Multi-piece adjusting element

Abstract

A multi-part adjusting element is proposed which allows a very precise adjustment of the bearing of a shaft.

Description

Technical Field

[0001] The invention relates to a lockable precision nut and a lockable threaded ring, which are used in particular for the assembly of spindles or shafts in housings. A particularly important field of application of the nut and the threaded ring according to the invention is the spindles of driven tool holders. The bearings of these spindles have extremely high requirements with regard to concentricity, axial runout, preload and rigidity. For example, for radial and axial runout, this means periodic fluctuations of less than 4 μm. Background Art

[0002] In order to meet these requirements, it has long been known to mount the bearings of the shaft (usually roller bearings, preferably spindle bearings or high-precision tapered roller bearings for the spindles of the driven tools) with a specific preload. In order to obtain the necessary rigidity, the preload in the bearing manufacturer's specifications should be strictly adhered to. For the bearings to be preloaded (e.g. spindle bearings), there is no play in the bearing and the bearing is very hard. For high-precision tapered roller bearings, it may be necessary to set a precise basic clearance, depending on the bearing arrangement, in order to obtain the required preload in operation when the operating temperature is reached. Due to the high rigidity of the shaft, housing and bearings, the adjustment of this preload or the required basic clearance requires extreme care and high precision. If the preload is selected too high, the bearing will be overloaded and its service life will be significantly shortened. If the preload is too low or the basic clearance is too large, the rigidity of the bearing will be too low. In extreme cases, spindle bearings can even cause play in the bearing.

[0003] Therefore, the position of the bearings is usually precisely adjusted and fixed with the aid of nuts with internal threads, which are screwed onto corresponding threads of the shaft. It is important that the nuts can be secured or fixed in any angular position relative to the shaft. The same applies to threaded rings with external threads. In order to adjust the bearings, they are screwed into the internal threads of the housing that accommodates and supports the spindle bearings, and after the bearings have been correctly set, they must be secured or fixed in exactly this angular position or position.

[0004] In order to maintain the adjustment of the bearing, the adjustment element (nut or threaded ring) must be fixed relative to the shaft or housing without changing the bearing adjustment. This means that by fixing or securing the adjustment element, no displacement in the axial direction should occur, nor should tilting. Both have a negative impact on the bearing.

[0005] Fine threads are usually provided on nuts and threaded rings to facilitate sensitive adjustment of the bearing. For the purposes of the present invention, nuts and threaded rings are summarized under the general term "adjusting element". The present invention can be used both with nuts and with threaded rings. The only difference between nuts and threaded rings is that nuts have internal threads and threaded rings have external threads.

[0006] DE 19944131 A1 discloses a nut known as a "clamping ring", in which a threaded pin is screwed radially from the outside into a corresponding threaded hole. So that the threaded pin does not press directly onto the outer thread of a gear shaft or another component, there are elastic tongues on the inner diameter, i.e. in the region of the inner thread of the nut, on which the end of the threaded pin presses. The elastic tongues in turn press onto the outer thread of the spindle or shaft, so that the nut is clamped and fixed against rotation relative to the shaft. However, tightening the threaded pin can lead to undesired relative movements between the nut and the spindle.

[0007] Another solution is known from DE 69406652 T2. In this embodiment, the radially extending threaded holes are designed as blind holes, the depth of which is so great that they end in the immediate vicinity of the internal thread. As a result, the internal thread becomes so soft in the radial direction that it is elastically deformed inwards by tightening the threaded pin. This deformation can cause the nut to jam on the external thread of the shaft. Similar solutions are known from GB 2177178 and WO 03 / 036104 A1.

[0008] A disadvantage of the solutions known from the prior art is that the clamping forces of the threaded pin act between the nut and the shaft; they therefore influence the previously set position of the nut relative to the shaft and therefore relative to the bearing.

[0009] In addition, tightening the threaded pin can cause the plane of the nut to tilt slightly relative to the shaft, resulting in uneven loading of the bearing inner ring or outer ring. This in turn leads to selective overloading of the bearing and a reduction in its rigidity. In addition, this error is reflected in a deterioration in the axial runout and the concentricity of the entire shaft.

[0010] The skilled person is also aware of "groove nuts" according to DIN 981 and locking plates according to DIN 5406. These locking plates have lugs on their inner diameter which fit into the longitudinal grooves of the shaft and thus prevent the locking plate from rotating relative to the shaft. If the bearing has been adjusted by tightening the groove nut, the lug on the outer diameter of the locking plate bends so that it snaps into a groove on the outer diameter of the correspondingly positioned groove nut.

[0011] With this system, the anti-rotation locking of the groove nut with a form-fitting lock is achieved in two steps or stages. Step 1: The locking plate is connected with the shaft with a form fit via the inner lug. Step 2: The locking plate is connected with the nut with a form fit via one of the outer lugs. A disadvantage of this system is that the groove nut cannot be fixed in all angular positions relative to the spindle, since the corresponding angular position of lug and groove must always be set. As a result, the basic play or preload of the bearing can only be set in large discrete steps and not continuously and finely. Summary of the invention

[0012] It is an object of the present invention to provide an adjustment element which can be fixed against rotation without affecting a previously set preload of the bearing.

[0013] According to the invention, this object is achieved by a multi-part adjusting element, which comprises an annular base body, a locking ring and at least one clamping element (clamping screw or threaded pin), wherein the base body comprises a flat surface and a thread and wherein the anti-rotational locking between the locking ring and the shaft or the housing is carried out in a form-fitting manner (step 1) and the anti-rotational locking between the locking ring and the nut and / or the threaded ring is carried out by a releasable force-fit connection (kraftschluss) (step 2).

[0014] According to the principle of the present invention, the anti-rotation locking between the locking ring and the shaft or the housing is achieved by a force-fit connection (step 1), and the anti-rotation locking between the locking ring and the nut or the threaded ring is achieved by a form-fit connection (step 2).

[0015] The releasable force-fit connection according to the invention between the locking ring and the base body or between the locking ring and the shaft or housing prevents these components from twisting after the bearing has been adjusted to any angular position by the force-fit connection; the form-fit connection according to the invention between the locking ring and the shaft or between the locking ring and the housing prevents the force flow during the production of the force-fit connection from flowing through the nut and the shaft or the threaded ring and the housing, and thus does not affect their relative position. In many cases, one or more arcuate segments are sufficient to achieve the advantages according to the invention. Therefore, such segments are also locking rings in the sense of the invention.

[0016] The force-fit connection is preferably produced by pulling the two parts against each other by one or more clamping screws, which interact with threaded holes in the base body. The clamping force required for this purpose can be introduced using the clamping screws without deforming the base body. The clamping screws and the associated threaded holes can be arranged parallel to the center axis of the base body or at an angle of between 10°, 20° or 30°. They can also be arranged radially.

[0017] The threaded pin can also be used to produce a releasable force-fit connection between the locking ring and the shaft or the housing.

[0018] According to the invention, the force flow when the locking ring is pressed against the base body by the clamping screw takes place only in three components: locking ring, base body and clamping screw. The housing, the shaft or spindle and their bearings are not affected or damaged by the closed force flow according to the invention. The same applies if the base body is designed as a threaded ring with an external thread. In other words: the production of the force-fitting connection according to the invention does not change the previously made adjustment of the bearing.

[0019] According to the type of clamping according to the invention, the locking ring can be connected to the base body in a rotationally fixed manner in any position without changing the position of the adjusting element on the shaft or in the housing. The orientation of the plane of the adjusting element is also not affected by the clamping according to the invention. Therefore, the bearing play or the preload of the bearing of the shaft can be adjusted with high precision. After adjustment, it is no longer affected by tightening the clamping screw. Therefore, by using the adjusting element according to the invention, the adjustment of the bearing play or the preload of the bearing can be carried out safely, reproducibly and reliably. No design changes are required for the shaft or spindle to be supported or the housing accommodating the bearing.

[0020] The anti-rotation lock according to the invention is also easy to release. For example, it can be used again after a bearing is replaced.

[0021] The bolt circle diameter of the at least one threaded hole for the at least one clamping screw is within a range that is larger than the outer diameter of the locking ring plus the nominal diameter of the threaded hole and smaller than the outer diameter of the locking ring plus the diameter of the head of the clamping screw screwed into the threaded hole.

[0022] By screwing one or more clamping screws into the threaded holes and tightening them, the locking ring is pressed or clamped in the axial direction against the base body of the adjusting element. This forms a friction anti-rotation lock. The clamping can be carried out in any (angular) position of the locking ring relative to the base body of the adjusting element.

[0023] In a corresponding manner, this can also be achieved by an adjusting element (threaded ring) with an external thread. In this case, the thread is an external thread.

[0024] Since in both embodiments the clamping screw is aligned parallel or obliquely to the longitudinal axis of the internal or external thread, it is easy to tighten the clamping screw and thus lock the adjustment element against rotation from the end face of the shaft or spindle. This is an advantage that should not be underestimated when installing or adjusting spindle bearings.

[0025] Preferably, two, three or even more threaded holes and clamping screws or threaded pins are provided to fix the locking ring. Then, a more reliable anti-rotation locking is achieved and the forces introduced into the locking ring and the base body by the clamping action are evenly distributed over the circumference. The coordinated sequence and metering of the tightening torques of the clamping screws ensure that the locking ring is clamped without distortion, because this means that the friction torque under the screw head is always significantly smaller than the friction torque between the shaft and the base body.

[0026] Another advantageous embodiment of the invention provides that a clamping plate is arranged on each clamping screw. When tightening the clamping screw, the clamping plate presses the locking ring against the base body of the adjusting element, thereby causing a force-fit anti-rotation locking. In order to eliminate the reaction of the tightening of the clamping screws to the previously set bearing play or bearing preload, the clamping plate is fixed to the base body in a form-fitting manner to prevent rotation. This form-fitting connection can be produced, for example, by designing one or two lugs on the clamping plate, which protrude into complementary recesses in the base body of the adjusting element. This ensures a form-fitting anti-rotation locking of the clamping plate relative to the base body and therefore also relative to the locking ring.

[0027] In an advantageous embodiment of the invention, at least one clamping screw has a head with a frustoconical contact surface (countersunk screw). When tightening the clamping screw, the frustoconical contact surface then leads to a selective plastic deformation of the locking ring, so that in addition to the friction clamping there is a form-fitting anti-rotation lock between the base body and the locking ring. In addition, this secures the clamping screw against unwanted loosening. This additional securing can be achieved by careful design without additional costs.

[0028] In order to ensure that the locking ring is centered as well as possible relative to the base body, a recess is provided on the end face of the base body. The diameter of the recess matches the outer diameter of the locking ring. The recess is arranged coaxially with the inner thread of the adjusting element or the outer thread of the adjusting element. It centers the locking ring over the entire circumference of the locking ring.

[0029] Alternatively, the centering can also be done via the shaft of the clamping screw. The recess can then be omitted. If the locking ring is thick enough, the centering can also be done via the external thread of the shaft or the internal thread of the housing. In this case, it has proven to be advantageous if the thickness of the locking ring is at least 1.5 times the pitch of the thread on the adjusting element or the shaft.

[0030] In another advantageous embodiment of the invention, it is provided that at least one of the threaded holes extends radially, so that the locking ring has a cylindrical portion with at least one elongated hole extending in the circumferential direction, and the at least one clamping screw is screwed into the radially extending threaded hole through the elongated hole. In certain applications, such entry of one or more clamping screws is more suitable than entry from the end face. The advantages according to the invention can also be fully achieved in this exemplary embodiment.

[0031] The adjusting element can be designed as a groove nut, a cross hole nut, a face hole nut or a hexagonal nut. All possibilities known in the prior art, i.e. the key for torque transmission from a tool to a nut or a threaded ring, can be used in the adjusting element according to the present invention.

[0032] In order to ensure that the adjustment element with the locking ring cannot rotate relative to the shaft / relative to the housing, the positive locking element of the locking ring is arranged on the inner diameter or, in the case of a threaded ring, on the outer diameter. The positive locking element is preferably a lug which, together with a longitudinal groove in the shaft or housing to be supported, ensures a positive locking against rotation. Since the locking ring and the base body can be positively fixed against rotation relative to each other in any angular position, the adjustment element according to the invention can be fixed against rotation relative to the shaft or housing in any axial position. Tightening the clamping screw does not change the previous adjustment of the bearing of the shaft in the housing.

[0033] The positive locking elements or lugs may extend radially inwards from the inner diameter or radially outwards from the outer diameter. In the case of locking plates according to DIN 5406, these lugs are known per se.

[0034] The anti-rotation locking according to the invention is carried out in two steps. The anti-rotation locking between the locking ring and the shaft is achieved by means of the lug and the longitudinal groove in the shaft. The anti-rotation locking between the locking ring and the base body of the adjusting element is achieved by means of the clamping screw according to the invention.

[0035] If there is no space on the outer diameter of the shaft for introducing a longitudinal groove, one or more depressions can also be provided on the end face of the shaft. When one or more lugs are bent to extend in the axial direction, the lugs of the locking ring can be inserted into these depressions on the end face in a form-fitting manner.

[0036] The lugs usually have two parallel sides which are inserted with little play into the longitudinal groove of the shaft. This results in a small torsional backlash and, since fine threads are usually used, a small axial impact. This backlash and thus the axial effect can be eliminated if one or more lugs have two wedge-shaped sides and these are dimensioned so that they slightly spring back the locking ring when the lug is inserted into the longitudinal groove of the shaft. This form-fitting anti-rotation lock is therefore absolutely free of play. The spring force acting between the shaft and the locking ring has only a small influence on the position of the base body.

[0037] One or more lugs may also have an opening which, together with a pin or a projection (e.g. an end face) on the shaft, provides a form-fitting anti-rotation lock between the shaft and the locking ring. This also allows an anti-rotation lock with very little play between the adjusting element and the shaft.

[0038] The locking ring can also be designed as a circular segment.

[0039] Further advantages and advantageous configurations can be found in the following drawings, their description and the claims.All features disclosed in the drawings, their description and the claims are essential to the invention, either individually or in any combination. BRIEF DESCRIPTION OF THE DRAWINGS

[0040] In the attached picture:

[0041] Figure 1 to Fig. 22 : an exemplary embodiment of an adjusting element according to the invention, and

[0042] Fig.23 : A driven tool holder having an adjusting element according to the invention. DETAILED DESCRIPTION

[0043] In all drawings, the same reference numerals are assigned to the same components. For the sake of clarity, not all reference numerals appear in all figures and views.

[0044] Figure 1a An exemplary embodiment of an adjustment element according to the invention is shown in a front view and an exploded side view. Figure 1a The most important components and functional surfaces of the multi-part adjusting element according to the invention are described.

[0045] Figure 1a The adjusting element shown in FIG. 1 is designed as a nut 1. More specifically, it is a groove nut having four grooves 3 arranged on the circumference. Using a hook spanner (not shown) inserted into one of the grooves 3, the nut 1 can be rotated.

[0046] The nut 1 or adjusting element comprises a base body 21, on which there are a flat surface 5, oppositely arranged end faces 7, an internal thread 9, an outer diameter 11, a recess 13 and a plurality of threaded holes 23. If the adjusting element is a threaded ring, it has an external thread 80 (see Figure 1b ).

[0047] In the region of the end face 7, the recess 13 is concave. The recess 13 is arranged concentrically with the internal thread 9 and accommodates a locking ring 15 according to the invention.

[0048] The locking ring 15 interacts with the base body 21 and has a lug 17, an inner diameter 19 and an outer diameter 25. In the exemplary embodiment, the locking ring 15 is circular on its outer diameter 25, i.e. it has no projections or depressions. The lug 17 is formed on the inner diameter 19 of the locking ring 15. The lug 17 is embedded in the longitudinal groove of the shaft in the assembled state. This creates a non-rotatable form-fit connection between the locking ring 15 and the above-mentioned shaft. The nut 1, i.e. the adjusting element, is then screwed onto the shaft.

[0049] Optionally, the diameter of the recess 13 is dimensioned such that the locking ring 15 with its outer diameter 25 can be inserted into the recess 13 .

[0050] The inner diameter 19 of the locking ring 15 is slightly larger than the nominal diameter of the outer thread of the shaft (not shown). In the present embodiment, the locking ring 15 is not centered on the thread of the shaft; the locking ring 15 is centered by means of a recess 13 in the nut 1 or in the base body 21 of the adjusting element. In the present exemplary embodiment, the depth of the recess 13 is less than or equal to the thickness of the locking ring 15.

[0051] In the present exemplary embodiment, four threaded holes 23 distributed on the end surface are provided in the base body 21 , and the longitudinal axes of the threaded holes extend parallel to the longitudinal axis of the internal thread 9 .

[0052] The diameter D of the bolt circle LK LK Preferably within the following range:

[0053] The center line of the threaded hole 23 is located on the bolt circle LK. The diameter D of the bolt circle LK is LK Larger than the outer diameter 25 of the locking ring 15 plus the nominal diameter 27 of the clamping screw 29 .

[0054] The diameter D of the bolt circle LK of the threaded hole 23 LK Smaller than the outer diameter 25 of the locking ring 15 plus the diameter 31 of the head 33 of the clamping screw 29. Therefore, when the clamping screw 29 is not tightened and the locking ring 15 is allowed to rotate freely, the locking ring 15 is axially held by the clamping screw 29.

[0055] This also ensures that the locking ring 15 is pressed against the base body 21 by tightening the clamping screw 29, because when tightening the clamping screw 29, the inner area of ​​the head 33 of the clamping screw 29 presses onto the locking ring 15. This can be seen from the front view of the nut 1 with the locking ring 15 installed.

[0056] In the present exemplary embodiment, the task of the recess 13 is to align the locking ring 15 concentrically with the internal thread 9 of the base body 21. The recess 13 can also be omitted. The axis of the clamping screw 29 can then center the locking ring 15 (see also Figure 7 and Figure 8 ). Then, the diameter D of the bolt circle LK LK It is only slightly larger than the outer diameter 25 of the locking ring 15 plus the nominal diameter 27 of the clamping screw 29. In this case, the axis of the clamping screw 29 centers the locking ring 15 relative to the thread 9 of the base body 21.

[0057] exist Figure 1aIn the embodiment, a nut 1 with an internal thread 9 is described as an adjusting element. However, the anti-rotation locking according to the invention can also be implemented in a threaded ring 79 which has an external thread 80 on the outer diameter 11 of the base body 21. Figure 1b A threaded ring 79 having an external thread 80 is shown. Figure 1a and Figure 1b A comparison of shows the similarity of the two regulatory elements according to the invention.

[0058] In the present configuration, the lugs 17 are arranged on the outer diameter. At the transition between the end face 7 and the outer diameter, there is an optional recess 13 which centers the locking ring 15 on its inner diameter.

[0059] The threaded ring 79 has clamping elements on its end face 7, which are designed here as holes 75. A corresponding tool can be attached to these clamping elements in order to be able to turn the threaded ring 79 and thus to be able to adjust the bearing.

[0060] The construction details and advantages of the present invention are mainly described below in conjunction with various exemplary embodiments involving a nut 1 with an internal thread 9. However, a person skilled in the art can easily transfer these to similar Figure 1b A threaded ring 79 having an external thread 80 .

[0061] Figure 2 The installation of a nut 1 according to the invention with a locking ring 15 as an example is shown in different views. As can be seen particularly clearly from the enlarged detail Z, the base body 21 of the nut 1 is screwed with its internal thread 9 onto the external thread of a spindle or shaft 35. For the sake of clarity, no reference numerals have been entered for the external thread 9 of the shaft 35 and the internal thread 9 of the base body 21.

[0062] It can also be seen from detail Z that the flat surface 5 of the nut 1 bears against the inner ring 37 of the roller bearing 39. The nut 1 presses the inner ring 37 against the collar or shoulder 41 of the shaft 35. In other words, in this exemplary embodiment, the roller bearing 39 is clamped on the shaft 35 as a fixed bearing.

[0063] In the present embodiment, the clamping screw 29 is designed as a countersunk screw. Therefore, the threaded hole 23 is provided in the base body 21 with a corresponding countersunk point. The locking ring 15 does not have such a countersunk hole. Instead, the countersunk head of the clamping screw 29 deforms the locking ring 15 locally and plastically when it is tightened. This deformation is shown in detail Z. It forms an additional form-fitting connection and anti-rotation lock between the locking ring 15 and the clamping screw 29. It also prevents accidental loosening of the clamping screw 29; it can also act as a screw lock.

[0064] As from Figure 2It can be seen from the medium angle view and the cross section that the lug 17 of the locking ring 15 is accommodated in the longitudinal groove 43 of the shaft 35 in a rotationally fixed but axially displaceable manner, and the tightening of the clamping screw 29 enables the nut 1 to be locked relative to the shaft 35 in a form-fitting and friction-locking anti-rotational manner.

[0065] The clamping of the locking ring 15 on the base body 21 by means of the clamping screw 29 results in a closed force flow between the base body 21, the locking ring 15 and the clamping screw 29. This force flow is indicated in detail Z by a dashed line.

[0066] The internal thread 9 of the nut 1 and the external thread of the shaft 35 are not affected by this clamping process. Therefore, the axial force exerted by the nut 1 on the inner ring 37 of the roller bearing 39 on the plane 5 is not changed by the clamping process. In other words: tightening the clamping screw 29 has no effect on the position of the nut 1 relative to the shaft 35 or the inner ring 37 of the roller bearing 39. This is an advantage of the adjustment element according to the invention.

[0067] Another advantage is that the clamping between the inner ring 15 and the base body 21 can be released at any time by loosening the clamping screw 29. The frictional engagement between the locking ring 15 and the base body 21 of the nut 1 is then released, as is the optional form-fitting connection between the countersunk head of the clamping screw 29 and the locking ring 15.

[0068] Typically, the locking ring 15 will be replaced after use due to the plastic deformation caused by the clamping screw 29 .

[0069] exist Figure 2 In the exemplary embodiment shown, a longitudinal groove 43 is machined into the shaft 35, which forms a positive connection with the lug 17 of the locking ring 15. The locking ring 15 remains axially displaceable but is prevented from rotating relative to the shaft 35 in a positive manner.

[0070] Figure 2 The longitudinal groove 43 is shown closed towards the end of the shaft 35. In order to be able to slide the locking ring onto the shaft, it must be mounted coaxially offset. This means that the inner circle between the lug 17 and the inner diameter 19 of the locking ring is greater than or at least equal to the diameter of the shaft. This allows the locking ring to be pushed coaxially offset onto the shaft until the lug 17 can engage into the longitudinal groove 43. The locking ring can then be pushed coaxially into the recess 13 of the base body 21. The clamping screw is usually installed afterwards. However, depending on the geometric design of the component, a radial installation gap can be integrated partially or even over the entire circumference by slightly loosening the clamping screw 29.

[0071] exist Figure 3, in which a radial recess 45 or a countersunk hole is provided in the shaft 35 instead of the longitudinal groove 43. This recess 45 can be produced, for example, by means of a twist drill.

[0072] exist Figure 4 In the embodiment, the longitudinal groove 43 opens toward the end face of the shaft 35. This variant is particularly simple in terms of production technology. Figure 2 , Figure 3 and Figure 4 In the exemplary embodiment of FIG. 3 , no changes need to be made to the adjusting element according to the invention. The difference lies in the shaft 35 .

[0073] exist Figure 5 , in which the lugs 17 initially extend radially inwards and then become angled in the axial direction, i.e. by approximately 90°. The ends of the lugs 17 extending in the axial direction engage in the recesses 45 on the end face of the shaft 45, thereby producing the required form-fit connection, so that the locking ring 15 is secured against rotation relative to the shaft 35. This embodiment is particularly advantageous if no grooves or holes are desired or should be present on the circumference of the shaft.

[0074] The lug 17 is preferably elastic, so that only very small forces are transmitted from the shaft to the locking ring in the radial direction. All advantages according to the invention are therefore fully achieved in this embodiment as well.

[0075] exist Figure 6 , in which the form-fit connection between the shaft 35 and the locking ring 15 likewise takes place via the end face of the shaft 35. In this exemplary embodiment, a pin 47 is pressed onto the end face of the shaft 35 and protrudes in the axial direction beyond the end face of the shaft 35. The pin 47 forms a form-fit connection together with the opening 49 in the lug 17, which prevents the locking ring 15 from rotating relative to the shaft 35.

[0076] The width of the opening 49 is matched to the diameter of the pin 47 so that a positive locking connection that is as free of play as possible is formed in the tangential direction of the locking ring 15. The opening 49 is preferably designed such that it is longer in the radial direction than the diameter of the pin 47. Therefore, there is play in the radial direction between the pin 47 and the opening 49, so that there is no tension and no transmission of forces between the locking ring 15 and the shaft 35 in the radial direction.

[0077] Figure 7 An exemplary embodiment is shown in which the locking ring 15 is centered on the shaft of the clamping screw 29. Guiding or centering can also be performed by the countersunk head 33 of the clamping screw 29. In this exemplary embodiment, more than three clamping screws 29 distributed over the circumference should be provided to ensure sufficiently accurate centering of the locking ring 15 relative to the base body 21 of the nut 1.

[0078] Figure 8 An exemplary embodiment is shown in which the locking ring 15 is centered via a lug 17. The lug 17 is inserted into a complementary recess 51 on the end face of the shaft 35. As a result, the locking ring 15 is centered. In the present exemplary embodiment, it is sufficient for at least two lugs 17 arranged at an offset of 180° to engage in two cutouts 51. Solutions with more than two lugs 17 and more than two recesses 51 for centering the locking ring 15 are of course also possible.

[0079] This ensures the positioning / centering of the locking ring 15 relative to the shaft 35 without direct contact through the outer diameter of the shaft 35 and the inner diameter of the locking ring 35. In addition, no radial forces can be transmitted from the locking ring to the base body 21, thereby not causing displacement of the base body 21 on the shaft 35.

[0080] In the present exemplary embodiment, the clamping screw 29 is designed as a “conventional” screw, ie without a countersunk head. When the clamping screw 29 is tightened, there is an axial clamping caused by friction between the locking ring 15 and the base body 21 of the nut 1 .

[0081] Figure 9a An exemplary embodiment is shown in which the locking ring 15 is centered by its inner diameter on the outer thread 53 of the shaft 35. In this variant, it is meaningful that the thickness of the locking ring 15, i.e. its extension in the axial direction of the shaft 35, is greater than the pitch of the outer thread of the shaft 35. It is then ensured that the locking ring 15 cannot get stuck in the outer thread 53. The outer thread of the shaft 35 has the reference numeral 53 on the detail Z.

[0082] Figure 9b The situation is shown where the shaft 35 , where the locking ring 15 is positioned, has no external thread 53 , but has a reduced diameter and in this way there is a cylindrical contact surface for centering the locking ring 15 .

[0083] Different designs of lugs 17 are Fig.10 , Fig.11 and Fig.12 In Fig.10 In the embodiment of the present invention, there is a slight gap in the circumferential direction between the side of the longitudinal groove 43 and the side of the lug 17. This small circumferential gap is tolerable in many applications.

[0084] Fig.11 An exemplary embodiment is shown in which the side surfaces of the lug 17 are wedge-shaped. The dimensions of the wedge-shaped side surfaces are selected such that the side surfaces are elastic from above the corners of the longitudinal groove 43 to the diameter of the shaft. This ensures a play-free, form-fitting connection between the lug 17 and the longitudinal groove 43 of the shaft in the tangential direction.

[0085] If the side faces of the longitudinal groove 43 are also arranged in a wedge shape and extend parallel to the wedge-shaped side faces of the lug 17, the same effect is produced, but the contact surface between the lug 17 and the longitudinal groove 43 is increased. Fig.12 Shown in.

[0086] Fig.13 The plastic deformation 57 (described several times) on the outer edge of the locking ring 15 produced by tightening the clamping screw 29 with a countersunk head is shown in detail X. This produces an additional positive connection between the clamping screw 29 and the locking ring 15.

[0087] Fig.14 An exemplary embodiment is shown in which a clamping plate 59 is provided below the head 33 of the clamping screw 29. The clamping plate 59 acts like a clamping jaw and presses the locking ring 15 against a complementary contact surface in the base body 21 of the nut 1 in the axial direction.

[0088] In a particularly preferred embodiment of the invention, the clamping plate 59 has one or two projections 61 on its side facing the base body 21. These projections 61 project into complementary recesses 63 on the end face of the base body 21. This ensures that the clamping plate 59 is locked against rotation and does not rotate when the clamping screw 29 is tightened.

[0089] Fig.15 Another exemplary embodiment is shown, in which the locking ring 15 has an axial length. The locking ring 15 consists of an annular surface with an adjoining cylindrical portion 65. The cylindrical portion 65 surrounds the base body 21 of the nut 1.

[0090] There is a circumferential groove 67 in the cylindrical portion 65. The clamping screw 29 is inserted through this circumferential groove 67 and screwed into a radially extending threaded hole in the base body 21 of the nut 1. Fig.15 In the figure, only a section of the locking ring 15 and the cylindrical portion 65 of approximately 45° is shown.

[0091] In many exemplary embodiments, it is sufficient to use such a section as a locking ring. However, in other embodiments, the locking ring may be formed as follows: Fig.16 The closed loop is shown.

[0092] If there are a plurality of radially extending threaded holes 69 on the circumference of the base body 21 and the distance between these threaded holes 69 is smaller than the tangential extension of the circumferential groove 67 , in this exemplary embodiment the locking ring 15 can also be clamped to the base body 21 in any angular position by means of the clamping screws 29 .

[0093] In accordance with Fig.16 In the exemplary embodiment of FIG. 1 , the locking ring 15 having a cylindrical portion 65 is shown as a closed body.

[0094] In accordance with Fig.17 In the exemplary embodiment of the nut, the cylindrical base body 21 has no grooves or holes on the outer diameter, so the outer diameter of the base body 21 can be used as a sealing surface, which interacts with a radial shaft sealing ring or any gap seal (not shown), for example.

[0095] In order to be able to introduce the torque required for adjusting the nut 1 into the base body 21, clamping elements, shown here as holes 75, can be mounted on the end face of the base body for this purpose. Appropriate tools can be attached to these clamping elements, which can then rotate the nut 1 relative to the shaft 35.

[0096] Due to the locked design of the shaft / housing and the adjusting element according to the invention, which is not affected by lateral forces, there is no radial displacement of the two components relative to each other even when fixed. This is particularly advantageous for the seal, since it means that the sealing elements are optimally aligned coaxially with each other. Problems caused by leakage due to a specific axial deviation of the orientation of the seal and the working surface are greatly reduced.

[0097] Fig.18 Another exemplary embodiment is shown using the example of a threaded ring 79 and a housing 83, in which the base body 21 of the adjusting element has a fine outer toothing 77 on the outer diameter, which interacts with the shape-complementary inner toothing 81 of the locking ring 15. An arc-shaped circumferential groove 67 is introduced into the locking ring 15, through which the clamping screw 29 is screwed into the housing 83. Fig.18 The locking ring 15 is shown in multiple parts; of course, it can also be made as a one-piece and / or closed locking ring 15.

[0098] In this exemplary embodiment, the adjustment element is designed as a threaded ring 79 with an external thread 80. Therefore, an anti-rotation lock must be fixed between the adjustment element and a housing 83 surrounding the adjustment element.

[0099] exist Fig.19 Another exemplary embodiment is shown in FIG. 1 , in which the locking ring 15 also has an internal thread. Both are screwed onto the thread of the shaft 35. The base body 21 and the locking ring 15 are connected to each other via one or more form-fitting locking elements. Fig.19 In the embodiment of the present invention, the form-fitting locking element is shown as a pin 84, which is pressed into the hole of the locking ring 15. The base body 21 is used for the precise adjustment of the bearing 39, while the locking ring 15 connected to the base body 21 via the pin 84 provides an anti-rotation lock, for example by radially arranged threaded pins 85. Of course, all possible thread locks are conceivable here, such as are described in the above-mentioned patents.

[0100] In the present embodiment, it is important that the locking ring and the basic body do not exert any forces on each other during the fixing process according to the invention.

[0101] In detail Z, it can be clearly seen that the pin 84 projects into a recess 86 of the base body 21 which is longer in the radial direction than the diameter of the pin 84. In the tangential direction, the length of the recess 86 is equal to the diameter of the pin 84. The pin 84 couples the locking ring 15 to the locking ring 15 so that a rotationally rigid connection is produced. On the other hand, the coupling in the radial and axial directions is so soft that it does not transmit position changes of the locking ring 15 relative to the shaft 35 which occur when the threaded pin 85 is screwed onto the base body 21.

[0102] Instead of an internal thread on the locking ring 15 , a simple cylindrical hole can also be provided. The shaft 35 can then also have only a cylindrical section in the region of the locking ring 15 instead of a thread.

[0103] exist Fig.20a , in which the locking ring 15 and the base body 21 are connected to one another in a rotationally fixed manner. The connection is made via a pin 84 extending approximately parallel to the longitudinal axis of the shaft 35. The pin 84 can be pressed into the base body 21 and can be guided in a hole 87 in the locking ring 15 with little play.

[0104] In this exemplary embodiment, preferably only one pin 84 is used as a form-fitting locking element. The clamping screw 29 is screwed into the shaft 35; there is a relatively large amount of "air" between the clamping screw 29 and the inner diameter of the locking ring 15, so that no radial forces are transmitted to the base body 21 via the clamping screw 29 and the locking ring 15. The axial forces that can be transmitted from the locking ring 15 to the base body 21 via the pin 84 are also so small that they do not have a negative impact on its axial runout.

[0105] Fig.20b An exemplary embodiment is shown which functions in a similar manner, but in which the adjustment element is designed as a threaded ring 79 . The clamping screw 29 is screwed into the housing 83 .

[0106] Fig.21 Another exemplary embodiment is shown, in which the locking ring 15 is guided in a recess 13 in the base body 21 or centered on its outer diameter. The clamping screw 29 is located in the inner region of the locking ring 15 and initially allows a partial rotation in the base body 21. However, due to the additional threaded holes 23 in the base body 21, any positioning is possible by clamping using the free threaded holes 23.

[0107] Fig. 22An exemplary embodiment is shown in which the clamping screw 29 is introduced at an angle relative to the longitudinal axis of the base body 21 in order to achieve better accessibility. For example, in certain applications, the head of the axially parallel clamping screw 29 can no longer be reached if a larger gear is located in front of the clamping screw 29. The inclination of the clamping screw 29 can be, for example, 20°, 30° or 45°.

[0108] In combination with the countersunk head, the inclination of the clamping screw also makes it possible to optimize the local deformation between the screw head and the locking ring 15 .

[0109] Fig.23 A directly driven tool 100 having a housing 83 and a spindle 102 is shown as an example of application of an adjusting element according to the invention.

[0110] The spindle 102 carries at the left end a tool holder for a standard chuck according to ISO 15488 and at the right end a coupling compatible with a drive of a machine tool (not shown). The spindle 102 is accommodated in a housing 83 by means of two angular contact ball bearings and can rotate. The O-arrangement of the spindle bearings is maintained axially without play and is more specifically preloaded by an adjusting element according to the invention, in this case a nut 1, and is fixed in the desired position by a locking ring 15 with a lug 17 according to the invention. Details of the adjusting element according to the invention cannot be found in this figure. In this respect, reference is made to FIGS. 1 and Figure 2 .

[0111] If tapered roller bearings are used instead of angular contact ball bearings, the axial clearance of the bearing can be sensitively adjusted and fixed in the desired position.

Claims

1. A drive tool (100) comprising a housing (83), a shaft (35, 102), and a multi-piece adjustment element (1, 79), the multi-piece adjustment element (1, 79) comprising an annular base (21), a locking ring (15) and at least one clamping element (29, 85), wherein: The base body (21) comprises a plane (5) and a thread (9, 80), wherein the adjusting element (1, 79) has a device for producing a positive connection between the locking ring (15) and the shaft (35, 102), and wherein the adjusting element (1, 79) has a device for producing a releasable force-fit connection between the locking ring (15) and the base body (21), characterized in that the device for producing a releasable force-fit connection between the base body (21) and the locking ring (15) comprises at least one clamping screw (29) and at least one threaded hole (23) in the base body (21), - the diameter of the bolt circle (LK) on which the at least one threaded hole (23) is arranged is greater than the outer diameter (25) of the locking ring (15) plus the nominal diameter (27) of the threaded hole (23), - The diameter of the bolt circle (LK) is smaller than the outer diameter (25) of the locking ring (15) plus the diameter (33) of the head of the clamping screw (29) screwed into the threaded hole.

2. A drive tool (100) comprising a housing (83), a shaft (35, 102), and a multi-piece adjustment element (1, 79), wherein the multi-piece adjustment element (1, 79) comprises: An annular base body (21), a locking ring (15), and at least one clamping element (29, 85), wherein the base body (21) comprises a plane (5) and a thread (9, 80), wherein the adjusting element (1, 79) has a device for producing a positive connection between the locking ring (15) and the housing (83), wherein the adjusting element (1, 79) has a device for producing a releasable force-fit connection between the locking ring (15) and the base body (21), characterized in that the device for producing a releasable force-fit connection between the base body (21) and the locking ring (15) comprises at least one clamping screw (29) and at least one threaded hole in the base body (21), - the diameter of the bolt circle on which the at least one threaded hole is arranged is smaller than the inner diameter of the locking ring (15) minus the nominal diameter of the threaded hole, - The diameter of the bolt circle is greater than the inner diameter of the locking ring (15) minus the diameter of the head of the clamping screw (29) screwed into the threaded hole.

3. A drive tool (100) comprising a housing (83), a shaft (35, 102), and a multi-piece adjustment element (1, 79), the multi-piece adjustment element (1, 79) comprising an annular base (21), a locking ring (15) and at least one clamping element (29, 85), wherein: The base body (21) comprises a plane (5) and a thread (9, 80), wherein the adjusting element (1, 79) has a device for producing a positive connection between the locking ring (15) and the shaft (35, 102), wherein the adjusting element (1, 79) has a device for producing a releasable force-fit connection between the locking ring (15) and the base body (21), characterized in that the device for producing a releasable force-fit connection between the base body (21) and the locking ring (15) comprises at least one clamping screw (29) and at least one threaded hole (23) in the base body (21), - the diameter of the bolt circle on which the at least one threaded hole (23) is arranged is smaller than the inner diameter of the locking ring (15) minus the nominal diameter of the threaded hole (23), - The diameter of the bolt circle is greater than the inner diameter of the locking ring (15) minus the diameter of the head of the clamping screw (29) screwed into the threaded hole.

4. The driving tool (100) according to claim 1, 2 or 3, characterized in that: A clamping plate (59) is arranged on one or more of the clamping screws (29).

5. The driving tool (100) according to claim 4, characterized in that: The clamping plate (59) is secured against rotation in a form-fitting manner.

6. The driving tool (100) according to claim 1, 2 or 3, characterized in that: The means for producing a positive connection between the locking ring (19) and the housing (83) or between the locking ring (19) and the shaft (35, 102) comprise at least one lug (17) on the locking ring (15).

7. The driving tool (100) according to claim 6, characterized in that: The at least one lug (17) extends radially inwardly from an inner diameter (19) of the locking ring (15), or radially outwardly from an outer diameter (25) of the locking ring (15).

8. The driving tool (100) according to claim 7, characterized in that: The at least one lug (17) also extends in the axial direction.

9. The driving tool (100) according to claim 6, characterized in that: The at least one lug (17) has two parallel side surfaces or two wedge-shaped side surfaces.

10. The driving tool (100) according to claim 6, characterized in that: The at least one lug (17) has an opening (49), and the opening (49) forms a positive connection with a pin (47) in the shaft (35, 102) or the housing (83).

11. The driving tool (100) according to claim 1, 2 or 3, characterized in that: The locking ring (15) is connected to the base body (21) in a form-fitting manner via teeth (77, 81).

12. The driving tool (100) according to claim 1, 2 or 3, characterized in that: The locking ring (15) is connected to the base body (21) in a form-fitting manner via one or more pins (84).

13. The driving tool (100) according to claim 1, 2 or 3, characterized in that: A recess (13) for the locking ring (15) is formed in the end surface (7) opposite to the plane (5) of the base body (21), and the recess (13) is arranged coaxially with the thread designed as an internal thread.

14. The driving tool (100) according to claim 1, 2 or 3, characterized in that: The locking ring (15) has a cylindrical portion (65) which has at least one circumferential groove (67) and through which at least one clamping screw (29) is screwed into the basic body (21).

15. The driving tool (100) according to claim 1, 2 or 3, wherein: The shaft (35, 102) is rotatably mounted in the housing (83), and the play, preload or position of at least one bearing (39) in the housing (83) or relative to the shaft (35, 102) can be adjusted or fixed by the adjusting element (1, 79).

16. The driving tool (100) according to claim 6, characterized in that A longitudinal groove (43) is formed in the shaft (35, 102) or the housing (83), and the longitudinal groove (43) together with the lug (17) of the locking ring (15) forms a gap-free form-fit connection between the locking ring (15) and the shaft (35, 102) or the housing (83) in the tangential direction.

17. The driving tool (100) according to claim 1, 2 or 3, wherein: The shaft (35, 102) is a driving spindle.

Images