Cylindrical mounting for adjustable optical and mechanical components
Patent Information
- Application Number
- EP2023723408
- Authority / Receiving Office
- EP · EP
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2022-04-22
- Filing Date
- 2023-04-21
- Publication Date
- 2025-02-26
Smart Images
Figure 1.1
Abstract
Description
[0001] Cylindrical mount for adjustable optical and mechanical components
[0002] 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 can be adjusted to various object distances, comprising a distance setting ring and a device coupled thereto for transmitting the set distance to the setting lever of a movable optical element of a split-image rangefinder arranged on the camera side. Split-image rangefinders are also known as mixed-image viewfinders, coincidence viewfinders, or colloquially rangefinders. Viewfinder cameras include, for example, cameras of the applicant's M system, which have been known for decades for their compatibility with associated lenses of various focal lengths of the M system.
[0003] In such photographic lenses, it is known to shift one or more of the imaging lenses along the optical axis in order to sharply image the subject being photographed in the camera's image-taking plane. It is also known to couple the movable optical element built into the camera's rangefinder with the movable objective lens, or rather, the lens's focus shift mechanism, via the camera's control lever. The shift mechanism in the lens is usually a worm-threaded sleeve with or without a linear guide, which can be actuated externally via an internally threaded distance setting ring.
[0004] With lenses with a normal focal length, such as a 50mm lens for 35mm format, a rotation of the focus adjustment ring limited to an angle of less than 95° causes both an axial displacement of the worm gear for focusing and a rotation of the same around the optical axis of the system. Because the adjustment lever rests against the front of the worm gear, it is thus coupled to the lens's focus shift mechanism. Visual focusing over a distance range from 0.7 m to infinity is thus possible with a coupled movement of the adjustment lever by 4.5 mm.Distance-dependent, varying adjustment paths and any nonlinearities between the axial adjustment movement of the optical imaging system required for focusing and the associated movement of the rangefinder adjustment lever are compensated for, for example, by a subsequent milling of a slope onto the end face of the worm gear sleeve, possibly as a linear or nonlinear axial curve. The mechanical complexity for this is very high, and a significant amount of labor is also required to apply the milling.
[0005] Depending on the lens design and focal length of the lens, the adjustment travel of the focus shift mechanism of the optics or the optics assembly required to focus on object distances from infinity to a close range often differs considerably, while the adjustment range in the rangefinder is mechanically limited ("calibrated") to object distances of 0.7 m to infinity due to its design, since the available adjustment travel of the adjustment lever is always 4.5 mm.
[0006] The compatibility of the lenses with the camera with regard to distance setting is achieved by converting the adjustment path of the setting lever in the rangefinder for the distance range from 0.7 m to infinity, regardless of the various adjustment paths of the focusing mechanism.
[0007] This implementation must be carried out with high precision and therefore requires considerable additional mechanical effort. Implementations based on the functional type of a lower or higher gear with multiple nested worm threads and threaded sleeves are common.
[0008] A complex lens mount of this type is known from DE 2 040227 A1. The lens mount contains several imaging lenses that can be moved along the optical axis of the system via a distance setting ring in order to sharply image an object to be recorded in the image recording plane. For this purpose, the distance setting ring is connected to an outer threaded tube designed as a worm gear as a drive device. An inner threaded tube, also designed as a worm gear, is inserted into this threaded tube and is guided in a straight line in the lens mount so that the rotation of the outer threaded tube is converted into a displacement of the inner threaded tube along the optical axis of the system. The imaging lenses are fixedly inserted into the inner threaded tube and therefore participate in this axial longitudinal displacement.A cam ring is also rotatably inserted into the inner threaded tube on the camera side, which is driven by a drive pin connected to the outer threaded tube. The cam ring rests on a shoulder screwed into the inner wall of the inner threaded tube and is held in place by a pre-screwed ring screwed onto the inner threaded tube. The drive pin is connected to the cam ring through a radial slot in the inner threaded tube. The cam ring has an axial cam on its camera-side face. A tappet rests on the axial cam via a roller, which is mounted so it can pivot about an axis perpendicular to the optical axis of the system. The tappet is coupled to the rangefinder's adjusting lever.
[0009] When the focus adjustment ring is rotated, the cam ring is axially displaced on the one hand and rotated around the optical axis of the system on the other. Both movements combined translate the relatively large axial displacement of the threaded barrel into the small tappet movement required for the adjustment of the rangefinder lever. In this way, the slope of the axial cam can compensate, to a limited extent, for focal-length-dependent, different adjustment travels and nonlinearities between the axial adjustment movement of the optical imaging system and the associated movement of the rangefinder lever.
[0010] For adjusting the adjusting lever and the focusing elements, so-called cylindrical cam threads are also known in lens construction. These threads consist of three grooved cams of a cam carrier arranged symmetrically around the circumference of a fixed sleeve and rising linearly in the axial direction. Engaging sliding transmission elements, in conjunction with a linear guide, convert a rotary movement on the distance setting ring into an axial displacement. The maximum angle of rotation available for focusing from infinity to the close-up range is limited, on the one hand, by the range of 120° between the grooved cams or sliding transmission elements, and, on the other hand, by the fact that a transmission element from the distance setting ring must also be arranged in this range to engage the linear guide of the cam carrier.
[0011] This limits the focusing accuracy, as the focus adjustment ring only has a rotation angle of less than 95° for a relatively large axial displacement of the threaded barrel of the focusing mechanism. This proves particularly disadvantageous, on the one hand, with lenses with long focal lengths, which require a large adjustment range for focusing, and on the other hand, with lenses with a large aperture, as the depth of field on the image side is reduced, thus making it impossible to compensate for focusing inaccuracies set by the operator.
[0012] It has been shown that a rotation angle of 95° just about meets the focusing accuracy requirements of a 50 mm lens in a range from 0.7 m to infinity. However, modern lens designs allow focusing at object distances closer to 0.7 m, for example, down to 0.45 m. However, these settings would require a rotation angle of approximately 175°.
[0013] However, the arrangement of the grooved cams symmetrically distributed around the circumference in an axial plane has proven effective in known cam carriers, as this prevents tilting moments and instabilities. The guideways or grooved cams have the same axial pitch. The angle of rotation of the distance adjustment ring is also limited by the start and end of the grooved cams. Small axial displacements can be achieved with a small axial pitch at a maximum angle of rotation of 95°. In this way, there is just enough cylinder surface material between the end of one grooved cam and the start of the adjacent grooved cam to ensure the mechanical stability of the cam carrier.
[0014] If larger angles of rotation are to be achieved in known 120° arrangements, this is only possible if the axial pitch of the guideways is selected so large that the beginning and end of adjacent groove curves have a sufficient axial offset. The minimum widths of the groove curves required for reliable mechanical movement do not allow for small axial displacements, such as the 4.5 mm specified for the rangefinder's adjusting lever.
[0015] EP 2 693 247 A1 discloses a cylindrical mount with a cam carrier and axially offset cam tracks, whereby the cam carrier enables a large angle of rotation. The axially offset cam tracks require a large amount of space and require a large cylinder surface area. A small axial adjustment range is not feasible. Furthermore, the cylinder material is mechanically weakened due to the multiple, closely spaced openings for the cam tracks and is unstable under axial load.
[0016] Further cylindrical mounts for optical components with cam carriers and cylindrical cam threads are known, for example, from US 2015 / 0205068 A1 and US 3,951,522. The object of the invention was to improve the disadvantages existing in connection with rangefinder cameras in lenses with regard to the conversion of the adjustment paths for the focusing elements to the adjustment path of a rangefinder, to increase the adjustment accuracy of the axial positioning of the focusing elements in lenses, in particular with large displacement paths of the same, and at the same time to ensure the transmission accuracy of a coupling to the adjusting lever of a camera rangefinder and its predetermined adjustment path required for focusing.A further object of the invention was to realize a focusability to object distances shorter than 0.7 m, namely from infinity down to 0.4 m, in a lens with rotary axial conversion for actuating the adjusting lever of a camera rangefinder.
[0017] This object is achieved by a cylindrical mount for adjustable optical and mechanical components having the features of claim 1; advantageous embodiments and further developments are the subject of the subclaims.
[0018] In a cylindrical socket according to the invention, a sleeve is provided which is fixed relative to a socket and which has three sliding transmission elements distributed along its inner cylindrical circumference for operative connection with three corresponding grooved curves of a cam carrier rotatably mounted in the sleeve. Each of the exactly three sliding transmission elements is assigned exactly one grooved curve. The sliding transmission elements have a shape adapted to the grooved curves, in particular as plastic round sleeves. For easy assembly, the sliding transmission elements have a cylindrical pin shape with two different outer diameters. The larger diameter in each case serves for easy insertion into drill blind holes which are provided on the outer cylindrical circumference of the sleeve as through holes with an inner edge for supporting the cylindrical part with the larger diameter.The smaller diameter is guided through the through hole into the grooved curve, adapted to the width of the grooved curve and advantageously designed as a hollow cylinder. The diameter of the smaller cylinder part engaging in the grooved curves can have a slight oversize compared to the respective groove width to compensate for any fluctuations in the groove width of the grooved curves, but precise manufacturing is advantageous. A cylindrical ring that can be actuated from the outside and is fixed in the axial direction is rotatably mounted on the outer surface of the sleeve. At least one transmission element, e.g. in the form of a tab, is provided on this rotating ring for engagement in a corresponding slotted guide acting in the axial direction.For this purpose, the slotted guide is provided on the cam carrier as a straight guide parallel to the cylinder axis, preferably on the outer circumference, so that the transmission element attached to the rotating ring can easily engage the slotted guide and establish the operative connection. Rotation of the rotating ring then causes both rotation and axial displacement of the cam carrier within the sleeve.
[0019] The same functionality is of course also ensured if the fixed sleeve is designed as a cam carrier with grooved cams formed on its inner cylindrical circumference, and a cylindrical sleeve axially displaceably mounted in the cam carrier has the sliding transmission elements on its outer circumference for operative connection with the corresponding grooved cams of the cam carrier. In this case, the linear guide must be incorporated in the cylindrical sleeve with the sliding transmission elements / sliding sleeves, while the rotating ring is mounted axially fixed on the fixed cam carrier. This embodiment is the subject of the subordinate claim 15; advantageous refinements are set out in the subclaims.
[0020] According to the invention, the angle between the radius of a first and a second of the three sliding transmission elements is smaller than their respective angle to the third sliding transmission element. In this way, on the one hand, a rotation angle of 120°, which is otherwise usual or only possible on the rotating ring, is increased, and an inventive design of the cam tracks or grooved cams is enabled. The basic idea of the invention is, on the one hand, to create space in the cylindrical mount for an increased angle of rotation of the rotating ring in order to increase the axial adjustment accuracy of optical and mechanical components slidably mounted in the mount and, on the other hand, to enable the rotational-axial conversion of a small axial stroke of the cam carrier caused by the rotation of the rotating ring and the slot-shaped straight guide.
[0021] For this purpose, it is particularly advantageous to arrange two of the three sliding transmission elements at a close radius angle of less than 90° to one another. To avoid mechanical instabilities and tilting moments, the third sliding transmission element is arranged diametrically opposite the first and second in an angular range on the circumference. Surprisingly, it has been shown that this special inventive arrangement of the sliding transmission elements on the circumference does not cause instabilities or tilting moments, and in this way, a rotation angle of the rotating ring of greater than 100°, up to a maximum of 185°, can be achieved. Grooved curves can then be incorporated into the cam carrier. These have a slight axial pitch but at the same time have a developed length greater than 1 / 3 of the circumference of the cam carrier.
[0022] Further advantageously, the first and third sliding transmission elements are arranged in the same plane in the axial direction, and the diameter of the second sliding transmission element is smaller than that of the adjacent first sliding transmission element. In this way, while simultaneously ensuring uninterrupted guidance of all sliding sleeves in their associated groove curves, overlapping of the two groove curves for the first and second sliding sleeves, which differ in width, is possible.
[0023] In a further embodiment of the invention, the second sliding transmission element with a smaller diameter is arranged axially offset from the plane of the first and third sliding transmission elements. In this case, the grooved curve associated with the second sliding transmission element can have an axial offset, preferably in the direction of the pitch of the other two grooved curves. In this way, it is possible to at least partially superimpose the narrower grooved curve of the second sliding transmission element on the wider grooved curve of the first sliding transmission element in order to keep the installation space required for the desired large angle of rotation and any additional linear guides required on the cam carrier free.
[0024] To ensure the most secure, independent, and uninterrupted guidance of the sliding sleeves of the first and second sliding transmission elements in the two partially overlapping groove curves, the radius distance of the first sliding transmission element from the cylinder axis is particularly advantageously greater than the radius distance of the second. A key feature of the invention is that the radius distances of the two sliding transmission elements, which are arranged close to one another within a narrow angular range and differ in the diameter of the sliding sleeves, differ. Preferably, the radius distance of the sliding transmission element with the smaller diameter sleeve is always smaller than the radius distance of the sliding transmission element with the larger diameter sleeve.In order to make optimal use of the limited space available for the grooved curves on the cylinder surface, the third sliding element, which is arranged opposite the other two on the circumference, has a small diameter, e.g. corresponding to the diameter of the smaller of the first or second sleeve. The space required for the width of the grooved curve of the third sliding transmission element is reduced in this way, so that there is no overlap with the partially overlapping grooved curves of the first and second sliding transmission elements. In this way, it is particularly advantageous for one end of the grooved curve of the third sliding transmission element to be axially offset on the cam carrier up to a start of the grooved curve of the second sliding transmission element and to extend further on the circumference than a start of the grooved curve of the first sliding transmission element.
[0025] In a further embodiment of the invention, the grooved cams assigned to the sliding transmission elements are incorporated into the outer surface of the cam carrier and designed as a so-called cylindrical cam thread. The radius distance of the groove base of the grooved cams is slidably adapted to the radius distance of the respective sliding transmission element. As already explained, the sliding transmission elements inserted into the sleeve have a cylindrical pin shape with two different outer diameters for easy assembly, with the larger diameter serving to ensure easy and centered insertion into the blind holes of the sleeve. In the radial direction, the penetration depth of the smaller diameter of the sliding elements into the grooved cams can advantageously center the cam carrier.In this way, in addition to the axially displaceable sliding bearing of the cam carrier in the fixed sleeve, the cam carrier is further guided, effectively preventing any possible wobbling of the axis of the cam carrier around the axis of the socket or sleeve. Essential to this function of the invention is that the grooved cams at least partially have a groove bottom or at least a groove bottom edge and do not consist of open curves that penetrate the cylindrical surface of the cam carrier and thereby form a slot.
[0026] Particularly advantageously, the grooved cams have a pitch running axially along the outer circumference, which is adapted to a predetermined or desired axial stroke of the cam carrier. Due to the aforementioned special design according to the invention, grooved cams with linear or non-linear running are possible.
[0027] Furthermore, the grooved curves of different depths assigned to the first and second sliding transmission elements are advantageously at least partially superimposed. The thinner grooved curve is inserted deeper into the curve carrier, and the wider one is shallower.
[0028] In a further embodiment of the invention, the grooved cams have a first region with a gradient which causes an axial travel, which, as the grooved cam progresses on the circumference of the cam carrier, merges into a second region without a gradient. This region does not cause any axial travel, despite an angular adjustment on the rotating ring. Advantageously, the axial travel of the cam carrier created by the region with a gradient is adapted to the maximum adjustment travel of the adjusting lever in the camera's rangefinder and amounts to 4.5 mm. In accordance with the required compatibility of a lens with a rangefinder camera mentioned in the introduction to the description, the axial travel created by the gradient corresponds in this way to the maximum distance setting range of 0.7 m to infinity in the camera's rangefinder.At the transition point from the area with a gradient to the area without a gradient, a haptic indicator can advantageously be provided to show the camera user that the close-up limit of focusing via the rangefinder has been reached. The haptic indicator can be formed by a spring-loaded detent pin which runs over a tactile ramp at the transition point from the area with a gradient to the area without a gradient. In this way, it is possible to show a user that further focusing of the focusing element is no longer possible using the optical rangefinder integrated in the camera, but is only possible using alternative means. For example, digital cameras can use an electronic viewfinder (EVF), via which close-range focusing between 0.7 m and, for example, 0.45 m must then be carried out.The angle of rotation of the area without a gradient is then advantageously used for extended close-range focusing of less than 0.7 m. The curve section without a gradient in this case advantageously corresponds to a close-up focusing range of 0.7 m to 0.4 m. Lenses with an optically possible maximum focusing range of 0.4 m or less to infinity were previously only adjustable in the range 0.7 m to infinity due to compatibility restrictions caused by the rangefinder camera. With lenses equipped with the invention, focusing in an extended close-up range is also possible. For use of the cylindrical mount according to the invention on a camera, preferably a rangefinder camera, a bayonet connection is provided on the fixed sleeve of the lens for locking into the camera system.For angle-oriented adjustment to a camera lens mount, the lens has an optical marking on its outer surface, which is arranged on the circumference, as seen in the direction of adjustment, at a distance from a locking recess in the front face of the bayonet connection. Advantageously, the first and second sliding transmission elements are provided at an angular distance from the locking recess such that, viewed in the axial direction of the camera, they are arranged in the area of the rangefinder adjustment lever, advantageously to the left and right.
[0029] Particularly advantageously, the first and second sliding transmission elements are arranged at an angle of 28° to each other, or both are spaced counterclockwise from the locking recess at an angle of 45° to 135° when viewed from the bayonet. This ensures a stable contact with the adjusting lever of the camera's rangefinder and a play-free transmission of the axial movement of the cam carrier to the adjusting lever, despite the asymmetrical distribution of the three sliding transmission elements on the cylinder circumference of the cam carrier.
[0030] In a further embodiment of the invention, a worm-thread sleeve with a slotted straight guide is arranged on the fixed sleeve for the axial displacement of another optical component. The worm-thread sleeve is operatively connected to the rotating ring, so that rotation is converted into an axial displacement movement of the other optical component. The operative connection to the worm-thread sleeve can advantageously be achieved by an internal worm thread formed on the inside of the rotating ring, while a cylindrical inner sleeve has a corresponding external worm thread that meshes with the internal worm thread of the rotating ring. To prevent rotation, the cylindrical inner sleeve has a slotted straight guide into which a transmission element in the form of a tab engages and is connected to the fixed sleeve of the cylindrical mount.In this way, a rotary movement of the rotating ring is converted into a linear movement of the cylindrical inner sleeve. The cylindrical inner sleeve can advantageously be used to axially displace a focusing element or so-called floating element of a lens. An advantage for the optical calculation of the lens is that the pitch of the worm thread can be adjusted to achieve a desired focusing accuracy depending on the large angle of rotation of the rotating ring provided by the invention, independent of the axial displacement specified for moving the adjusting lever of a rangefinder.
[0031] Embodiments of the cylindrical socket according to the invention are shown schematically in the drawing and are described in more detail below with reference to the figures.
[0032] Show
[0033] Fig. 1 a cylindrical socket seen in axial direction with cutouts (section AA and section BB)
[0034] Fig. 2 a sectional view along the outbreak AA from Fig. 1
[0035] Fig. 3 a sectional view along the offset cutout BB from Fig. 1 Fig. 4 a plan view X of a cylindrical socket with bayonet connection (section AA and section BB as Fig. 1)
[0036] Fig. 5 a top view X as Fig. 4 with cutouts along AA and BB and locking recess
[0037] Fig. 6 a sectional view along the outbreak AA as Fig. 4
[0038] Fig. 7 a sectional view along the offset breakout BB as Fig. 4
[0039] Fig. 8 a top view Y (as Fig. 6 and 7) with cutout
[0040] Fig. 9 a curve carrier perspective view with transmission elements
[0041] Fig. 10 a curve carrier perspective view without transmission elements
[0042] Fig. 11 Development of a cam carrier
[0043] Fig. 12 side view of the curve support with cutout
[0044] Figure 1 shows a cylindrical mount 1 for optical and mechanical components that can be adjusted in the direction of an optical or cylinder axis 10. The top view of cutouts along section lines AA and BB show sectional views of sliding transmission elements G1, G2 and G3 that are inserted into a stationary sleeve 2. The sliding transmission elements G1, G2 and G3 have a cylindrical pin shape with two different outer diameters. The larger diameter in each case is inserted into a blind hole that is made on the outer cylindrical circumference of the sleeve 2. The blind holes are made as through holes in the sleeve 2 and are designed with an inner edge to support the respective cylindrical part with a larger diameter. The sliding transmission elements G1 and G2 are arranged with respect to their radii on the circumference of the sleeve 2 in an angular range of less than 90° with an angular distance W1-2 from one another.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 also smaller than the angular distance W2-3 between the sliding transmission elements G2 and G3. In the example shown in Figure 1, the angle W1-2 is 28°, the angle W1-3 is 168°, and the angle W2-3 is 164°. The axial distance from the cylinder axis 10 of the cylinder parts of the sliding elements G2 and G1 with smaller diameters, which are guided through the through hole, is referred to as radius distance 9 and 11. The radius distance 11 of the first sliding transmission element G1 is greater than the radius distance 9 of the second sliding transmission element G2. Correspondingly, the outer diameter of the smaller diameter cylinder part of the sliding element G1 guided through the through hole is also larger than the outer diameter of the smaller diameter cylinder part of the sliding element G2 guided through the through hole.
[0045] Figure 2 shows a sectional view along AA from Figure 1. A cam carrier 5 is mounted in the sleeve 2 so as to be rotatable and axially displaceable along a cylinder axis 10. The cam carrier has grooved curves N1, N2 and N3 incorporated into its outer cylinder surface. The sliding transmission element G1 engaging in the grooved curve N1 and the sliding transmission element G3 engaging in the grooved curve N3 are arranged in the axial direction in a plane, indicated by the dashed line 16. A rotating ring 7 is schematically shown mounted on the sleeve 2 so as to be rotatable and axially non-displaceable. For the axial displacement of the cam carrier 5, a transmission element (not shown in Figure 2) is fastened to the rotating ring 7 and engages in a straight guide (likewise not shown). The transmission element and straight guide are described in more detail below in Figure 9.
[0046] Figure 3 shows a sectional view along section line BB sketched in Figure 1, which has an axial offset at the cylinder axis 10. The sliding transmission element G2 is arranged at an axial distance from the sliding transmission element G3. For clarity, the dashed line 17 at the cylinder axis 10 has a lateral offset in the axial direction. The dashed line passing through the sliding transmission element G3 corresponds to line 16 in Figure 2 up to the cylinder axis 10.
[0047] Figure 4 shows a cylindrical mount 1 with a bayonet connection 3 for locking the mount 1 to a camera system (not shown) in a top view X. The bayonet connection 3 has a locking recess 4 in its support surface for locking. Viewed counterclockwise from the locking recess 4, an angular range between 45° and 135° is provided. The sectional planes AA and BB in Figure 4 correspond to those in Figure 1.
[0048] This is illustrated by the cutouts in Figure 5, in which the sliding transmission elements G1, G2, and G3 are shown in cross-section and their angular position relative to the locking recess 4. An optical marking 15 is provided on the outside of the cylindrical socket 1, running counterclockwise between the locking recess 4 and the position of the sliding transmission element G1.
[0049] Figure 6 shows a sectional view along line AA of Figure 4. An optical mount 18 with a lens 19 is mounted in the rotating ring 7, axially displaceably via a worm thread 20. Similar to Figure 2, the sliding elements G1 and G3 are arranged in a plane represented by the dashed line 16. Figure 7 shows a cross-section along the offset cutout BB of Figure 4. Similar to Figure 2, the sliding transmission elements G2 and G3 are arranged axially offset along the dashed line 17.
[0050] Figure 8 shows a plan view Y corresponding to the illustrations in Figures 6 and 7 of the lens 19 and the mount part 18 with a cutout. The cutout shows the transmission element 8, which is attached to the rotating ring 7, in the straight guide 6 of the cam carrier 5. The mount part 18, shown in section in the cutout, has an axially extending groove 21 on its inner cylindrical surface, into which a transmission element 22, attached to the sleeve 2, engages for axially displacing the mount 18.
[0051] Figure 9 shows a perspective view of a cam carrier 5 with sliding transmission elements G1 and G2 arranged side by side and shown without a sleeve 2, which engage in the beginning of their associated grooved curves N1 and N2. The end of the grooved curve N3 is shown axially offset from the sliding transmission element G1. The sliding transmission element G3 is shown schematically, partially concealed by the cam carrier 5, and is located on the outside of the cam carrier 5 at the beginning of the grooved curve N3, which is not visible here.
[0052] To clarify the positions of the groove curves N1, N2 and N3 and the slot-shaped straight guide 6 on the circumference, the curve carrier 5 from Figure 9 is shown in Figure 10 without the sliding transmission element G1, G2 and G3.
[0053] Figure 11 shows the outside of the cam carrier in a developed view, which further clarifies the design and positioning of the grooved curves N1, N2 and N3. The sliding transmission elements G1, G2 and G3 are each shown at a position which marks the starting area of the respective associated grooved curves N1, N2 and N3. An axial stroke 12 of the cam carrier 5 is formed by the area of the grooved curves N1, N2 and N3 starting from the beginning with an axial pitch 13, which is followed by the area without a pitch 14 and without axial stroke up to the end of the grooved curves. The sliding transmission element G1 is arranged in the same axial plane as the sliding transmission element G3. In Figure 11, the sliding transmission elements G1 and G3 are therefore arranged on the same dashed line running parallel to the edge of the cam carrier 5.The initial area of the associated groove curves N1 and N3 is open in the axial direction towards the edge of the curve carrier 5, the sliding transmission element G1 has a larger 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 associated groove curve N1 is greater than the width of the groove curve N2 of the sliding transmission element G2. The groove curve N1 runs in its initial area up to the initial area of the groove curve N2 without overlap. To overlap the groove curves N1 and N2 in the area with axial pitch 13, the thinner groove curve N2 is inserted deeper in the curve carrier 5 and the wider groove curve N1 is flatter. The groove curve depth of the wider and shallower shaped groove curve N1 corresponds to the larger radius distance 11 of the first sliding transmission element G1 shown and described in Figure 1.The groove curve depth of the narrower and deeper groove curve N2 corresponds to the smaller radius distance 9 of the sliding transmission element G2 shown and described in Figure 1. The axial offset between the sliding transmission elements G1 and G2 corresponds to the radius of the sliding transmission element G2 in Figure 11. In this way, a narrow support edge for the wider groove curve N1 remains in the area with gradient 13 to the left and right of the deeper groove curve N2. In conjunction with the groove curve N2, which is deeper but narrower than the groove curve N1, the two can overlap without interference, while the sliding transmission element G1 is securely guided in the groove curve N1 and the narrower sliding transmission element G2 is securely guided in the groove curve N2.Advantageously, after the transition from the area with axial pitch 13 to the area without pitch 14 for the wider grooved curve N1, a lateral support edge of the width of the radius of the sliding transmission element G2 remains for radial guidance and additional coaxial alignment of the cam carrier 5 in the sleeve 2 or in the socket 1. In the area without axial pitch 14, the cam carrier no longer moves axially but only rotates in place. The area at the end of the grooved curve N2 is arranged axially offset from the beginning of the grooved curve N3 by the amount of the axial stroke 12, without overlapping with the grooved curve N1.
[0054] Figure 12 shows a cam carrier 5 in a side view of the cylinder outer surface. In the area shown above the cylinder axis 10 with a gradient 13, the starting area of the wide groove curve N1 is shown next to the end of the narrow groove curve N3. The starting area of the groove curve N1 runs without overlapping with the groove curve N2 in the cam carrier 5 in relation to the likewise narrower groove curve N2, less deep, but wider than the adjoining and superimposed groove curve N2. The lower area of Figure 12 shows a cutout as a sectional view in the area without a gradient 14 of the groove curves N1 and N2. The sliding element G2 (not shown) is fully immersed down to the groove base of the groove curve N2, while the groove base for the sliding element G1, which has a wider diameter, is formed from a groove curve edge N1, the width of which corresponds to half of the groove curve N2.An alternative cylindrical mount making use of the same inventive concept is the subject of claim 15, wherein the same object is achieved with the features of this claim and advantageous embodiments and further developments are the subject of the subclaims which refer back to claim 15.
[0055] In the cylindrical socket 101, the groove curves N'1, N'2, N'3 assigned to the sliding transmission elements G101, G102, G103 in the cam carrier 102 are advantageously designed as cylindrical cam threads and introduced into the inner surface of the cam carrier 102. The axial distance of the groove bottom from the cylinder axis 110 is referred to as the radius distance 109, 111 and is adapted to the outwardly facing axial distance / radius distance of the respective sliding transmission element G101, G102.
[0056] In an advantageous embodiment of the cylindrical socket 101, the groove curves N'1, N'2, N'3 have a pitch adapted in the axial direction to a predetermined axial stroke of the sleeve 105, wherein the groove curves N'1, N'2, N'3 are designed to be linear or non-linear.
[0057] In a cylindrical socket 101 further designed according to the invention, the groove curves N'1, N'2 of different depths or different radius distances 109, 111 assigned to the first G101 and second G102 sliding transmission elements overlap at least partially.
[0058] Furthermore, the grooved curves in the cylindrical mount 101 can advantageously have a first region with a pitch 13, which causes an axial stroke 12 of the sleeve 105, and a second region without a pitch 14, which does not cause an axial stroke 12. In a further advantageous embodiment, a bayonet connection with a locking recess for locking to a camera system (not further described) is provided on the fixed curve carrier 102, and the first and second sliding transmission elements G101, G102 are arranged in an angular range spaced from the locking recess.
[0059] Particularly advantageous is the arrangement of the first and second sliding transmission elements G101, G102, spaced counterclockwise from the locking recess 4 to the bayonet connection 3, in an angular range of 45° to 135°.
[0060] In a cylindrical mount 101 designed according to the invention, a worm thread sleeve 18 with a slot-shaped straight guide for the axial displacement of a further optical component 19 is arranged on the fixed cam carrier 102 and is in operative connection with the rotating ring 107.
[0061] Advantageously, the axial displacement path 12 of the worm-thread sleeve 18 can be configured to be greater or smaller than the axial displacement path 12 of the sleeve 105, wherein a further transmission element 22 connected to the stationary cam carrier 102 is provided, engaging in the slot-shaped straight guide 21 of the worm-thread sleeve 18 to prevent rotation. In this way, a reduction or transmission ratio can be realized between the axially displaceable sleeve 105 and the worm-thread sleeve 18, for example, with a focusing element of an objective.
[0062] Particularly advantageously, the angle of rotation of the rotating ring 107 is between 100° and a maximum of 185° in order to ensure a particularly sensitive adjustment of the focus via the focusing element.
[0063] Embodiments of the cylindrical socket according to the invention according to claim 15 are shown schematically in the drawing using equivalent alternative features and are described in more detail with reference to Figures 13 to 19.
[0064] Figure 13 shows an alternative cylindrical mount 101 for optical and mechanical components adjustable in the direction of an optical or cylinder axis 110. The top view of cutouts along section lines CC and DD show sectional views of sliding transmission elements G101, G102 and G103 that are inserted into a stationary cam support 102. The sliding transmission elements G101, G102 and G103 have a cylindrical pin shape with two different outer diameters. The larger diameter in each case is inserted into a blind hole that is provided on the inner cylindrical circumference of the cam support 102. The blind holes are provided as through holes in the cam support 102 and are designed with an inner edge for supporting the respective cylindrical part with a larger diameter.The sliding transmission elements G101 and G102 are arranged at an angular distance W'1-2 from one another, based on their radii, on the outer circumference of the cam carrier 102. 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 thus 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 on the circumference of the sleeve 105 between the first G101 and the second G102 of the three sliding transmission elements is smaller than their respective distance on the circumference to the third sliding transmission element G103.The inventive design, which deviates from the usual 120° symmetrical arrangements, can also be defined based on the angle between the radius vectors or angles between the radii of the sliding transmission elements. In the example shown in Figure 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 distance from the cylinder axis 110 of the smaller-diameter cylinder parts of the sliding elements G101 and G102 guided through the through holes is designated as radius distance 109 (for G101) and 111 (for G102). The radius distance 111 of the second sliding transmission element G102 is smaller than the radius distance 109 of the first sliding transmission element G101. The outer diameter of the smaller diameter cylinder part of the sliding element G102 guided through the through hole is larger than the outer diameter of the smaller diameter cylinder part of the sliding element G101 guided through the through hole.
[0065] Figure 14 shows a sectional view along section line DD sketched in Figure 13, which has an axial offset at the cylinder axis 110. The sliding transmission element G101 is arranged at an axial distance from the sliding transmission element G103. For clarity, the line I in line 117 has a lateral offset in the axial direction at the cylinder axis 110. The dashed line passing through the sliding transmission element G103 corresponds to the dashed line 116 in Figure 15 up to the cylinder axis 10.
[0066] Figure 15 shows a sectional view along CC from Figure 13. In the cam carrier 102, a sleeve 105 is mounted so as to be rotatable and axially displaceable along a cylinder axis 110. The cam carrier 102 has grooved curves N'1, N'2 and N'3 incorporated in its inner cylinder surface. The sliding transmission element G101 engaging in the grooved curve N'1 and the sliding transmission element G103 engaging in the grooved curve N'3 are arranged in the axial direction in a plane, indicated by the dashed line 116. A rotating ring 107 is schematically shown mounted on the cam carrier 102 so as to be rotatable and axially non-displaceable. For the axial displacement of the sleeve 105, a transmission element 108 is fastened to the rotating ring 107 and engages in a slot-shaped straight guide 106.
[0067] Figure 16 shows a sectional view of the inside of the cam carrier 102, which further clarifies the design and positioning of the groove curves N'1, N'2 and N'3 relative to one another.
[0068] Above the cylinder axis 110, overlapping, axially linearly rising regions of the grooved curves N'1 and N'2 are shown, which cause an axial stroke of the sleeve 105 when the sleeve 105 (not shown in Figure 16) rotates. Below the cylinder axis 110, the grooved curves N'1 and N'2 run with an axial offset that corresponds to the offset between dashed line 117 in Figure 14 and dashed line 116 in Figure 15. However, the grooved curves N'1 and N'2 run parallel to one another in this region and no longer rise linearly axially relative to one another. If the sliding transmission elements G101 and G102 of the sleeve 105 (not shown) engage in this region, there is no longer any axial displacement of the sleeve 105 along the cylinder axis 110 within the cam carrier 102, despite the rotation of the sleeve 105.
[0069] The perspective views in Figures 17 and 18 illustrate the geometric arrangement of the grooved curves N'1, N'2 and N'3 on the inner circumference of the curve carrier 102. The sliding transmission elements G101, G102 and G103 engaging in the grooved curves are shown schematically and without the sleeve 105.
[0070] Figure 19 shows an alternative linear guide 106', which is designed as a raised formation on the sleeve 105 running parallel to the cylinder axis 110. The transmission element 108', which is attached to the rotating ring 107 (not shown), engages around the linear guide 106'. In this way, a rotary movement performed on the rotating ring 107 can be transmitted to the sleeve 105 via the transmission element 108' and, due to the operative connection between the grooved curves of the cam carrier 102 and the sliding transmission elements of the sleeve 105, can be converted into an axial displacement of the sleeve 105.
[0071] List of reference symbols
[0072] 1 , 101 Cylindrical version
[0073] 2, 105 fixed sleeve
[0074] 3 bayonet connection
[0075] 4 locking recess
[0076] 5, 102 Curve carrier
[0077] 6, 106 slot-shaped straight guide
[0078] 106' Straight guide outside
[0079] 7, 107 rotating ring
[0080] 8, 108 Transmission element rotating
[0081] 9 Radius distance sliding transmission element G2
[0082] 109 Radius distance sliding transmission element G101
[0083] 10, 110 cylinder axis
[0084] 11 Radius distance sliding transmission element G1
[0085] 111 Radius distance sliding transmission element G102
[0086] 12 axial stroke
[0087] 13 Groove curve area with axial pitch
[0088] 14 Groove curve area without axial pitch
[0089] 15 optical marking
[0090] 16 Dashed line level G1 G3
[0091] 116 Dashed line plane G102 G103 17 Dashed line axial offset G2 G3
[0092] 117 Dashed line axial offset G101 G103
[0093] 18 Socket with worm thread, worm thread sleeve
[0094] 19 lens
[0095] 20 worm threads
[0096] 21 axial groove
[0097] 22 Transmission element fixed
[0098] G1, G2, G3 sliding transmission element
[0099] G101, G102, G103 sliding transmission element old.
[0100] N1, N2, N3 groove curves
[0101] N'1 , N'2, N'3 groove curves old.
[0102] W1-2 Angle between sliding transmission element G1 and G2
[0103] W1-3 Angle between sliding transmission element G1 and G3
[0104] W2-3 Angle between sliding transmission element G2 and G3
[0105] W'1-2 Angle between sliding transmission element G101 and G102
[0106] W1 -3 Angle between sliding transmission element G101 and G103
[0107] W'2-3 Angle between sliding transmission element G102 and G103
Claims
Claims ) Cylindrical housing (1 ) for adjustable optical and mechanical components with a sleeve (2) fixed relative to a housing, with three sliding transmission elements arranged distributed around its inner circumference for operative connection with corresponding groove curves of a cam carrier (5) rotatably and axially displaceably mounted in the sleeve (2) which has a slotted straight guide (6) and a rotating ring (7) fixed in the axial direction, mounted on the outer surface of the sleeve and actuated from the outside, which has at least one transmission element (8) for engaging in the slotted straight guide (6) of the cam carrier (5), characterized in that the angle (W1-2) between the radius of a first (G1 ) and a second (G2) of the three sliding transmission elements (G1 , G2, G3) is smaller than their respective angles (W1-3,W2-3) to the third sliding transmission element (G3).) Cylindrical socket (1) according to claim 1, characterized in that the angle (W1-2) between the radius of the first (G1) and the second (G2) sliding transmission element is less than 90°. ) Cylindrical socket (1) according to claim 2, characterized in that the first (G1) and the third (G3). The sliding transfer element is arranged in an axial direction in one plane and the diameter of the second sliding transfer element (G2) is smaller than that of the first sliding transfer element (G1). 4) Cylindrical socket (1 ) according to claim 3, characterized in that the second (G2) sliding transmission element with smaller diameter is arranged axially spaced from the plane of the first (G1 ) and third (G3) sliding transmission element. 5) Cylindrical socket (1) according to claim 3 or 4, characterized in that the radius distance (9) to the cylinder axis (10) of the second (G2) sliding transmission element, which has a smaller diameter than the first (G1) sliding transmission element, is smaller than the radius distance (11) of the first (G1) sliding transmission element. 6) Cylindrical version (1 ) according to claim 5, characterized in that the groove curves (N1 , N2, N3) assigned to the sliding transmission elements (G1 , G2, G3) are formed as cylindrical curve threads in the cam carrier (5) and are incorporated into the outer surface of the cam carrier (5), wherein the radius spacing of the groove base is adapted to the radius spacing (9, 11 ) of the respective sliding transmission element (G2, G1 ). 7) Cylindrical socket (1) according to claim 6, characterized in that the groove curves (N1, N2, N3) have an axially aligned axial stroke (12) of the curve carrier (5) have an adapted slope, wherein the groove curves (N1, N2, N3) are linear or non-linear. ) Cylindrical socket (1) according to claim 7, characterized in that the groove curves (N1, N2) of different depths assigned to the first (G1) and second (G2) sliding transmission element overlap at least partially. ) Cylindrical socket (1) according to claim 8, characterized in that the groove curves have a first area with a slope (13) that effects an axial stroke (12) and a second area without a slope (14) that does not cause an axial stroke (12). 0) Cylindrical socket (1) according to any one of the preceding claims, characterized in that a bayonet connection with a detent for locking onto a camera system is provided on the stationary sleeve (2) and the first and second sliding transmission elements are arranged at an angular distance from the detent.1) Cylindrical socket (1) according to claim 10, characterized in that the first and the second sliding transmission element (G1, G2) are arranged at an angle of 45° to 135° to the bayonet connection (3), spaced counterclockwise from the detent recess (4). 2) Cylindrical socket (1) according to claim 11, characterized in that a rotating ring (7) is operatively connected to the stationary sleeve (2). A worm gear sleeve (18) with a slotted linear guide for the axial displacement of a further optical component (19) is arranged. A cylindrical socket (1) according to claim 12, characterized in that the axial displacement path (12) of the worm gear sleeve (18) is greater or less than the axial displacement path (12) of the cam carrier (5), wherein a further transmission element (22) connected to the stationary sleeve (2) is provided with engagement in the slotted linear guide (21) of the worm gear sleeve (18) to prevent rotation. A cylindrical socket (1) according to 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°.)Cylindrical socket (101) for adjustable optical and mechanical components with a cam carrier (102) fixed relative to a socket, with three groove cams (N'1 , N'2 , N'3) distributed around its inner cylindrical circumference for operative connection with corresponding sliding transmission elements (G101 , G102 , G103) of a sleeve (105) rotatably and axially displaceably mounted in the cam carrier (102) which has a slotted linear guide (106) and a rotating ring (107) fixed in the axial direction, mounted on the outer surface of the cam carrier (102) and actuated from the outside, which has at least one transmission element (108) for engagement with the slotted linear guide (106) of the sleeve (105), characterized in that the angle (W101-102) between the radius of a first (G101) and a second. (G102) of the three sliding transmission elements (G101 , G102, G103) is smaller than their respective angles (W101-103, W102-103) to the third sliding transmission element (G103) or the distance on the circumference of the sleeve (105) between the first (G101 ) and the second (G102) of the three sliding transmission elements (G101 , G102, G103) is smaller than their respective distance on the circumference to the third sliding transmission element (G103). )Cylindrical socket (101) according to claim 15, characterized in that the angle (W101-102) between the radius of the first (G101 ) and the second (G102) sliding transmission element is less than 90° or the distance on the circumference of the sleeve (105) between the first (G101 ) and the second (G102) sliding transmission element is less than 25% of the total circumference of the sleeve (105).Cylindrical socket (101) according to claim 16, characterized in that the second (G102) and the third (G103) sliding transfer element are arranged axially in one plane and the diameter of the first sliding transfer element (G101) is smaller than that of the second sliding transfer element (G102). Cylindrical socket (101) according to claim 17, characterized in that the first (G101) sliding transfer element with the smaller diameter is arranged axially spaced from the plane of the second (G102) and third (G103) sliding transfer elements. )Cylindrical socket (101 ) according to claim 17 or 18, characterized in that the radius distance (109) to the cylinder axis (110) of the first (G101 ) sliding transmission element, which has a smaller diameter than the second (G102) sliding transmission element, is larger than the radius distance (111 ) of the second (G102) sliding transmission element.