CN115899214A - Gear, in particular toothed ring - Google Patents
Gear, in particular toothed ring Download PDFInfo
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- CN115899214A CN115899214A CN202110960963.6A CN202110960963A CN115899214A CN 115899214 A CN115899214 A CN 115899214A CN 202110960963 A CN202110960963 A CN 202110960963A CN 115899214 A CN115899214 A CN 115899214A
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Abstract
The invention relates to a gearwheel which is assembled from segments, each having a bearing region, a first flange region arranged at the front in the circumferential direction, a second flange region arranged at the rear in the circumferential direction, the first flange region of each segment resting with a first surface region against a second surface region of the second flange region of the segment closest to the respective segment, at least one bolt passing through the first flange region of each segment and the flange region of the respective closest segment connecting the segments to the closest segment, a toothing being machined in the bearing region of the segments, the toothing being designed as a helical toothing, the first surface region of each segment being parallel to the toothing of the toothing closest to this first surface region.
Description
Technical Field
The invention relates to a gear, in particular a toothed ring (component with ring teeth).
Background
WO 2013/020639 A1 discloses a gearwheel made up of segments, which has helical toothing.
Disclosure of Invention
The object of the invention is therefore to improve a gear such that a high service life is achieved.
According to the invention, this object is achieved by a gearwheel according to the features given in claim 1.
For gears, in particular toothed rings, the important features of the invention are: the gear is assembled from segments arranged one after the other in the circumferential direction with reference to the axis of rotation of the gear,
-a support area for supporting the support element,
a first flange region arranged forward in the circumferential direction,
a second flange region arranged at the rear in the circumferential direction,
wherein the first flange region of each segment bears with a first surface region against a second surface region of the second flange region of the segment closest to the respective segment,
wherein at least one bolt passing through the first flange region of each segment and the flange region of the respective closest segment connects the segment with the closest segment,
wherein teeth are machined in the bearing regions of the segments,
wherein the toothing is designed as a skewed toothing, in particular with a non-negligible skew angle, in particular with a skew angle different from zero,
the first surface area of each segment is parallel to the closest tooth of the toothing to the first surface area, and/or
The first surface area of each segment is parallel to the teeth of the toothed segment adjacent to the first surface area,
in particular, the surface region adjoins the tooth flush, so that the tooth neither projects nor retracts relative to the first surface region in the circumferential direction.
The advantage is that only minor mechanical stresses occur. Since the transition from the tooth to the surface region is designed to neither protrude nor retract. The surface area is thus connected flush to the teeth and the stresses are distributed as evenly as possible. This increases the service life or allows higher torques to be transmitted.
In an advantageous embodiment, the respective section has a plate region/center plate region and a support part,
wherein the bearing region and the plate region are connected by the support and by the first flange region,
in particular, wherein the first flange region is located radially between the bearing region and the plate region,
in particular, the first flange region is arranged on an end face region of the segment which is located in front in the circumferential direction. The advantage is that high stability can be achieved with low material costs, so that high torques can be transmitted with low material costs and a high service life can be achieved.
In an advantageous embodiment, the bearing region and the plate region are also connected by a second flange region,
in particular, wherein the second flange region is located radially between the bearing region and the plate region,
in particular, the second flange region is arranged on an end face region of the segment which is located behind in the circumferential direction. The advantage is that the segments are designed to be rigid and to be able to transmit high torques at low material costs.
In an advantageous embodiment, the supports are spaced apart from one another in the circumferential direction by means of a cut-out which passes through in the axial direction,
in particular wherein the indentations each have a clear width measured in the circumferential direction which increases with increasing radial distance, in particular in a radial distance region which exceeds at least 70% of the radial distance region covered by the indentation as a whole. The advantage is that high stability can be achieved at low material costs.
In particular, the axial direction is parallel to the direction of the rotation axis of the gear.
In an advantageous embodiment, the bearing region, the plate region, the first flange region, the second flange region and the support are designed as one piece, in particular in one piece, in particular so that the segments are made of one piece of steel. The advantage of this is that the segments can be produced as a cast part, and the toothing and the surface region can then be finished.
In one advantageous embodiment, the segments are made of Austempered Ductile Iron (ADI), i.e. in particular of bainitic iron with spheroidal graphite, in particular of heat-treated ductile iron. The advantage is that, despite the high manufacturing costs, a high load capacity and thus a high torque transmission can be achieved.
In an advantageous embodiment, the first surface region and/or the second surface region are designed to be flat and/or substantially flat. The advantage of this is that the contact surfaces of the two sections can be made sufficiently large so that the two sections to be connected can be pressed against one another with a high contact pressure.
In an advantageous embodiment, the normal direction of the first surface area has an angle of inclination with respect to the tangential direction associated with the first surface area. This has the advantage that the surface area extends parallel to the teeth. The tooth root therefore opens directly into the flat surface region over its entire axial length. In this way, a protrusion or retraction is avoided, so that the resulting mechanical stresses remain low.
In an advantageous embodiment, a first stepped bore is formed in the first surface region, through which the screw passes,
in particular, the hole axis of the first stepped hole is not parallel to the normal direction of the first surface region and/or is inclined at an angle to the normal direction of the first surface region. The advantage of this is that the stepped bore can be produced in a simple manner and the bolt can be protected by the widened region, i.e. the annular gap, upstream of the first step in order to avoid shearing forces in the section. By introducing the force further away, less shear force can be created inside the bolt.
In an advantageous embodiment, the minimum spacing between the step of the first stepped bore and the first surface region varies in the circumferential direction with respect to the bore axis of the first stepped bore, in particular in dependence on the associated circumferential angle with respect to the bore axis. This has the advantage that the stepped bore is oriented obliquely to the normal direction about the inclination angle. The stepped bore is thus oriented in the tangential direction, but the flange region is designed parallel to the toothing. In this way, on the one hand, a high service life is achieved by the absence of projections or the like and thus reducing the mechanical stresses and extending them smoothly. On the other hand, the bolts are oriented in the tangential direction, i.e. in the tangential direction perpendicular to the radial direction on the contact surface.
In an advantageous embodiment, the clear internal diameter of the first stepped bore increases monotonically with increasing distance from the first surface region. This has the advantage that the annular gap protects the bolts from excessive shear forces in the area where the two flange areas of the interconnected segments are in contact. In this way, the shear forces can be deflected and thus the load on the screw can be reduced and the service life can be increased.
In an advantageous embodiment, a second stepped bore is formed in the second surface region, through which the screw passes. The advantage of this is that a tangential stepped bore is produced in the other section, also in the region of the surface inclined about the angle of inclination with respect to the radial plane.
In an advantageous embodiment, the hole axis of the second stepped hole is not parallel to the normal direction of the first surface region and/or has an angle of inclination with respect to the normal direction of the first surface region. The advantage is that the service life is increased, since a protrusion of the toothing is avoided.
In an advantageous embodiment, the minimum spacing between the step of the second stepped bore and the second surface region varies in the circumferential direction with respect to the bore axis of the second stepped bore, in particular in dependence on the associated circumferential angle with respect to the bore axis. This has the advantage that the bolts are arranged in the tangential direction and the surface area is arranged obliquely around the angle of inclination. The teeth are thus prevented from protruding and the service life is increased.
In an advantageous embodiment, the clear internal diameter of the second stepped bore increases monotonically with increasing distance from the second surface region. This has the advantage that the annular gap of the protective screw surrounds the screw in the contact region of the two flange regions.
In an advantageous embodiment, the threaded region of the bolt is screwed with a nut, so that the flange region of the respective section and the flange region of the section closest to the respective section are pressed against one another between the nut and the bolt head of the bolt. This has the advantage that the segments can be connected in a simple and cost-effective manner.
In an advantageous embodiment, the bolt is surrounded by an annular gap in the region in the direction of the bolt axis, which annular gap is arranged between the contact region of the bolt with the first flange region and the contact region of the bolt with the second flange region. This has the advantage that the bolts are protected against excessive shear forces and thus have an increased service life.
In an advantageous embodiment, the annular gap comprises a region which is covered in the axial direction of the bolt by a contact region between the first surface region and the second surface region. This has the advantage that the bolts are protected against excessive shear forces and thus have an increased service life.
In an advantageous embodiment, the first flange region has a through-opening in the circumferential direction, the clear diameter, the maximum inner diameter and/or the clear opening area of which decreases monotonically in the circumferential direction with increasing distance from the first surface region. This has the advantage that, for connecting the segments, on the one hand the nut and on the other hand the head of the bolt are pressed onto the flange region, to be precise on one side of the narrowing region of the recess. The indentation widens towards the contact region. Since there a sufficiently large surface area acts as a contact area. Thus, the surface pressure is kept sufficiently small. However, the compression of the nut and the bolt head takes place in a very small surface area. Furthermore, instead of only one bolt, a plurality of corresponding bolts are provided, and thus a high pressing force is applied. However, since the gap narrows there, there is sufficient material for the high contact pressures to be absorbed. However, the enlargement of the indentation towards the contact area also saves material and thus weight.
In an advantageous embodiment, the second flange region has a through-opening in the circumferential direction, the clear diameter, the maximum inner diameter and/or the clear opening area of which decreases monotonically with increasing distance from the second surface region, counter to the circumferential direction. The advantage of this is that, for connecting the segments, on the one hand the nut and on the other hand the bolt head of the bolt is pressed onto the flange region, to be precise on one side of the narrowing region of the recess. The indentation widens towards the contact region. Since there a sufficiently large surface area acts as a contact area. Thus, the surface pressure is kept sufficiently small. However, the compression of the nut and the bolt head takes place in a very small surface area. Furthermore, instead of only one bolt, a plurality of corresponding bolts are provided, and therefore a high contact pressure is applied. However, since the gap narrows there, there is sufficient material for the high contact pressures to be absorbed. However, the enlargement of the indentation towards the contact area also saves material and thus weight.
Further advantages are given by the dependent claims. The invention is not limited to the combination of features of the claims. Further possible combinations of the features of the claims and/or of the individual claims and/or of the features of the description and/or of the drawings can be derived by the person skilled in the art, in particular from the presentation of technical problems and/or by comparison with the prior art.
Drawings
The invention will now be described in detail with reference to the schematic drawings:
fig. 1 is a view of one of the segments 1, wherein a gear wheel, in particular a toothed ring, according to the invention is composed of these segments.
Fig. 2 is a plan view of the segment 1, which is viewed from the radial direction.
Fig. 3 is a side view of two of the segments 1 connected with the bolt 30.
Fig. 4 is a sectional view of the connecting region of two segments 1.
Fig. 5 is an oblique view of the section 1.
Fig. 6 is a schematic view of the connection region of the two segments 1 around one of the bolts 30, so that fig. 6 corresponds to an enlarged detail of fig. 4.
List of reference numerals:
1. segment of
2. Gap
3. Toothed section
4. Plate-like region
5. Flange region
6. Supporting part
7. Bearing area
20. Angle of inclination
30. Bolt
40. Window, in particular stepped window
50. Hole(s)
60. Contact surface
61. Shear force
62. Annular gap
Detailed Description
As shown in the drawing, the respective segment 1 has a plate region 4, with which the segment is fastened by means of screws to a drum, in particular a cement drum, to be driven by a gear, in particular a toothed ring. Alternatively, a welded connection can also be implemented. The plate region 4 projects between the two annular regions of the drum and is welded to these annular regions. In the embodiment with bolts, these are each guided in the axial direction through the annular region and also through the plate region 4.
As shown, the toothing 3 is machined in the bearing region 7 on the radial outer circumference of the segment 1 of the gearwheel.
The toothing 3 is designed as a helical toothing with a bevel angle 20.
The bearing regions 7 are connected by a support 6 arranged radially between the plate region 4 and the bearing regions 7. The supports are spaced apart from one another in the circumferential direction by means of a through-opening 2 which runs in the axial direction.
The axial direction is parallel to the direction of the rotational axis of the gear.
Each recess 2 extends in a circumferential direction in a manner expanding with increasing radial distance from the axis of rotation of the gear.
Furthermore, the bearing region 7 and the plate region 4 are also connected by a first flange region 5, which is located in particular radially between the bearing region 7 and the plate region 4. The first flange region 5 is arranged on an end face region of the segment 1 located forward in the circumferential direction.
Furthermore, the bearing region 7 and the plate region 4 are also connected by a second flange region 5, which is located in particular radially between the bearing region 7 and the plate region 4. The second flange region 5 is arranged on an end face region of the segment 1 located rearward in the circumferential direction.
The preferably finished, in particular ground, front and rear end faces of the segments are the surface regions of the first and second flanges 5, respectively. These surface areas are used to connect the closest segments 1. The flanges 5 of two adjacent, interconnected segments 1, which are in contact with one another, can therefore be precisely aligned with one another. The surface region thus serves as an orientation surface and/or a centering surface.
The surface region is preferably designed as a flat surface.
These surface regions are parallel to the root curve of the toothing of the portion 1 respectively closest to the flange 5. Since the toothing is designed as a helical toothing, the surface region is likewise designed with an angle of inclination with respect to the plane: the plane contains the rotational axis of the gear wheel and preferably lies tangentially on the tooth root curve at a point of the tooth root curve.
The tooth root is the following surface point of the tooth of the toothing 3: the surface point is located on the root circle of the toothing, in particular at an axial position. The distance between the tooth root and the rotational axis of the gear is thus the root circle radius. The root curve here refers to the line formed by the roots at all axial positions.
Since the surface region of the respective flange region 5 is parallel to the adjoining tooth of the toothing, i.e. in particular the tooth with which the surface region is closest, the surface region adjoins the tooth flush, so that the tooth neither projects nor retracts in the circumferential direction. Thus, a smooth stress distribution curve can advantageously be achieved and predetermined breaking points can be avoided.
The axial width of the flange region 5 is greater than the axial width of the plate region 4.
As shown in fig. 4 and 6, the respective screws 30 pass through the flange regions 5 of the respective sections 1 that are closest to one another and abut against one another in a contacting manner. For this purpose, the bolt 30 is cylindrical in design in the region arranged between the bolt head of the bolt 30 and the threaded region of the bolt 30. The bolts 30 rest via a cylindrical region against the holes of the flange region 5 through which the bolts 30 pass.
In this way, the two sections can be centered relative to one another.
A nut is screwed onto the threaded region of the bolt 30, so that the nut and the bolt head press the two flange regions 5 against one another.
However, in the plane of the contact surface of the receiving section 1, the hole is designed to be widened, i.e. the hole has in particular a step.
This widening of the bore creates an annular gap 62 around the bolt 30.
The shear forces 61 acting in the contact plane are thus deflected and the screw 30 is protected against high peak stress distributions. In this way, the service life of the bolt and the bolted connection of the two segments 1 in particular is increased.
The two holes that are aligned with one another are each designed as a stepped hole in the respective flange region 5, the two holes bearing against one another with their wider clear inner diameters.
These two holes are machined in the respective surface areas. The hole axis is therefore not parallel to the normal direction of the respective surface area. However, the normal directions of the two surface areas are parallel to each other.
Thus, the step of the respective hole has a non-constant and/or varying spacing to the flat surface area. The pitch of the steps and the flat surface regions is related to the circumferential angle in the circumferential direction with respect to the bore axis.
The clear internal diameter of the respective bore decreases monotonically with increasing distance from the respective further section 1 or bore, in particular decreases monotonically with increasing distance from the surface area of the flange region 5.
The threaded region of the bolt 30 projects from the flange region 5, so that a nut is screwed onto the threaded region.
Since the bolts 30 each bear, in particular with a fit, precisely against a narrow region of the bore, the segments 1 are centered with respect to one another.
In a further exemplary embodiment according to the invention, instead of designing the bore as a stepped bore for receiving the bolt 30, a non-stepped, i.e. non-stepped or less stepped extension of the clear inner diameter of the respective bore is designed. In this way, the shear forces do not act directly from the step, but rather slowly form with increasing distance from the surface region. In this way, the bolt 30 is subjected to a less varying stress distribution, and therefore the service life of the bolt 30 is increased.
In this case, the clear internal diameter preferably varies as a function of decreasing, smooth and/or continuously differentiable function with increasing spacing from the respective surface region, after the contact region between the screw 30 and the bore, in particular the flange region 5.
Claims (17)
1. A gear, in particular a toothed ring,
wherein the gear is assembled from segments arranged one after the other in the circumferential direction with reference to the rotational axis of the gear,
wherein each section has
-a support area for supporting the support element,
a first flange region arranged forward in the circumferential direction,
a second flange region arranged at the rear in the circumferential direction,
wherein the first flange region of each segment rests with a first surface region against a second surface region of the second flange region of the segment closest to the respective segment,
wherein at least one bolt passing through the first flange region of each segment and the flange region of the respective closest segment connects the segment with the closest segment,
wherein teeth are machined in the bearing regions of the segments,
wherein the toothing is designed as a bevelled toothing, in particular with a non-negligible bevel angle, in particular with a bevel angle different from zero,
it is characterized in that the preparation method is characterized in that,
the first surface area of each segment is parallel to the closest tooth of the tooth section to the first surface area,
and/or
The first surface area of each segment is parallel to the teeth of the toothed segment adjacent to the first surface area,
in particular, the surface region adjoins the teeth flush, so that the teeth neither project nor retract in the circumferential direction relative to the first surface region.
2. The gear according to claim 1, wherein the gear is a single gear,
it is characterized in that the preparation method is characterized in that,
each section has a plate region and a support portion,
wherein the bearing region and the plate region are connected by the support and by the first flange region,
in particular, wherein the first flange region is located radially between the bearing region and the plate region,
in particular, the first flange region is arranged on an end face region of the segment which is located at the front in the circumferential direction.
3. Gear according to any one of the previous claims,
it is characterized in that the preparation method is characterized in that,
the support region and the plate region are also connected by a second flange region,
in particular, wherein the second flange region is located radially between the bearing region and the plate region,
in particular, the second flange region is arranged on an end face region of the segment which is located to the rear in the circumferential direction.
4. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the supports are spaced apart from one another in the circumferential direction by means of a cut-out which passes through in the axial direction,
in particular, the indentations each have a clear width measured in the circumferential direction, which clear width increases with increasing radial distance, in particular in a radial distance region which exceeds at least 70% of the radial distance region covered by the indentations as a whole.
5. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the axial direction is parallel to the direction of the rotational axis of the gear.
6. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the support region, the plate region, the first flange region, the second flange region and the support are designed as one piece, in particular in one piece, in particular so that the section is made of one piece of steel.
7. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the segments are made of austempered ductile iron, i.e. in particular bainitic iron with spheroidal graphite, in particular heat-treated ductile iron.
8. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the first surface area and/or the second surface area are designed to be flat and/or are designed to be substantially flat.
9. Gear according to any one of the previous claims,
it is characterized in that the preparation method is characterized in that,
the normal direction of the first surface area has an inclination angle with respect to the tangential direction belonging to the first surface area.
10. Gear according to any one of the previous claims,
it is characterized in that the preparation method is characterized in that,
machining a first stepped hole in the first surface region, through which the bolt passes,
in particular, the hole axis of the first stepped hole is not parallel to the normal direction of the first surface region and/or is inclined at an angle to the normal direction of the first surface region.
11. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the minimum spacing between the step of the first stepped bore and the first surface region varies in the circumferential direction with respect to the bore axis of the first stepped bore, in particular varies in relation to the associated circumferential angle with respect to the bore axis,
and/or
The first stepped bore has a net inner diameter that monotonically increases with increasing spacing from the first surface area.
12. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
a second stepped bore is machined in the second surface region, through which the bolt passes,
in particular, the hole axis of the second stepped hole is not parallel to the normal direction of the first surface region and/or has an angle of inclination with respect to the normal direction of the first surface region.
13. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the minimum spacing between the step of the second stepped bore and the second surface region varies in the circumferential direction with respect to the bore axis of the second stepped bore, in particular varies in relation to the associated circumferential angle with respect to the bore axis,
and/or
The net inner diameter of the second stepped bore monotonically increases with increasing spacing from the second surface area.
14. Gear according to any one of the previous claims,
it is characterized in that the preparation method is characterized in that,
the threaded region of the bolt is screwed with a nut so that the flange region of each segment and the flange region of the segment closest to the respective segment are pressed against each other between the nut and the bolt head of the bolt.
15. Gear according to any one of the previous claims,
it is characterized in that the preparation method is characterized in that,
in the region in the direction of the bolt axis, the bolt is surrounded by an annular gap which is arranged between the contact region of the bolt with the first flange region and the contact region of the bolt with the second flange region,
and/or
The annular gap comprises an area in the direction of the bolt axis covered by a contact area between the first surface area and the second surface area.
16. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
the first flange region has a cut-out running through in the circumferential direction, the clear diameter, the maximum inner diameter and/or the clear opening area of which in the circumferential direction decreases monotonically with increasing spacing from the first surface region,
and/or
The second flange region has a cut-out running through in the circumferential direction, the clear diameter, the maximum inner diameter and/or the clear opening area of which decreases monotonically with increasing distance from the second surface region, counter to the circumferential direction.
17. Gear according to any one of the preceding claims,
it is characterized in that the preparation method is characterized in that,
adjoining the contact region between the screw and the wall of the stepped bore, in particular the flange region, the clear inner diameter of the respective stepped bore changes according to a decreasing, smooth and/or continuously differentiable function as the distance from the respective surface region increases.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110960963.6A CN115899214A (en) | 2021-08-20 | 2021-08-20 | Gear, in particular toothed ring |
| PCT/EP2022/025333 WO2023020711A1 (en) | 2021-08-20 | 2022-07-18 | Gear, in particular gear rim |
| DE102022002624.4A DE102022002624A1 (en) | 2021-08-20 | 2022-07-18 | Gear, in particular ring gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110960963.6A CN115899214A (en) | 2021-08-20 | 2021-08-20 | Gear, in particular toothed ring |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115899214A true CN115899214A (en) | 2023-04-04 |
Family
ID=86471447
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110960963.6A Pending CN115899214A (en) | 2021-08-20 | 2021-08-20 | Gear, in particular toothed ring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115899214A (en) |
-
2021
- 2021-08-20 CN CN202110960963.6A patent/CN115899214A/en active Pending
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