POWER RECEIPT COMPONENT AND GEARBOX ASSEMBLY

Abstract

Force receiving component (3) designed to receive a transverse force acting in a transverse direction of the force receiving component (3), wherein a step (S) is formed on the force receiving component (3) in which a component cross-sectional area changes, such that the step (S) has a first step surface (S1) and a second step surface (S2) which are arranged at a step angle to each other, wherein the second step surface (S2) extends essentially in a direction perpendicular to the transverse direction of the force receiving component (3), wherein a rounding is formed between the first step surface (S1) and the second step surface (S2), which has a first rounding section (RB1) having a first rounding radius (rb) and a second rounding section (RA) having a second rounding radius (ra), where the first radius of curvature (rb) is different from the second radius of curvature (ra), wherein the first rounding section (RB1) is arranged on the side of the first step surface (S1) with respect to the second rounding section (RA), characterized by the fact that an opening angle (ζ) of the second rounding section (RA) in a range of 51.5° to 55.5°.

Description

[0001] The invention relates to a power receiving component and a gear assembly comprising the power receiving component, in particular a cycloidal gear assembly.

[0002] A conventional cycloidal gear assembly, for example, has the following: Fig. The setup shown in section 6. Fig. The conventional gear assembly 101 shown in Figure 6 has a drive shaft 102 with several eccentric sections 102a. Furthermore, the gear assembly 101 has a housing 105 formed from a first housing component 151 and a second housing component 152. The drive shaft 102 is rotatably supported in the first housing component 151. The gear assembly 101 also has an output flange 103 formed from an output flange main body 103b and several drive pins 103a. The drive pins 103a are pressed into the output flange main body 103b. The output flange main body 103b is rotatably supported on the drive shaft 102.

[0003] The drive force is transmitted from the drive shaft 102 to the output flange 103 via three cycloidal disks 142, each supported by a rolling bearing at the eccentric sections 102a of the drive shaft 102. The rolling bearings allow relative movement of the drive shaft 102 and the cycloidal disks 142 in a circumferential direction of the drive shaft 102. The cycloidal disks 142 are further supported on their outer circumference by support bolts 141. The support bolts 141 are inserted into a housing toothing 152a formed on an inner circumferential surface of the second housing component 152. Furthermore, movement of the support bolts 141 in an axial direction of the gear assembly 101 (the drive shaft 102) is limited by an axial support section 151a of the first housing component 151.

[0004] Rotation of the drive shaft 102 by a driving force causes an eccentric rotational movement of the cycloidal discs 142, which roll against the support bolts 141. The direction of rotation of the cycloidal discs 142 is opposite to the direction of rotation of the drive shaft 102. The drive pins 103a engage with openings formed in the cycloidal discs 142. As a result, the output flange 103 is also set into rotation when the drive shaft 102 is rotated. The rotational speed of the output flange 103 is lower than the rotational speed of the drive shaft 102. The direction of rotation of the output flange 103 is opposite to the direction of rotation of the drive shaft 102.

[0005] In the gear assembly 101 described above, a change in speed between the drive shaft 102 and the output flange 103 is thus achieved by the operating principle of a cycloidal gear, which is known per se.

[0006] However, a conventional gear assembly (such as the gear assembly 101 described above) has a complex structure with a large number of individual parts that must be assembled during manufacturing. This increases the manufacturing costs of the gear assembly. Furthermore, the production of the individual parts of a conventional gear assembly is also sometimes very complex and expensive. This further increases the manufacturing costs of the conventional gear assembly.

[0007] DE 10 2020 125 792 A1 discloses a power receiving component according to the preamble of claim 1. DE 10 2019 114 097 A1 discloses a gear assembly with an output element. Further gear assemblies are known from CN 1 14 251 418 A, JP 2014-70 706 A, DE 10 2010 048 778 A1, JP 2002-39 287 A and DE 10 2013 017 925 A1.

[0008] The object of the invention is to provide a force receiving component that has a reduced notch stress and to simplify the construction of a gearbox assembly with this component.

[0009] The object of the invention is achieved with a power receiving component according to claim 1 and a transmission assembly according to claim 9. Advantageous embodiments of the invention are the subject of the dependent claims.

[0010] According to the invention, a force-receiving component is provided, which is designed to receive a transverse force acting in a transverse direction of the force-receiving component. A step is formed on the force-receiving component, in which a component cross-sectional area changes such that the step has a first step surface and a second step surface, which are arranged at a step angle to each other, wherein the second step surface extends substantially in a direction perpendicular to the transverse direction of the force-receiving component. A fillet is formed between the first step surface and the second step surface, which has a first fillet section having a first fillet radius and a second fillet section having a second fillet radius, wherein the first fillet radius is different from the second fillet radius.The first rounded section is located on the side of the first step surface relative to the second rounded section. The opening angle of the second rounded section is in the range of 51.5° to 55.5°.

[0011] Accordingly, the force-receiving component can have a step section where its cross-sectional area changes. In other words, the force-receiving component can have a region with a smaller cross-sectional area and a region with a larger cross-sectional area (for example, cross-sectional areas in a section that includes a central axis of the force-receiving component). Thus, the force-receiving component can have a transition region between the region with the smaller cross-sectional area and the region with the larger cross-sectional area.

[0012] At this step (the transition zone), curved surfaces (rounded sections) can be formed, connecting the outer surfaces of the area with the smaller cross-sectional area and the area with the larger cross-sectional area. At least two curved surfaces with different radii of curvature can be formed, arranged consecutively in one longitudinal direction of the force-receiving component. The aforementioned design of the rounding between the step surfaces reduces the notch stress that occurs at the step when a shear force is applied to the force-receiving component, allowing the force-receiving component to transmit a greater driving force with a constant cross-section (constant cross-sectional area) without sustaining damage (e.g., cracks).Furthermore, the rounding described above, with its two rounding sections with different radii of curvature, can be easily manufactured.

[0013] The first fillet section can be tangent to the second fillet section. This means the transition from the first to the second fillet section can be continuous. Therefore, the first and second fillet sections can have the same slope at their junction. This further reduces the notch stress.

[0014] However, it is not necessary for the radii to be tangentially connected. A discontinuous transition from the first radii to the second radii is also possible, as long as the notch stress is sufficiently reduced. This is the case, for example, if the slopes of the first and second radii differ slightly at their junction. In this case, the slopes of the radii at their junction can differ by up to 10°, preferably up to 5°, and most preferably up to 2°.

[0015] Alternatively, the radius of the force-receiving component can include a third radius of radii, wherein the third radius of radii is located on the side of the second step surface relative to the second radius of radii, wherein the second radius of radii is tangent to the third radius of radii, and wherein the third radius of radii is at least partially recessed relative to the second step surface. Furthermore, the first radius of radii can also be at least partially recessed relative to the first step surface.

[0016] According to the designs described above, a simple shoulder rounding, a radial undercut, or a radial-axial undercut can be created on the step of the force-receiving component. These features are easy to manufacture and can reduce the notch stress as described above, which is associated with the advantages described above. Furthermore, the radial undercut and the radial-axial undercut, for example, allow for subsequent finishing of the step surfaces.

[0017] However, it is not necessary for the rounded sections and stepped surfaces to be tangentially connected. A discontinuous transition between the rounded sections and stepped surfaces is also possible, as long as the notch stress is sufficiently reduced. In this case, the slopes of the rounded sections and the stepped surfaces at the respective connection points can differ from each other by, for example, up to 10°, preferably up to 5°, and most preferably up to 2°.

[0018] In the case of the force receiving component, if rb denotes the first radius of curvature, ra denotes the second radius of curvature, and Φ denotes the golden number, the relationship rb = ra / (2Φ) can be satisfied.

[0019] In the above relationship, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0020] By specifying the rounding radii above, a particularly advantageous reduction of the notch stress on the force-receiving component can be achieved.

[0021] Preferably, the opening angle of the second rounding section is in a range of 53° to 53.3°.

[0022] In the case of the force receiving component, if in a sectional view of the second engagement section the shortest distance between the center of a circle with the first radius of the first radius of the first radius of the third radius of the third is denoted by RC, ra denotes the second radius of the radius and Φ denotes the golden number, the relationship RC = ra / Φ can be satisfied.

[0023] In the above relationship, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0024] In a sectional view of the force receiving component, a junction of the first fillet section and the second fillet section, the center of a circle with the first fillet radius of the first fillet section, and the center of a circle with the second fillet radius of the second fillet section can lie on a straight line that is inclined at an angle α with respect to a connecting line between the center of the circle with the first fillet radius of the first fillet section and a junction between the first fillet section and the first step surface or the second connecting section, where the relationship α = 360° × (Φ-1) / Φ is satisfied.

[0025] In the above relationship, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0026] With a simple shoulder rounding using the above design, a reduction in notch stress of up to 19% can be achieved compared to a conventional rounding design, particularly through the interaction of the radii ra and rb related to each other in the above relationship with the angle α and the distance RC determined according to the above relationship, while maintaining the same radial utilization length. With a radial undercut, a reduction in notch stress of up to 19% can be achieved compared to a conventionally designed radial undercut, with the same depth of cut on the second step surface and a radial utilization length that is more than 15% shorter.

[0027] The aforementioned relationships between the radii ra, rb, the angle a, and the distance RC are each defined as a function of the irrational number Φ. The aforementioned ratios between the quantities ra, rb, a, and RC, which determine the design of the radii according to the invention, are thus to be considered a theoretical ideal case. In practice, deviations from this theoretical ideal case cannot be avoided due to design and manufacturing considerations, which inevitably involve rounding up or down the resulting irrational numerical values. Radius designs that, for this reason, deviate from the theoretical ideal case defined by the aforementioned relationships are therefore to be considered radius designs according to the invention.

[0028] Furthermore, radii on components that deviate from the theoretical ideal case defined by the aforementioned relationships due to usual manufacturing tolerances (e.g. DIN general tolerances) are to be regarded as radii designs according to the invention.

[0029] According to another aspect of the invention, the power receiving component is an output element of a transmission assembly.

[0030] This enables a simple, cost-effective and reliable design of the output element or the gear assembly with the output element.

[0031] The output element can be offered as a replacement component without the rest of the gearbox assembly as an improvement solution.

[0032] The gearbox assembly can be a cycloidal gearbox.

[0033] The invention is described in more detail with reference to preferred embodiments. The following are shown: Fig. 1 a gear assembly according to the invention in a sectional view; Fig. 2 a housing that is in Fig. 1 Gear assembly shown in an isometric view; Fig. 3(a) and Fig. 3(b) a support ring which is in Fig. 1 gear assembly shown; Fig. 4(a) a drive flange and cycloidal disks of the in Fig. 1 shown gear assembly in a partial section; Fig. 4(b) the output flange of the in Fig. 1. Gear assembly shown in a section; and Fig. 4(c) the output flange in an isometric view; Fig. 5(a), Fig. 5(b) and Fig. 5(c) on the output flange of the in Fig. The gear assembly shown in section 1 has radii that can be formed. Fig. 5(d) the constriction process of the contour of the in Fig. 5(a), Fig. 5(b) and Fig. 5(c) roundings shown. Fig. 6 a gearbox assembly in accordance with the state of the art.

[0034] Fig. Figure 1 shows a cycloidal gear assembly 1 according to the invention in a sectional view in a plane which contains an axis of rotation of a drive shaft 2 of the cycloidal gear assembly 1.

[0035] The in Fig. The gear assembly 1 shown in Figure 1 has a drive shaft 2 (drive element) which has several eccentric sections 2a. Furthermore, the gear assembly 1 has a housing 5, which is formed from a first housing section 51 and a second housing section 52. The drive shaft 2 is rotatably supported in the first housing section 51. The first housing section 51 and the second housing section 52 are formed in one piece. That is, the housing 5 is formed as a single, integral housing component. In addition, the gear assembly 1 has an output flange 3 (output element), which is formed from an output flange main body 3b (output element main body) and six drive pins 3a (second engagement sections), of which in the Fig. Only one section is shown in Figure 1. The drive pins 3a are arranged at equal intervals along the circumference of the output flange main body 3b (see Figure 1). Fig. 4(c)). The drive pins 3a and the output flange main body 3b are formed in one piece. That is, the output flange 3 is formed as a single, integral output component. The output flange main body 3b is rotatably supported on the drive shaft 2.

[0036] The driving force is transmitted from the drive shaft 2 to the output flange 3 via three cycloidal or cycloidal disks 42 (power transmission components), each supported at the eccentric sections 2a of the drive shaft 2 by a rolling bearing. The rolling bearings allow relative movement of the drive shaft 2 and the cycloidal disks 42 in a circumferential direction of the drive shaft 2. The cycloidal disks 42 are further supported on their outer circumference by support bolts 41 (support elements). The support bolts 41 are inserted into a housing toothing 52a, which is formed on an inner circumferential surface of the second housing section 52 (see Fig. 2) Furthermore, axial movement of the support bolts 41 of the transmission assembly 1 (the drive shaft 2) is limited by a support ring 6 (axial support component), which in turn is supported in the axial direction by an axial support section 51a of the first housing section 51. In other words, the support bolts 41 are supported in the axial direction by the axial support section 51a of the first housing section 51 by means of the support ring 6. In addition, axial movement of the support bolts 41 is limited by an annular limiting component 4, which is attached to the second housing section 52. As in Fig. As shown in Figure 1, the first housing section 51 has an annular collar 51c that limits a relative movement of the support ring 6 and the housing 5 in a radial direction of the gear assembly 1 (the drive shaft 2).

[0037] Rotation of the drive shaft 2 by a driving force causes an eccentric rotational movement of the cycloidal discs 42, which roll against the support bolts 41. The direction of rotation of the cycloidal discs 42 is opposite to the direction of rotation of the drive shaft 2. The drive pins 3a engage with openings 42a (first engagement sections) formed in the cycloidal discs 42. As a result, the output flange 3 is also set into rotation when the drive shaft 2 is rotated. The rotational speed of the output flange 3 is lower than the rotational speed of the drive shaft 2. The direction of rotation of the output flange 3 is opposite to the direction of rotation of the drive shaft 2.

[0038] In the gearbox assembly 1 described above, a change in speed is thus achieved between the drive shaft 2 and the output flange 3.

[0039] The first housing section 51 also has a centering collar 51b, which allows the housing 5 of the gear assembly 1 to be centered on an adjacent drive assembly, such as a motor assembly. An output of the drive assembly can be connected to the drive shaft 2 of the gear assembly, so that a drive force can be transmitted from the drive assembly to the drive shaft 2. The output flange 3 of the gear assembly has mounting holes 3c, which can be used to connect the output flange 3 to a drive flange of an adjacent working assembly, so that a drive force can be transmitted from the output flange 3 of the gear assembly to the working assembly.

[0040] Fig. 2 shows the housing 5 of the in Fig. Figure 1 shows an isometric view of the gear assembly 1. The housing teeth 52a for the support bolts 41 are formed on an inner circumferential surface of the second housing section 52. A surface of the first housing section 51, which is substantially perpendicular to the axial direction of the gear assembly 1, forms the axial support section 51a. As shown in Fig. 1 and Fig. As shown in Figure 2, a recessed section is formed between the housing toothing 52a and the axial support section 51a in the radial direction of the gear assembly 1 with respect to the housing toothing 52a. This recessed section serves as a runout for the tool used to manufacture the housing toothing 52a during the production of the housing 5. In other words, the axial support section 51a is spaced apart from the housing toothing 52a in the axial direction of the gear assembly 1.

[0041] Furthermore, the first and second housing sections have axial bores (not shown). These bores are mounting bores for attaching the housing 5 to an adjacent drive assembly and / or fluid passages.

[0042] Fig. 3 shows the support ring 6 of which is in Fig. The gear assembly 1 shown in 1 is shown in an isometric view. This shows Fig. 3(a) the support ring of the in Fig. 1 shows the gearbox assembly in the semi-finished product stage after a turning process. Furthermore, it shows Fig. 3(b) the support ring of the in Fig. 1 Gearbox assembly 1 shown in a final, ready-to-install state after a milling, cutting, or punching process.

[0043] More precisely, it shows Fig. 3(a) the support ring 6 in a state in which, by a preceding turning process, an annular semi-finished product with an annular projection arranged at one axial end of the semi-finished product has been produced from a blank, such as a round bar. Furthermore, it shows Fig. 3(b) the support ring in a state in which, by a prior milling, cutting, or stamping process, an external toothing 6a (support toothing) corresponding to the housing toothing 52a is formed on the annular projection of the in Fig. 3(a) was produced. Thus, the outer diameter of the annular projection of the in Fig. 3(a) of the semi-finished product shown is greater than or equal to a maximum outside diameter of the external gearing 6a.

[0044] The in Fig. 3(b) The support ring 6 shown, with the external toothing 6a corresponding to the housing toothing 52a, is as shown in Fig. Figure 1 shows the gear assembly 5 of the gearbox assembly 1 inserted into the housing. Here, the external toothing 6a is located at one end of the housing toothing 52a on the side of the axial support section 51a. The external toothing 6a and the housing toothing 52a overlap in the axial direction. Thus, the external toothing 6a and the housing toothing 52a are in mesh with each other. Movement of the support bolts 41 in the axial direction is therefore prevented by the... Fig. 3(b) shown frontal surfaces of the teeth of the external toothing 6a limited.

[0045] Fig. Figure 4(a) shows the engagement of the drive pins 3a of the output flange 3 with the openings 42a of the cycloidal disks 42. When the cycloidal disks 42 rotate, an outer circumferential surface of the drive pins 3a of the output flange 3 comes into contact with an inner circumferential surface of the openings 42a of the cycloidal disks 42. This allows a drive force to be transmitted from the cycloidal disks 42 to the output flange 3. During the transmission of the drive force from the cycloidal disks 42 to the drive pins 3a, a lateral force is applied to the drive pins 3a, which depends on the transmitted drive force (the transmitted torque). As shown in Fig. As shown in Figure 4(b), the cross-section of the output flange 3 changes at the transition (transition section) between the drive pins 3a and the output flange main body 3b. Thus, at the transition between the drive pins 3a and the output flange main body 3b, there is a step S (see circle marking in Figure 4(b)). Fig. 4(b)). In the area of ​​stage S, the shear force applied to the drive bolts 3a causes stress peaks, a so-called notch stress, due to the notch effect of the cross-sectional change.

[0046] Fig. Figure 4(c) shows the output flange 3 in an isometric view. The drive pins 3a, spaced apart and regularly distributed around the circumference of the output flange main body 3b, can be seen. The fastening bores 3c, formed on the axial end face of the output flange main body 3b opposite the drive pins 3a, are also visible. As in Fig. As shown in 4(c), the fastening holes 3c and the drive bolts 3a overlap at least partially in the circumferential direction of the output flange 3 (i.e., as seen in the axial direction of the gear assembly 1).

[0047] While the axial mounting holes of the first and second housing sections ensure a fixed connection to the drive assembly in one axial direction, the mounting holes 3c of the output flange 3 ensure a fixed connection to the working assembly in the opposite axial direction. Thus, the working assembly with the connected output flange 3 can be axially joined to and separated from the rest of the gearbox assembly, which in turn is connected to the drive assembly. Accordingly, the separate output flange can be offered as a replacement component without the rest of the gearbox assembly as an improvement solution. Likewise, the rest of the gearbox assembly without the output flange can be offered as a replacement component or assembly as an improvement solution.

[0048] Fig. Figure 5 shows radii formed on the output flange 3 of the gearbox assembly 1. More precisely, it shows Fig. 5 radii formed in the area of ​​one of the steps S of the output flange 3, in a sectional view in a plane containing a central axis of the driver bolt 3a, on which the in Fig. Level S, as shown in section 5, is trained. Although in Fig. 5 only shows one stage S of the output flange 3, are those in Fig. The 5 roundings shown are formed at each stage S of the output flange 3, that is, at each transition between one of the drive pins 3a and the output flange main body 3b.

[0049] Fig. 5(a) shows a radial relief groove formed in the area of ​​step S as a first rounding form. As in Fig. As shown in Figure 5(a), the step S has a first step surface S1, which is substantially perpendicular to the axial direction, and a second step surface S2, which extends substantially parallel to the axial direction. The first step surface S1 and the second step surface S2 are thus arranged at a step angle to each other, which is substantially 90°. The radial undercut is formed between the first step surface S1 and the second step surface S2.

[0050] The radial undercut has a first fillet section RB1, which is connected to the first step surface. Furthermore, the radial undercut has a second fillet section RA, which is connected to the first fillet section RB1. More precisely, the second fillet section RA is tangent to the first fillet section RB1. That is, the transition from the first fillet section RB1 to the second fillet section RA is continuous. Thus, the first fillet section RB1 and the second fillet section RA have the same slope at a junction between the first fillet section RB1 and the second fillet section RA. As in Fig. As shown in Figure 5(a), the second fillet section RA is located closer to the second step surface S2 in the axial direction than the first fillet section RB1. That is, the first fillet section RB1 is located on the side of the first step surface S1 with respect to the second fillet section RA.

[0051] The center of a circle with the second radius of the second fillet section RA lies on a straight line passing through the junction of the first fillet section RB1 and the second fillet section RA, and the center of a circle with the first radius of the first fillet section RB1. This straight line is inclined at an angle α (golden angle) to a line connecting the center of the circle with the first radius of the first fillet section RB1 and a junction of the first step surface S1 and the first fillet section RB1.

[0052] Furthermore, the radial relief groove has a third rounding section RB2, which is tangent to the second rounding section RA. As in Fig. As shown in Figure 5(a), the third fillet section RB2 is located on the side of the second step surface S2 with respect to the second fillet section RA. The second fillet section RA is thus located axially between the first fillet section RB1 and the third fillet section RB2. Additionally, the Fig. 5(a) the radial relief cut shown is a planar (in the in Fig. 5(a) shown in the sectional view (represented by a straight line) the first connecting section V1, which is tangent to the third rounding section RB2. The first connecting section V1 is also connected to the second step surface S2. In the Fig. In section 5(a) shown, an angle between the outer surface of the first connecting section V1 and the second step surface S2 is an angle β.

[0053] The outer surfaces of the third rounded section RB2 and the second rounded section RA are arranged at least partially on one side of the central axis of the driver bolt 3a in a radial direction with respect to a connection point of the second step surface S2 and the first connecting section V1. This means that the second rounded section RA and the third rounded section RB2 are recessed at least partially with respect to the second step surface S2. The third rounded section RB2 is recessed with respect to the second step surface S2 by an amount t. This means that the maximum distance from the connection point of the second step surface S2 and the first connecting section V1 to an outer surface of the third rounded section RB2 has a value of t.

[0054] In the Fig. In the sectional view shown in Figure 5(a), Ir denotes a radial utilization length of the radial undercut, that is, a distance from the junction of the first step surface S1 and the first rounded section RB1 to a junction of the second step surface S2 and the first connecting section V1 in the radial direction of the driver bolt 3a. Furthermore, lax denotes an axial utilization length of the radial undercut, that is, a distance from a junction of the first step surface S1 and the first rounded section RB1 to a junction of the second step surface S2 and the first connecting section V1 in an axial direction of the driver bolt 3a.

[0055] Fig. Figure 5(b) shows a radial-axial relief groove formed in the area of ​​step S as an alternative second rounding form. As in Fig. As shown in Figure 5(b), the radial-axial relief groove has a first rounding section RB1, a second rounding section RA, a third rounding section RB2, and a first connecting section V1, each of which is tangent to one another, and as in the Fig. 5(a) show radial relief grooves arranged in the axial direction relative to each other.

[0056] Furthermore, the in Fig. 5(b) the radial-axial relief shown is a planar (in the in Fig. 5(b) shown in the sectional view (represented by a straight line) the second connecting section V2, which is tangent to the first rounded section RB1. The second connecting section V2 is also connected to the first step surface S1. In the Fig. In section 5(b) shown, an angle between the outer surface of the second connecting section V2 and the first step surface S1 is an angle γ.

[0057] Thus, in the Fig. 5(b) In the radial-axial relief shown, not only is the second rounding section RA and the third rounding section RB2 recessed by an amount t with respect to the second step surface S2, but the first rounding section RB1 is also recessed with respect to the first step surface S1.

[0058] It should be noted that in the Fig. 5(b) a radial-axial relief cut is a straight line passing through a connection point of the first rounding section RB1 and the second rounding section RA, the center of a circle with the first rounding radius rb of the first rounding section RB1 and the center of a circle with the second rounding radius ra of the second rounding section RA at an angle α (golden angle) to a connecting line between the center of the circle with the first rounding radius rb of the first rounding section RB1 and a connection point of the first rounding section RB1 and the second connecting section V2.

[0059] It should also be noted that in the radial-axial undercut described above, a radial utilization length Ir is defined as a distance from a connection point of the first step surface S1 and the second connection section V2 to a connection point of the second step surface S2 and the first connection section V1 in the radial direction of the driver bolt 3a, and an axial utilization length lax is defined as a distance from the connection point of the first step surface S1 and the second connection section V2 to the connection point of the second step surface S2 and the first connection section V1 in the axial direction of the driver bolt 3a.

[0060] Fig. 5(c) shows a paragraph rounding formed in the area of ​​level S as an alternative third rounding form. As in Fig. As shown in Figure 5(c), the step fillet has a first fillet section RB1 and a second fillet section RA. The first fillet section RB1 and the second fillet section RA are tangent to each other. Furthermore, the first fillet section RB1 is tangent to the first step surface S1, and the second fillet section RA is tangent to the second step surface S2.

[0061] It should be noted that in the step rounding described above, a radial utilization length Ir is defined as a distance from a connection point of the first step surface S1 and the first rounding section RB1 to a connection point of the second step surface S2 and the second rounding section RA in the radial direction of the driver bolt 3a, and an axial utilization length lax is defined as a distance from the connection point of the first step surface S1 and the first rounding section RB1 to the connection point of the second step surface S2 and the second rounding section RA in the axial direction of the driver bolt 3a.

[0062] With regard to the above statements, it should also be noted that Fig. 5(a), Fig. 5(b) and Fig. 5(c) each show sectional views and in Fig. 5(a), Fig. 5(b) and Fig. 5(c) thus each section through the respective rounding is shown. Therefore, in the case of the Fig. 5(a) radial relief cut shown, in which in Fig. 5(b) radial-axial relief cut shown and in the Fig. 5(c) the first step surface S1, the second step surface S2, the first rounding section RB1, the second rounding section RA, the third rounding section RB2, the first connecting section V1 and the second connecting section V2 each in a ring shape along the circumference of the driver bolt 3a around the central axis of the driver bolt 3a.

[0063] Furthermore, in the Fig. 5(a) radial relief cut shown and in the Fig. In the radial-axial relief groove shown in Figure 5(b), the first fillet section RB1 and the third fillet section RB2 have the same fillet radius rb (first fillet radius), and the second fillet section RA has the fillet radius ra (second fillet radius). In the Fig. In the paragraph rounding shown in 5(c), the first rounding section RB1 has the rounding radius rb and the second rounding section RA has the rounding radius ra.

[0064] The radius of curvature ra and rb can be chosen arbitrarily depending on the dimensions of the output flange 3 (the output flange main body 3b and the drive pins 3a), as long as the following relationship is satisfied: rb=ra2×ϕ

[0065] In the above relationship, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0066] The angle α (golden angle) for the radii described above is determined according to the following equation: α=360∘x(ϕ−1)ϕ

[0067] In the above equation, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0068] At the in Fig. 5(a) radial relief cut shown and in the Fig. In the radial-axial relief shown in Figure 5(b), the shortest distance between the center of the circle with the first radius rb of the first section RB1 and the center of the circle with the first radius rb of the third section RB2 is represented by a radius RC. The radius RC is determined as a function of the second radius ra according to the following equation: RC=raϕ

[0069] In the above equation, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0070] The ideal contour of the above described and in Fig. 5(a), Fig. 5(b) and Fig. The roundings shown in 5(c) can also be achieved using the method described in Fig. The construction steps shown in section 5(d) (steps 1 to 10) are described.

[0071] The radius of curvature ra is selected appropriately depending on the dimensions of the output flange 3 (the output flange main body 3b and the drive pins 3a) (Step 1). The lower end of the first line with length ra generated in Step 1 corresponds to the center of the circle with the second radius of curvature ra of the second curvature section RA. As mentioned above, further design parameters result according to the following principles: rb=ra2×ϕ RC=raϕ α=360∘×(ϕ−1)ϕ

[0072] In the above equations, Φ stands for the irrational number Φ (1.6180339887...), which is associated with the so-called Fibonacci sequence and the so-called "Golden Ratio" and is also referred to as the "Golden Number".

[0073] In step 2, a second line of length RC is added to the top of the first line of length ra, which is then folded 90° in step 3. In step 4, the second line of length RC is shifted by the amount rb, where rb is half the length RC. After step 4, the top of the first line of length ra and the midpoint of the second line of length RC coincide. In step 5, the bottom of the first line and the ends of the second line are connected by further straight lines.

[0074] In step 6, the second line with length RC is shifted along the first line until a circle with radius rb around one end of the second line is tangent to a circle with radius ra around the lower end of the first line. Connecting the ends of the first and second lines then creates a kite-shaped area, which, due to the aforementioned equations where the "Golden Number" plays a crucial role, can also be called the "Golden Kite" (step 7). The opening angle ζ of the circular segment with radius ra around the lower end of the first line (the angle between the lines connecting the lower end of the first line with length ra and the ends of the second line with length RC) is always an irrational angle of 53.13184423...°.

[0075] In step 8, the contour is completed by another circle with radius rb around the other end of the second line with length RC. Furthermore, in step 9, the contour is rotated by the angle α. As shown in step 10, the fillets described above can be created by applying the contour thus generated to the step of the output flange 3.

[0076] By designing the radii as described above, in particular by fulfilling the above relationship between the radius of radii rb and the radius of radii ra, the notch stress (stress peaks occurring at the step S) can be significantly reduced compared to conventional radii and undercuts.

[0077] Furthermore, the above-described determination of the angle α and the opening angle ζ (or the distance RC between the centers of the radii of the first and third fillet sections), in conjunction with the above-described ratio of the fillet radii ra and rb, ensures optimal adaptation of the fillets to the stress distribution arising when the shear force is applied and an optimal reduction of the resulting notch stress (stress peaks). With a simple shoulder fillet using the above-described design, a reduction in notch stress of up to 19% can be achieved compared to a conventional fillet design, while maintaining the same radial utilization length Ir.In a radial undercut with the aforementioned ratio of the radius of curvature ra and rb, a reduction of the notch stress of up to 19% can be achieved compared to a conventionally designed radial undercut (for example, an undercut according to DIN509-E) with the same depth of cut t with respect to the second step surface S2 and a radial utilization length Ir that is more than 15% lower.

[0078] The aforementioned relationships between the radii ra, rb, the angle α, and the distance RC are each defined as a function of the irrational number Φ. The aforementioned ratios between the quantities ra, rb, α, and RC, which determine the design of the radii according to the invention, are thus to be considered a theoretical ideal case. In practice, deviations from this theoretical ideal case cannot be avoided due to design and manufacturing considerations, which inevitably involve rounding up or down the resulting irrational numerical values. Radius designs that, for this reason, deviate from the theoretical ideal case defined by the aforementioned relationships are therefore to be considered radius designs according to the invention.

[0079] Furthermore, radii on components that deviate from the theoretical ideal case defined by the aforementioned relationships due to usual manufacturing tolerances (e.g. DIN general tolerances) are to be regarded as radii designs according to the invention.

Claims

[1] Force receiving component (3) designed to receive a transverse force acting in a transverse direction of the force receiving component (3), wherein a step (S) is formed on the force receiving component (3) in which a component cross-sectional area changes, such that the step (S) has a first step surface (S1) and a second step surface (S2) which are arranged at a step angle to each other, wherein the second step surface (S2) extends essentially in a direction perpendicular to the transverse direction of the force receiving component (3), wherein a rounding is formed between the first step surface (S1) and the second step surface (S2), which has a first rounding section (RB1) having a first rounding radius (rb) and a second rounding section (RA) having a second rounding radius (ra), where the first radius of curvature (rb) is different from the second radius of curvature (ra), wherein the first rounding section (RB1) is arranged on the side of the first step surface (S1) with respect to the second rounding section (RA), characterized by , that an opening angle (ζ) of the second rounding section (RA) in a range of 51.5° to 55.5°. [2] Force receiving component (3) according to claim 1, wherein the first rounding section (RB1) is tangentially connected to the second rounding section (RA). [3] Power receiving component (3) according to claim 1 or 2, wherein the rounding has a third rounding section (RB2) which has the first rounding radius (rb), wherein the third rounding section (RB2) is arranged on the side of the second step surface (S2) with respect to the second rounding section (RA), wherein the second rounding section (RA) is tangentially connected to the third rounding section (RB2), and where the third rounding section (RB2) is at least partially recessed with respect to the second step surface (S2). [4] Force receiving component (3) according to one of claims 1 to 3, wherein the first rounding section (RB1) is at least partially recessed with respect to the first step surface (S1). [5] Force receiving component (3) according to one of claims 1 to 4, wherein the opening angle (ζ) of the second rounding section (RA) is in a range of 53° to 53.3°. [6] Force receiving component (3) according to one of claims 1 to 5, wherein, in a sectional view of the force receiving component (3), the shortest distance between the center of a circle with the first radius of curvature (rb) of the first rounding section (RB1) and the center of a circle with the first radius of curvature (rb) of the third rounding section (RB2) is designated by RC, ra designates the second radius of curvature (ra) and Φ designates the golden ratio, the following relationship is satisfied: RC=ra / ϕ. [7] Force receiving component (3) according to one of claims 1 to 6, wherein, where rb denotes the first radius of curvature (rb), ra denotes the second radius of curvature (ra) and Φ denotes the golden number, the following relationship is satisfied: rb=ra / (2ϕ). [8] Force receiving component (3) according to one of claims 1 to 7, wherein in a sectional view of the force receiving component (3) a connection point of the first rounding section (RB1) and the second rounding section (RA), the center of a circle with the first rounding radius (rb) of the first rounding section (RB1) and the center of a circle with the second rounding radius (ra) of the second rounding section (RA) lie on a straight line which is inclined at an angle α with respect to a connecting line between the center of the circle with the first rounding radius (rb) of the first rounding section (RB1) and a connection point between the first rounding section (RB1) and the first step surface (S1) or the second connecting section (V2), wherein, where Φ denotes the golden ratio, the following relationship is satisfied: α=360∘×(ϕ−1) / ϕ. [9] Gear assembly (1) comprising: a drive element (2); a drive element (3); a speed-changing device between the drive element (2) and the driven element (3); and a housing (5) in which the speed changing device is housed, wherein the housing (5) has a first housing section (51) and a second housing section (52), wherein the first housing section (51) supports the drive element (2) and has an axial support section (51a), wherein the second housing section (52) has an inner circumferential surface on which a housing toothing (52a) is formed, wherein the speed changing device has at least one support bolt (41) which is arranged on the inner circumferential surface of the second housing section (52) and engages with the housing teeth (52a), wherein the speed changing device has at least one power transmission component (42), wherein the power transmission component (42) is supported by an eccentric section (2a) of the drive element (2) and the power transmission component (42) is supported at its outer circumference by the support bolt (41), so that a drive force can be transmitted from the drive element (2) to the power transmission component (42), wherein the power transmission component (42) has at least one first engagement section (42a), wherein the output element (3) has at least one second engagement section (3a), wherein the first engagement section (42a) and the second engagement section (3a) are engaged with each other, so that the driving force can be transmitted from the power transmission component (42) to the output element (3), wherein the output element (3) is the force receiving component (3) according to any one of claims 1 to 8. [10] Gear assembly (1) according to claim 9, wherein the second engagement section (3a) is bolt-shaped and is formed integrally on the output element (3), wherein the output element (3) has an output element main body (3b), and wherein the step (S) is formed on the second engagement section (3a) or on a transition section between the second engagement section (3a) and the drive element main body (3b). [11] Gear assembly (1) according to claim 9 or 10, wherein the first housing section (51) and the second housing section (52) are formed in one piece. [12] Gear assembly (1) according to claim 11, which further comprises an axial support component (6), wherein the axial support section (51a) of the first housing section (51) supports the axial support component (6) in the axial direction of the gear assembly (1), and wherein the axial support component (6) supports the support bolt (41) in the axial direction of the gear assembly (1). [13] Gear assembly (1) according to claim 12, wherein the axial support component (6) is ring-shaped and has a support toothing (6a) which is formed on an outer circumference of the axial support component (6) and corresponds to the housing toothing (52a). [14] Gear assembly (1) according to any one of claims 9 to 13, wherein the gear assembly (1) is a cycloidal gear.

Images