slotted nut

Abstract

A slotted nut (6) for axially fixing an inner ring (4) of a bearing is disclosed, which is fixedly arranged on an axle (2) or shaft, wherein the slotted nut (4) has a thickness D in the axial direction of the axle (4) or shaft, a center with an inner diameter provided with a thread, and an outer peripheral surface (10), wherein the slotted nut (6) is provided with at least one recess (8) on its outer peripheral surface (10), wherein the depth t of the recess (8) is smaller than the axial thickness D of the slotted nut (6) in the axial direction.

Description

Technical Field

[0001] This invention relates to a grooved nut. Background Technology

[0002] In many applications, such as vehicle axles, wheel bearing assemblies are secured to the axle using axle nuts. Here, the wheel bearing assembly serves as a connecting element between a rotating element (such as a motor vehicle wheel) and a stationary element (such as a vehicle axle). For example, if the wheel bearing assembly is implemented using wheel bearing units, it can be mounted on the vehicle axle and secured axially and tangentially by attachment elements to resist displacement or rotation. Here, the attachment elements support the entire axial operating load and transmit it to the axle, for example, via threads (through which the attachment elements are attached to the axle), where, in particular, a high clamping force between the inner rings of the bearing may be required, generated by a very high tightening torque on the attachment elements.

[0003] However, for certain attachment elements, such as grooved nuts (which are particularly advantageous when axial mounting space is limited), these high axial clamping forces can lead to high deformation under certain conditions. In particular, this deformation can result in a loss of clamping strength, a shortened lifespan of the wheel bearing assembly, and, in extreme cases, complete failure of the wheel bearing unit.

[0004] Grooved nuts typically have an annular shape, with eponymous grooves evenly distributed around the outer circumference. Because the grooves are continuous in the axial direction, this gives the grooved nut a segmented shape in the circumferential direction. However, if the segmented areas on the outer circumference of the grooved nut are subjected to high axial loads, the grooved nut may yield and cause the cylindrical threaded hole to deform taperedly.

[0005] This tapered deformation leads to the first thread of the threaded connection being unloaded, while the last thread is subjected to an equal axial load. Therefore, the more tapered the grooved nut, the higher the additional load on the last thread. If the grooved nut's threads are severely tapered, more and more threads are unloaded in the preceding region, and the last two or three threads are subjected to such great stress that they plastically yield and lose (or lose) clamping force or preload. Summary of the Invention

[0006] Therefore, the object of the present invention is to provide a slotted nut that resists deformation more stably.

[0007] This object is achieved by the following slotted nut.

[0008] In the following, a slotted nut for axially fixing the inner ring of a bearing is proposed, and the inner ring is arranged to be fixed on a wheel axle or a shaft. The inner ring can be a fixed ring or a ring that rotates with the shaft. The slotted nut has a thickness D in the axial direction of the wheel axle, a central hole with an inner diameter provided with threads, and an outer peripheral surface, wherein at least one recess is provided on the outer peripheral surface of the slotted nut. In order to construct the slotted nut to resist deformation more stably even under adverse forces, in the axial direction, the depth t of the recess is less than the axial thickness D of the slotted nut. That is to say, the recess does not extend over the entire axial thickness of the slotted nut. Compared with known slotted nuts, the outer periphery of the proposed slotted nut is not continuously segmented, and compared with traditional slotted nuts, the conical deformation of the threaded hole of the slotted nut can be reduced.

[0009] Preferably, the slotted nut is provided with a plurality of recesses uniformly distributed in the circumferential direction. In addition, in particular, the size of the recess can be selected such that a slotted nut wrench or a C-shaped wrench can be used in the slot.

[0010] In addition, the axial depth t of the recess can be 0.3D < t < 0.7D, preferably 0.4D < t < 0.6D, where D is the axial thickness of the slotted nut. In addition, the slotted nut has a width B in the radial direction, and the radial depth b of the recess can be between 0.4B < b < 0.6B. Thus, the deformation of the slotted nut can also be offset.

[0011] According to another embodiment, the slotted nut has an L-shaped profile in the cross-section passing through the recess. The L-shaped profile can further reduce the deformation of the slotted nut.

[0012] According to another embodiment, the slotted nut has a stepped shape including a first ring portion and a second ring portion, wherein at least one recess is provided in the outer peripheral surface of the first ring portion, and the outer diameter of the second ring portion is greater than the outer diameter of the first ring portion. Preferably, the first ring portion and the second ring portion are formed as an integral piece. Therefore, the second ring portion forms a type of flange that extends radially and protrudes beyond the first ring portion. Preferably, the first ring portion has a radial width B1, and the second ring portion has a radial width B2, wherein the radial width B2 of the second ring is between 1.2B1 < B2 < 2B1. Thus, the deformation of the slotted nut can be further reduced.

[0013] According to another aspect, an assembly is proposed that includes a bearing, a wheel axle or shaft, and at least one of the aforementioned grooved nuts.

[0014] Further advantages and advantageous embodiments are specified in the specification and drawings. In particular, the combinations of features specified in the specification and drawings are merely exemplary, such that the features may also exist individually or in other combinations. Attached Figure Description

[0015] The invention will now be described in more detail with reference to exemplary embodiments depicted in the accompanying drawings. These exemplary embodiments and combinations thereof are merely illustrative and are not intended to limit the scope of the invention.

[0016] Figure 1 A cross-sectional view of an assembly including a wheel axle, an inner ring of a bearing, and a grooved nut according to one embodiment is shown.

[0017] Figure 2 A cross-sectional view of a grooved nut according to another embodiment is shown; and

[0018] Figure 3 Showing from Figure 1 Grooved nuts, from Figure 2 Diagrams showing a grooved nut and a variation of a grooved nut according to the prior art.

[0019] Explanation of reference numerals in the attached figures

[0020] 1 component

[0021] 2 wheel axles

[0022] 4 Inner ring

[0023] 6. Grooved Nuts

[0024] 8 concavity

[0025] 10 periphery

[0026] 12 First lap

[0027] 14 Second lap

[0028] 16 Periphery

[0029] 18 lines

[0030] 20 lines

[0031] Line 22

[0032] t Axial depth

[0033] D Axial Thickness

[0034] Outer diameter of d1

[0035] Outer diameter of d2

[0036] Radial widths of B, B1, B2

[0037] Radial depth of b Detailed implementation manners

[0038] In the following, identical or functionally equivalent elements are denoted by the same reference numerals.

[0039] Figure 1 A schematic cross-sectional view of a component 1 according to a first embodiment is shown. The component 1 includes an axle 2, an inner ring 4, and a slotted nut 6. The slotted nut 6 has a central opening with an inner diameter, and the opening is provided with threads, particularly fine threads, which interact with the external threads on the axle 2. Thus, the inner ring 4 can be fixed to the axle 2 by the slotted nut 6.

[0040] The slotted nut has an outer peripheral surface 10, a radial width B, and an axial thickness D. In addition, the slotted nut 6 includes a plurality of recesses 8 on the outer peripheral surface 10 of the slotted nut 6. The recesses 8 can be particularly evenly distributed circumferentially on the outer peripheral surface 10 of the slotted nut 6. Each of the recesses 8 of the slotted nut 6 has a radial depth b and an axial depth t. Preferably, the dimensions of the plurality of recesses 8 are substantially the same.

[0041] Advantageously, the axial depth T of the recess 8 can be between 30% and 70% of the axial thickness D of the slotted nut 6, that is, 0.3D < T < 0.7D, preferably between 40% and 60%, that is, preferably, 0.4D < T < 0.6D. Here, the smaller the axial depth T of the recess is compared to the axial thickness D of the slotted nut 6, the more stable the slotted nut 6 is. In addition, the slotted nut 6 has a radial width B, and the radial depth b of the recess 8 can be between 40% and 60% of the radial width B of the slotted nut 6, that is, 0.4B < b < 0.6B.

[0042] Figure 2 A cross-sectional view of a slotted nut 6 according to another embodiment is shown. Figure 2 The slotted nut 6 has a stepped shape and includes a first ring portion 12 and a second ring portion 14. In particular, the first ring portion 12 and the second ring portion 14 can be formed as an integral piece. Here, the recesses 8 are provided in the outer peripheral surface 10 of the first ring portion 12.

[0043] In addition, the outer diameter d1 of the outer peripheral surface 10 of the first ring portion 12 is smaller than the outer diameter of the outer peripheral surface 16 of the second ring portion 14, or in other words, the second ring portion 14 has a larger outer diameter than the first ring portion 12, whereby the slotted nut 6 has an L-shaped profile in cross section. For the sake of clarity, the outer radii 0.5d1 and 0.5d2 are depicted in Figure 2 Here, the first ring portion 12 has a radial width B1 and the second ring portion 14 has a radial width B2. Preferably, the radial width B2 of the second ring portion 14 is between 1.2B1 < B2 < 2B1.

[0044] Due to the larger radial extension of the second ring portion 14 in which the recess 8 is not provided, compared to the slotted nut 6 of Figure 1 the stability of the slotted nut 6 of Figure 2 can be further increased to resist conical deformation. This can be seen particularly in Figure 3 where the deformation of the threads of the slotted nut from Figure 3 the slotted nut from Figure 1 and the slotted nut according to the prior art are shown in the illustration. Figure 2

[0045] In Figure 3 the x-axis shows the length of the threaded hole in millimeters, where the origin corresponds to the side of the slotted nut 6 furthest from the inner ring 6. The deformation of the threaded hole in millimeters is plotted on the y-axis. Line 18 represents a conventional ( / traditional) slotted nut from the prior art, line 20 represents the slotted nut 6 of Figure 1 and line 22 represents the slotted nut 6 of Figure 2

[0046] The slotted nut 8 generally has an annular shape. However, if the slotted nut 6 is loaded with a high axial load, the slotted nut 6 may yield, in which case the cylindrical threaded hole provided on the inner diameter of the central opening may ( / might) deform conically. Such conical deformation can cause the first thread of the screw connection to be unloaded, and finally the thread is loaded with an equal axial load. Thus, the more conically the slotted nut 6 deforms, the higher the additional load on the last thread. If the threads of the slotted nut undergo severe conical deformation, more and more threads in the front region (i.e., the region where the slotted nut 6 contacts the inner ring 2) are unloaded, and the last two to three threads (i.e., the threads furthest from the inner ring 2) are subjected to such a large stress that they may ( / might) plastically yield and may ( / might) lose the clamping force or preload.

[0047] ​In the slotted nut 6, the axial depth T of the recess is less than the axial thickness D of the slotted nut 6. That is, the slotted nut 6 is continuous on its front side facing the inner ring 4. Since the recess 8 does not completely pass through the slotted nut 6 in the axial direction, the stability of the slotted nut 6 can be increased to resist tapered deformation in this area, and the tapered deformation of the threaded hole can be reduced.

[0048] from Figure 3 As can be seen, assuming the axial load is applied to the exact same surface, compared to a traditional grooved nut, Figure 1 The proposed slotted nut 6 can reduce the tapered deformation of the threaded hole by up to 24%. Also assuming the axial load is applied to the exact same surface, the slotted nut 6 reduces the deformation of the threaded hole by up to 45% compared to the conventional slotted nut.

[0049] In summary, the stability of the grooved nut 6 against tapered deformation caused by axial loads can be increased by reducing the depth T of the recess 8. Furthermore, stability can be further increased by extending the radial flange of the grooved nut.

Claims

1. A grooved nut (6) for axially fixing an inner ring (4) of a bearing, said inner ring (4) being fixedly arranged on a wheel axle (2) or shaft, wherein, The slotted nut (6) has a thickness D in the axial direction of the axle (2) or the shaft, a central hole with an inner diameter provided with a thread, and an outer peripheral surface (10), wherein the slotted nut (6) is provided with at least one recess (8) on its outer peripheral surface (10), and is characterized in that, in the axial direction, the depth t of the recess (8) is less than the axial thickness D of the slotted nut (6). The slotted nut (6) has a width B in the radial direction, and the radial depth b of the recess (8) is between 0.4B < b < 0.6B.

2. The grooved nut according to claim 1, characterized in that, The axial depth t of the recess (8) is 0.3D < t < 0.7D.

3. The grooved nut according to claim 1 or 2, characterized in that, The slotted nut (6) has an L-shaped profile in a cross-section passing through the recess (8).

4. The grooved nut according to claim 1 or 2, characterized in that, The slotted nut (6) has a stepped shape, the stepped shape includes a first ring portion (12) and a second ring portion (14), the at least one recess (8) is provided in the outer peripheral surface (10) of the first ring portion (12), and the outer diameter (d2) of the second ring portion (14) is greater than the outer diameter (d1) of the first ring portion (14).

5. The grooved nut according to claim 4, characterized in that, The first ring portion (12) has a radial width B1, the second ring portion (14) has a radial width B2, and the radial width B2 of the second ring portion (14) is between 1.2B1 < B2 < 2B1.

6. The grooved nut according to claim 1 or 2, characterized in that, The slotted nut (6) is provided with a plurality of recesses (8) evenly distributed in the circumferential direction.

7. The grooved nut according to claim 1, characterized in that, The axial depth t of the recess (8) is 0.4D < t < 0.6D.

8. An assembly (1) comprising a bearing, an axle (2) or a shaft, and at least one slotted nut (6) according to any one of claims 1 to 7.

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