JPS5926612A - Axial fixing element - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention Technical Field The present invention provides two workpieces each having a cylindrical fitting surface on the inside and outside, and a conical surface inclined at an angle of 90° or less with respect to the fitting surface. Axial for absorbing particularly high axial forces, configured to be fixed to each other by means of a notched ring section with an external surface and a rectangular cross section that can be fitted into a groove in the workpiece by varying its diameter. It concerns the fixing element.

PRIOR ART An axial fixing element of this type is known (DE 24 50 767). This is designed to absorb as high an axial force as possible due to the wider inclined contact surface and the resulting improved force distribution than the similarly known fixing ring, which has a rectangular cross section and fits into a groove perpendicular to the mating surface. It was born out of an effort to However, this known conical fixing ring has a relatively large bending moment of resistance and is therefore extremely difficult to widen, and, especially in deep grooves, the maximum bending moment caused by widening the ring is limited by the elasticity of the material used. There are drawbacks such as the possibility of the size becoming larger than the range.

OBJECTS OF THE INVENTION It is an object of the present invention to provide an axial fixing element as described above that is capable of absorbing large axial forces without difficulty in assembly, without causing load limits due to the cross-sectional shape when the axial fixing element is deformed. The key is to configure it in such a way.

Structure and Effects of the Invention In the axial fixing element of the present invention, the above objects are achieved in that the ring part is composed of at least two parts that can be assembled independently of each other and that can cooperate with each other. Although such a configuration requires at least two work steps for assembly, the bending moment that must be spent is small due to the small difference in the radius of curvature of the axial fixing elements resulting from the unfolding operation, or the bending resistance moment is small. This has the great advantage that the force required for assembly or disassembly is less than that of the known configuration, and that in the assembled state it is able to absorb a greater axial force than the conventional known configuration. . The invention provides that for the transmission of axial forces, it is not the width of the contact surface on the protected part that is of concern, but the grooves that are decisive for the cross-sectional area of the axial fastening element used and therefore also for the resistance moment. It is also based on the finding that the depth of

With the aid of the invention, deep grooves can be achieved in the assembled state without the drawbacks of the known embodiments, which limit the ring expansion operation or the forces that must be applied to do so.

There are various ways in which the ring portion may be divided into pieces. Preferably, the partial pieces may be constituted by ring segments obtained by dividing the circumference of the ring. Like fixing rings that have only one cut, each ring segment can be inserted into the corresponding groove only after being elastically deformed, so once it is inserted between two protected parts, it will no longer fall out of the groove. It's impossible to do that. This arrangement therefore reduces the bending moments and bending stresses that occur in the individual ring segments during assembly or disassembly, and the bending moments and bending stresses that occur at least at the point of maximum bending moment when the remaining closed ring is unfolded. It has the advantage that the stress υ is much smaller and there is less variation. The partial piece has a square cross section, the partial piece and the groove,
The same axial force can be handled with the shortest structural length if the squares forming the cross section are arranged so that their diagonals are perpendicular to the interfitting surfaces of the workpieces. In this case the groove is 90° at the bottom
angles, each formed at an angle of 45° on the workpiece interfitting surfaces. A minimum bending resistance moment is therefore achieved for a given groove depth.

Preferably, the depth of the groove is such that each segment is retained in the groove by only half of its cross section. In this way, the maximum groove depth can be utilized for transmitting axial force.

On the other hand, as a mode of dividing the ring portion into partial pieces, it is also possible to divide the ring portion into partial rings having different average diameters, the inner and outer surface shapes of which are set relative to each other so that the partial rings fit on mutually opposing surfaces. It is. That is, in the first embodiment, conventionally, a ring having only one cut is divided into segments, whereas in this embodiment, the division is performed concentrically along the circumference. The partial rings each have a rectangular cross-section corresponding to half a square and abut one another on two sides such that the short sides of the rectangles align in the same plane with one another. Therefore, the two mutually independent partial rings are combined to form one ring with a square cross section. Since the partial rings can be assembled and disassembled differently, in this embodiment also much lower bending moments and bending stresses occur than would occur in the case of an integral ring construction. During assembly and disassembly, this partial ring can either be snapped into the groove by expanding the partial ring and then contracted, or it can be opened inwardly by first contracting the partial ring and then expanding it. Depending on whether it is inserted into the groove or extracted, it may be associated with each protected portion in different ways.

In addition, the groove has only one abutment surface, preferably formed at 45° to the interfitting surface of the workpieces, in order to receive the fastening element, in particular square in cross section, and opposite to this abutment surface. It is preferable to include four machining waste removal parts that reach the workpiece interfitting surface via rounded portions. This configuration has the advantage that notch brittleness due to the grooves can be reduced without reducing the effectiveness of the grooves. It is of course also possible to divide the ring part used into individual ring segments in the circumferential part and into concentric rings or concentric ring parts of different diameters, thereby reducing the maximum bending moments and bending stresses. It can be reduced by as much as 2 times.

one or two pieces having a generally square cross section
It is also preferable that the two or more pieces fit into only one of a total of two grooves formed in each workpiece, and the squares formed from one or more pieces abut each other on one side. .

In this case, a total fastening element with a rectangular cross section is formed by joining two partial elements each with a square cross section. An important advantage of this arrangement is that, for example, the shaft can be fixed to a hub or the like in both directions along the axis, and only needs to be fixed at one point, making assembly simple. Such bidirectional fixation was not possible with previously known fixing rings.

Hereinafter, the present invention will be described in detail based on preferred embodiments with reference to the accompanying drawings.

Embodiment FIG. 1 shows a mode in which the end of a shaft 1 is axially fixed in a casing or a hub 2 by means of an axial fixing element 3 according to the invention. In the illustrated embodiment, this axial fixing element 3 consists of three ring segments, each spanning an angle of approximately 120°, formed of a curved section with a square cross section, as is clear from FIGS. 2 and 3). 3a, 3b and 3
Consisting of c. The axial fixation has a triangular cross section with the bottom forming an angle of 90° and the side walls connecting the shaft 1 and the hub 2.
This is achieved by fitting the ring segment into a groove 4 formed in the hub 2 at an angle α of 45° with respect to the cylindrical fitting surface 5.

The depth t of the groove 4 is such that each of the axial fixing elements 3 (i.e., ring segments) 3a, 3b, and 3c fits into the groove 4 up to half of its cross section, and the remaining half fits into the hole 6 of the hub 2. Set. The upper side surface of the axial fixing element 3 is a shaft 10
Since the shaft 1 comes into contact with the 45° inclined surface 1a, the shaft 1 is prevented from moving in the direction of the arrow 7 in the axial direction. The axial forces exerted on the hub 2 by the shaft 1 can be absorbed by a normal force perpendicular to the side faces 3' of the axial locking element 3 and by a normal force perpendicular to the side faces 4' of the groove 4, respectively, by means of a suitable configuration. I can do it.

This also applies to the axial fixation in Figure 4.
The embodiment differs from that of FIG. 1 in that an axial locking element 3, which otherwise has the same shape as that shown in FIGS. 2 and 3, is inserted into a groove 8 in the shaft 1 and acts in the direction of the arrow 9. The only point is that the hub 20 is fixed at the corresponding 45° inclined surface 2a against the axial force.

In the embodiments shown in FIGS. 1 and 4, the manner in which the axial fixing element 3 is inserted is different. That is, in the case of FIG. 1, the ends of the individual ring segments 1-3a, 3b and 3c't are engaged with a tool to be slightly compressed, and then expanded and restored to their original shape, thereby forming grooves 4. Since it is inserted, it fits into the groove 4 in a stress-free state, and since it is in a state of shape engagement, it is impossible for it to fall off. ring segment 3a,
It is also possible to put the respective ends of 3b and 3C into the groove 4 from the outside and then fit them into the groove 4 one after another. In the simplest case, use a hammer and punching tool.

When performing axial fixation on both sides while the shaft 1 is still displaceable in the longitudinal direction, the axial fixation element 3 is manually inserted into the groove 4 in the radial direction, and then the 45° inclined surface 1a of the shaft 1 is It is brought into contact with and engaged with the inserted axial fixing element 3. The second fixing element is assembled with a tool as already described.

In the embodiment of FIG. 4, the axial fixing element 3'ff is fitted obliquely into the groove 8 of the shaft 1 from the outside, so the individual ring segments 3a, 3b, 3el are expanded and inserted into the groove.
It is contracted and engaged with the groove again under stress to prevent it from falling diagonally forward.

In the case of FIG. 5, two axial fixing elements 3 of the present invention are provided on the inner diameter and the outer diameter of the ball bearing 10, and the ball bearing 10 is
The outer ring and the inner ring of are axially fixed in the part 20 and the shaft 1, respectively.

FIG. 6 shows that the groove 4 does not necessarily have to be implemented as a cut groove with a 90° bottom as shown in FIGS. 1 and 4. In order to minimize the notch effect, the groove has only one side wall 4' at 45° to the cylindrical mating surface 5, as shown in FIG. A possible embodiment can also be implemented in which the workpiece removal recess 12 reaches the workpiece interfitting surface 5 via a rounded part. Here too, the transmission of the axial force takes place by diametrically opposed abutment surfaces 3' and 3 of the axial fixing element 3, which has a square cross section. In this case, the side surface 3" is the contact surface 4 of the machining waste removal recess 12.
' and also the side surface 3' abut, with their rounded edges, the inner ring 10a of the ball bearing 10, which abuts the axial fixing element 3, respectively.

7 to 10 show other embodiments of the axial fixation of the present invention. In this case, the axial fixing element 3 has a cut in one place in a known manner and has at least two cuts with different average diameters.
It consists of two partial rings 3d and 3e, which are designed to abut one another with their mutually facing sides 13 and 14. Partial rings 3e and 3d also have their end faces 1
5 and 16 are aligned in the same plane with each other, thus forming an axial locking element 3 with a generally square cross section, which fits into the groove 4 and abuts the 45° inclined surface of the shaft 1. In the embodiment of FIG.
each of the force absorbing side surface of the groove 4 and the inclined surface 1a of the shaft 1
It is configured so that it comes into contact with the Assembly of this ring takes place by first compressing the partial ring 3e and then inserting it obliquely into the conical space between the groove 4 and the shaft 1 while expanding it. Next, in the same way, ring 3d'
to fit into. Decomposition takes place in the opposite order. If shaft 1 is still in the position shown, ring 3e
It goes without saying that the shaft 1 may be positioned only after the shafts 1 and 3d are sequentially inserted into the groove 4. Similarly, in the embodiment of FIG. 9 in which the shaft 1 is axially fixed within the shaft 7, the ring 3e is first inserted, and then the ring 3d is inserted. In this case, the partial rings 3e and 3d are constructed in such a way that their end faces 15 and 16 are in close contact with the force-transmitting surface. The partial rings 3d and 3e abut the force-transmitting wall on their side surfaces, but not on their end faces.

8 and 10 show similar embodiments for fixing the shaft 1 to the hub 2 against forces acting in the direction of the arrow 17. FIGS. However, the partial rings 3d and 3e are the grooves 8 of the shaft 1.
7 and 9 in that the partial rings are not compressed before assembly, but on the contrary must be unfolded and passed through the shaft 1. In this embodiment as well, the groove 4 is deep so that even if the axial locking element has a relatively large square cross-section, the forces required for compression or expansion are reduced by dividing it into two half-rings, i.e. partial rings 3d and 3e. You have the advantage of being able to. In this case as well, as already mentioned, assembly and disassembly is possible even when the shaft 1 is already in its terminal position relative to the hub. Partial rings 3d, 3e
and ring segments) 3a, 3b, 3c are expanded and compressed by applying a suitable tool to each end of these sections.
This can be done in a known manner, in part by forming openings, eyelets, notches or ramps of the known construction from fastening rings and retaining rings.

FIG. 11 shows a special embodiment of the axial direction in that the end of the shaft 1 is fixed axially in the knob 2 or a corresponding casing not only in the direction of the arrow 7 but also in the direction of the arrow 17. showed fixation. This fixation is achieved by forming a groove 4 in the nose 2 and a groove 8 in the shaft 1, as shown in FIG. This is achieved by fitting the second partial ring 3g having a cross section into the groove 4 of the hub 2 so that these partial rings abut each other.

In this case, the assembly is done by first positioning the shaft 1 or expanding the partial link 3f with the shaft 1 removed and inserting it into the groove 8.
This is done by fitting the shaft 1 into position, then compressing the partial ring 3g and inserting it obliquely from the outside into the annular gap remaining between the partial ring 3f and the groove 4. Rings 3f and 3 are used to generate biasing force.
It does not mean that g should be set to have a radius larger and a radius smaller than the respective grooves of cooperation.

The advantage is that axial fixation can be achieved in both directions by inserting the fixing ring in only one location, which is different from the embodiment shown in FIG. This is particularly useful when In the embodiment shown in FIG. 11a, the groove 4 does not have two equally sized side walls, but one side wall 4'', on which the two partial rings 3g and 3f rest, is twice as wide as the other side wall. In this case too, the side walls of the groove 4 are at right angles to each other, and the side wall 4/// and the other side wall are each formed at an angle α of 45° to the associated cylindrical mating surface 5. ing.

The embodiment shown in FIG. 11b also allows axial fixation in both directions. However, in this embodiment, the outer groove 4 of the hub 2
has an isosceles right triangular cross section, and the groove 8 is formed on one side wall 8.
``'' is twice as wide as the other side wall. In this embodiment, the assembly is performed by first compressing the partial ring 3g so that it fits into the groove 4, and then attaching it to the surface 8.
After positioning the shaft 1 by bringing the ring 3g into contact with the ring 3g, the partial ring 3fe is expanded and then contracted so as to fit into the groove 8 and achieve axial fixation. .

In the embodiments shown in FIGS. 7 to 11, in each case the partial rings 3d, 3e, 3f and 3g are each further divided into separate ring segments in the circumferential direction. Needless to say, it is possible to have both the advantages of radial division and the advantages of radial division.

[Brief explanation of the drawing]

1 is a longitudinal sectional view schematically illustrating the axial fixation of the shaft end to a hub or the like; FIG. 2 is a combination of three individual ring segments that can be fitted into corresponding grooves; FIGS. 1 and 4; FIG. 3 is a cross-sectional view taken along the line ■-■ of the fixing element in FIG. 2, and FIG. FIG. 5 is a longitudinal sectional view schematically showing another embodiment of axial fixation in which the ball bearing is fitted into a groove in the shaft, and FIG. Figure 6 is an enlarged longitudinal cross-sectional view showing detail ■ in Figure 5;
7 is a longitudinal section similar to FIG. 1, but schematically illustrating the aspect of axial fixation by means of an axial fixation element consisting of two notched partial rings abutting each other in concentric relation; FIG. FIG. 9 is a longitudinal section similar to FIG. 4, but schematically illustrating the mode of axial fixation by two superimposed partial rings concentrically; FIG. 9 is a longitudinal section similar to FIG. 7, but in the axial direction of the bore wall and shaft. A vertical cross-sectional view schematically showing a mode of axial fixation by a partial ring with a rectangular cross section whose side surface is in contact with a force-absorbing surface;
Fig. 10 is a longitudinal sectional view similar to Fig. 8, but schematically illustrating a mode of axial fixation by a partial ring in which the end face rather than the side surface abuts the axial force absorbing surface; FIG. 11a is a longitudinal sectional view schematically showing the manner in which the shaft is axially fixed in the hole wall in both directions by fitting two abutting partial rings into grooves in the shaft and the hole wall, respectively; FIG. FIG. 11b is a diagram showing an embodiment in which a groove having a contact surface with the ring is provided in the hole wall, and a embodiment in which such a groove is provided in the shaft. 1...Shaft, 2...Hub, 3... Axial fixing element (ring portion), 3a, 3b, 3c... Ring segment, 3d, 3e, 3f, 3g partial ring, 4... Groove, 5... Workpiece mutual fitting surface , 6... Hole of knob 1, 8... Groove, 10... Ball bearing, 11...
Rounded part, 12... Machining waste removal recess. Patent Applicant Palter Pauer Patent Attorney Akira Aoki Patent Attorney Kazuyuki Nishidate Patent Attorney Takashi Nakayama Patent Attorney Akira Yamaguchi

Claims (1)

[Claims] 1. Having cylindrical fitting surfaces on the inside and outside, 2.
A cut with a rectangular cross section, which has a conical outer surface inclined at an angle of 90 degrees or less with respect to the fitting surface, and which can be fitted into the groove of the workpiece by changing the diameter. In an axial fixing element for absorbing particularly high axial forces designed to be fixed to one another by certain ring parts, the ring parts (3) have at least two parts which can be attached independently of each other and which cooperate with each other.
An axial fixing element characterized in that it consists of two partial pieces (3a to 3g). 2. Axial fixation according to claim 1, characterized in that the partial pieces consist of ring segments (3&. 3b, 3c) obtained by dividing the circumference of the ring (3). element. 3. Axial fixing element 0 according to claim 1 or 2, characterized in that the partial pieces (3a, 3b, 3e, 3f, 3g) have a square cross section. Claims: The partial pieces (3a, 3b, 3c T 3 tr 3g ) and the groove (4) are configured such that the diagonal of the square is perpendicular to the fitting surface (5). The axial fixing element according to item 3 of Section 5. 5. Partial piece (3a * 3 b, 3 c + 3 f
, 3 g) are each grooved in only half of its cross section (4
5. The axial fixing element according to claim 4, characterized in that the depth 1) of the groove (4) is set such that the groove (4) is held within the range 1). 6. The partial piece consists of partial rings (3d, 3e) with cuts having different average diameters, and the inner and outer shapes of the partial rings are respectively set relative to each other so that the partial rings can be fitted into each other on the surfaces facing each other. The axial fixing element according to claim 1, characterized in that: 7. The partial rings (3d, 3e) each have a rectangular cross section that spirals in half of a square, and rectangular end surfaces (15, 16)
7. Axial fixation element according to claim 6, characterized in that the axial fixation element abuts the adjacent partial rings on two sides such that they align in the same plane with each other. 8. The partial rings (3d, 3e) have an end surface (
Claim 7, characterized in that the groove (4) of the workpiece (1, 2) is in contact with the axial force supporting surface (4') or the opposing surface (1a) on the side (15, 16). The axial fixation element described in section. 9. The partial ring (3d, 3e) is attached to the workpiece (1) on its side.
, 2), the surface (4') supporting the axial force of the groove (4, 8)
The axial fixing element according to claim 7, characterized in that it comes into contact with the opposite surface (1a). 10. The grooves (4, 8) preferably have a single abutment surface (4') inclined at an angle of 45° to the mating surface (5) and an opposing rounded portion (11). Through the mating surface (5)
Any one of claims 1 to 9, characterized in that it has four machining waste removal parts (12) reaching .
The axial fixation element described in section. 11. Only one in each case of square section sections (3f, 3g) has two grooves (4) associated with each workpiece (1, 2).
, 8), and both partial pieces abut each other on their sides.
The axial fixing element according to any one of items 0 to 0.