising:

12. 12. The cylindrical holder according to claim 11, The stationary sleeve (2) is provided with a helicoidal threaded sleeve (18) which has a slotted linear guide for the axial shifting of a further optical component (19) and is operatively connected to the rotating ring (7). A cylindrical holder comprising:

13. 13. The cylindrical holder according to claim 12, The axial shift (12) of the helicoid thread sleeve (18) is greater or less than the axial shift (12) of the cam carrier (5); A further transmission element (22) is provided which is connected to the fixed sleeve (2) and engages in a slotted linear guide (21) of the helicoid threaded sleeve (18) to prevent rotation. A cylindrical holder comprising:

14. The cylindrical holder according to any one of claims 2 to 13, The rotation angle of the rotating ring (7) is from 100° to a maximum of 185°. A cylindrical holder comprising:

15. A cylindrical holder for position-adjustable optical and mechanical structural elements, comprising: The holder comprises a cam carrier (102) whose position is fixed relative to the holder, three grooved cams (N'1, N'2, N'3) distributed on the cylinder inner circumference of the cam carrier (102) for operatively connecting with corresponding sliding transmission elements (G101, G102, G103) of a sleeve (105) having a slot-shaped linear guide (106) and supported rotatably and axially shiftably in the cam carrier (102), and a rotating ring (107) whose position is fixed in the axial direction, supported on the outer circumferential surface of the cam carrier (102), and operable from the outside, and having at least one transmission element (108) that fits into the slot-shaped linear guide (106) of the sleeve (105); The angle (W101-102) between the radius of the first sliding transmission element (G101) and the radius of the second sliding transmission element (G102) among the three sliding transmission elements (G101, G102, G103) is smaller than the respective angles (W101-103, W102-103) relative to the third sliding transmission element (G103), or the distance on the circumference of the sleeve (105) between the first sliding transmission element (G101) and the second sliding transmission element (G102) among the three sliding transmission elements (G101, G102, G103) is smaller than the respective distance on the circumference relative to the third sliding transmission element (G103). A cylindrical holder comprising:

16. 16. The cylindrical holder according to claim 15, The angle (W101-102) between the radius of the first sliding transmission element (G101) and the radius of the second sliding transmission element (G102) is configured to be less than 90°, or the distance around the circumference of the sleeve (105) between the first sliding transmission element (G101) and the second sliding transmission element (G102) is configured to be less than 25% of the entire circumference of the sleeve (105). A cylindrical holder comprising:

17. 17. The cylindrical holder according to claim 16, The second sliding transmission element (G102) and the third sliding transmission element (G103) are arranged on one surface 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). A cylindrical holder comprising:

18. 18. The cylindrical holder according to claim 17, the first sliding transmission element (G101) having a smaller diameter is arranged axially spaced apart from the faces of the second sliding transmission element (G102) and the third sliding transmission element (G103); A cylindrical holder comprising:

19. 19. The cylindrical holder according to claim 17 or 18, The radial distance (109) of the first sliding transmission element (G101), which has a smaller diameter than the second sliding transmission element (G102), to the cylinder axis (110) is greater than the radial distance (111) of the second sliding transmission element (G102). A cylindrical holder comprising:

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