Shaft and hub connection arrangement

Abstract

Shaft and hub connection arrangement (10) for transmitting torque, comprising: a shaft (12) which extends along a and is rotatable about an axis (A) and terminates axially at a shaft end (14); a hub (22) which extends along the and is rotatable about the axis (A) and terminates axially at a hub end (24); a first flange (18) which extends outwards from the shaft (12) at a distance from the shaft end (14) and extends in a ring shape around the shaft (12); a second flange (26) extending from the hub (22), adjacent to the hub end (24), to be positioned in an adjacent axial end-to-end relationship with the first flange (18); a fastening mechanism (32) which engages with the first and second flanges (18, 20) and preloads them against each other; wherein one of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a male connecting section (16), and the other of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a female connecting section (28) for receiving and being coupled with the male connecting section (16); wherein the female connecting section (28) has a radially inner surface (36) defined by a plurality of inner surfaces (40); wherein the male connecting section (16) has a radially outer surface (34) defined by a plurality of outer surfaces (38) nested within the plurality of inner surfaces (40) to couple the male and female connecting sections (16, 28) together; wherein the radially outer surface (34) of the male connecting section (16) has a plurality of outer transition regions (42), each of the plurality of outer transition regions (42) being arranged between and connecting adjacent persons of the plurality of outer surfaces (38) in a circumferential direction along an outer radius (R3); and the radially inner surface (36) of the female connecting section (28) has a plurality of inner transition regions (44), each of the plurality of inner transition regions (44) being arranged between and connecting adjacent persons of the plurality of inner surfaces (40) in the circumferential direction along an inner radius (R4); and a first gap (G1) defined between adjacent areas of the plurality of outer and inner transition regions (42, 44) to provide tolerances in the radial direction during the manufacture of the male and female components.

Description

CROSS-REFERENCE TO RELATED REGISTRATIONS

[0001] This application claims priority over US Provisional Patent Application serial number 63 / 071,741, which was filed on August 28, 2020. TECHNICAL AREA

[0002] The present invention relates to a shaft and hub connection arrangement for transmitting torque. Particularly preferably, the present invention relates to a shaft and hub connection arrangement that includes connecting components of the shaft and hub, respectively, which provide a simple and effective connection between the shaft and the hub and are easy and inexpensive to manufacture. BACKGROUND

[0003] Shaft-hub connection assemblies for transmitting torque are known in the art. For example, one-piece constant velocity joint half-shaft assemblies typically have an externally toothed shaft section integrally connected to a hub section, such as an outer ring or a tulip housing. The externally toothed shaft section typically engages directly with a differential gear within an axle or transaxle differential assembly. The externally toothed shaft section also typically includes a sealing pin to engage with a seal on the axle or transaxle housing, allowing lubricating fluid to be introduced into the axle or transaxle assembly once the half-shafts have been installed. However, a number of problems arise with such constant velocity joint assemblies. For example,Constant velocity joints and tripod joints (tulip joints) require special adaptations to connect with a wide variety of axle and transaxle interfaces, including variations in shaft length, gear geometry, and sealing interfaces. This results in high manufacturing and development costs. Additionally, common half-shaft constant velocity joints with integrally splined shaft sections prevent the axle or transaxle assembly from being filled with lubrication until vehicle assembly, as the axle / transaxle is not sealed until the half-shafts are installed.Lubrication filling during vehicle assembly is undesirable because it requires additional infrastructure and costs to access filling points within the assembly area, and special controls are needed to ensure proper lubrication due to the wide variety of lubricants and fluids used in vehicle assembly plants. Furthermore, common constant velocity joints with integrally splined shaft sections can damage axle or transaxle housing seals if the externally splined section of the half-shaft is installed in the axle or transaxle during vehicle assembly.

[0004] Shaft and hub arrangements with mechanical connections located outside the axle or transaxle arrangement are known to allow vehicle assembly to take place without disturbing axle / transaxle housing seals.

[0005] Document US 8,075,218 B2 discloses a shaft and hub connection arrangement comprising a shaft having a polygonally shaped male connection section and a hub defining a female connection section for receiving and coupling with the male connection section. The male connection section has a radially outer surface with a plurality of outer faces, and the female connection section has a radially inner surface with a plurality of inner faces. The outer faces are interlocked within the inner faces to connect the male and female connection sections. The male and female connection sections incorporate certain geometric features, such as a non-constant taper angle and corner radii, for self-locking of the male and female connection sections and to prevent rotational play.However, it has turned out that these geometric features are relatively complex and therefore difficult and expensive to reliably mass-produce.

[0006] Document US 9,387,544 B2 discloses a spline connection consisting of a male spline component and a female sleeve coupled together. The male component has external teeth with multiple tooth gaps that feature conical and angular reliefs to provide tool clearance. These reliefs extend into a shoulder and base region of the component. The female sleeve has internal teeth with corresponding tooth gaps that also feature conical and angular reliefs for tool clearance and extend into the bearing surface of a countersunk hole. The external and internal teeth are of equal length, resulting in a defined effective engagement width of the spline connection.

[0007] Document US 1,552,343 A discloses an invention for securely fastening a pinion to a drive shaft. The aim is to reliably prevent the pinion from twisting or loosening after installation, particularly during power transmission, e.g., in motor vehicles. The solution utilizes a tapered (conical), polygonal shaft shape, a matching sleeve, and additional locking elements such as a keyway, a key, and a threaded connection with a nut. This results in a secure, positive-locking, and friction-locking connection that is easy to install and provides long-term reliability.

[0008] Document DE 299 01 561 U1 discloses an arrangement of a developer cylinder and a drive wheel for developer refill devices in copiers, printers, or fax machines. To overcome the high manufacturing costs of known twisted couplings, the developer cylinder is provided with a hexagonal coupling block that engages in a coupling hole in the drive shaft. This ensures that the developer cylinder rotates securely during coupling. Advantages include simple geometry, cost-effective injection molding, quick replacement of the developer cylinder, and reliable power transmission.

[0009] Document EP 1 225 356 A1 discloses a shaft-hub connection for torque transmission between a rotating shaft and a coaxially arranged hub. The shaft and hub interlock over a drive length section and have non-circular retaining sections for torque transmission. At least one of the components has several retaining sections arranged at angular offsets, thereby ensuring reliable torque transmission.

[0010] Document DE 102 20 372 B4 discloses a power transmission device, in particular a drive shaft of a motor vehicle, which is connected to a differential via a pinion. Instead of a conventional splined connection with a mounting flange, a polygonal coupling connection is used. This reduces or eliminates backlash and rotational imbalances and ensures improved power transmission between the drive shaft and the differential. The polygonal connection can also be used for other power transmission connections.

[0011] Document EP 1 871 277 B1 discloses a dental implant and a component to be connected to it, which can be coupled to each other via an internal connection. This internal connection comprises a cylindrical section and an anti-rotation section. The anti-rotation section is composed of several repeated, arc-shaped elements whose arcs connect tangentially to one another. This special geometry achieves improved anti-rotation stability and performance compared to known solutions.

[0012] Accordingly, there remains a need for improvements to shaft and hub connection arrangements that provide a mechanical connection outside of an axle or transaxle arrangement, offering simpler and more reliable connections. OVERVIEW

[0013] According to one aspect, the invention relates to a shaft and hub connection arrangement for transmitting torque of a shaft which extends along a shaft and is rotatable about an axis and terminates axially at a shaft end, a hub which extends along the shaft and is rotatable about the axis and terminates axially at a hub end, a first flange which extends outwards from the shaft at a distance from the shaft end and extends annularly around the shaft, a second flange which extends from the hub, adjacent to the hub end, in order to be positioned in an axial end-to-end relationship with the first flange, a fastening mechanism which engages with the first and second flanges and preloads them against each other, wherein one of the shaft end of the shaft and the hub end defines a male connection section.and the other, from the shaft end of the shaft and the hub end of the hub, a female connecting section defined for receiving and being coupled to the male connecting section, wherein the female connecting section has a radially inner surface defined by a plurality of inner surfaces, wherein the male connecting section has a radially outer surface defined by a plurality of outer surfaces, nested within the plurality of inner surfaces to couple the male and female connecting sections together, wherein the radially outer surface of the male connecting section has a plurality of outer transition regions, each of the plurality of outer transition regions being arranged between and connecting adjacent ones of the plurality of outer surfaces in a circumferential direction along an outer radius,and the radially inner surface of the female connection section has a plurality of inner transition regions, each of the plurality of inner transition regions arranged between and connecting adjacent plurality of inner surfaces in the circumferential direction along an inner radius, and a first gap defined between adjacent plurality of outer and inner transition regions to provide tolerances in the radial direction during the manufacture of the male and female components.

[0014] The shaft and hub connection provides a modular external connection that is reliable, simple, and cost-effective to manufacture. The overlapping outer and inner surfaces preferably provide a large surface contact area between the male and female connection components, thus ensuring a reliable torque-transmitting connection between the shaft and hub. Meanwhile, the gap between the outer and inner transition areas, created during the manufacturing of the male and female components, provides tolerances in the radial direction, ensuring a reliable contact pattern between the male and female connection sections that does not drastically change with given geometric errors, thereby providing improved service life.In addition, the arrangement of the overlapping outer and inner surfaces and the gap between the outer and inner transition areas requires no special equipment for manufacturing and allows for simple dimensional checks, thus enabling frequent quality control.

[0015] According to a further aspect, the invention relates to a shaft and hub connection arrangement for transmitting torque, comprising a shaft extending along a path and rotatable about an axis and terminating axially at a shaft end, a hub extending along a path and rotatable about the axis and terminating axially at a hub end, wherein one end of the shaft and the hub end defines a male connection section, and the other end of the shaft and the hub end defines a female connection section for receiving and coupling with the male connection section, wherein the female connection section has a radially inner surface defined by a plurality of inner surfaces, and wherein the male connection section has a radially outer surface.defined by a plurality of outer surfaces and nested within the plurality of inner surfaces to couple the male and female connection sections, a first flange extending outwards from the shaft in a spaced relationship with the shaft end, a second flange extending from the hub adjacent to the hub end and positioned in an axial end-to-end relationship with the first flange, wherein a first axial radius is defined between the first flange and one of the radially outer and inner surfaces, a second axial radius is defined between the second flange and the other of the radially outer and inner surfaces, and a gap is defined between the first axial radius and the second axial radius, such that total contact between the male and female connection sections occurs along the outer and inner surfaces.

[0016] The arrangement of the first radius of curvature, which is larger than the second radius of curvature, further ensures that complete contact between the male and female connection sections occurs along the outer and inner surfaces, and further provides tolerances during the manufacture of the male and female connection sections, ensuring that the manufacture of the arrangement is simple and cost-effective and produces reliable components. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Other advantages of the present invention will be readily understood, as they will be better understood by reference to the following detailed description when viewed in conjunction with the accompanying drawings, wherein: Fig. Figure 1 is a side cross-sectional view of a shaft and hub connection assembly; Fig. Figure 2 is an enlarged side cross-sectional view of the male and female connection sections of the shaft and hub connection assembly. Fig. 1; Fig. 3A is a side cross-sectional view of the female connecting section; Fig. 3B is a front view of the female connecting section; Fig. 3C is a perspective view of the female connecting section; Fig. 4A is a side cross-sectional view of the male connecting section; Fig. 4B is a front view of the male connector section; Fig. 4C is a perspective view of the male connection section; and Fig. Figure 5 is a front cross-sectional view of the male and female connection section. DETAILED DESCRIPTION OF THE INVENTION

[0018] Referring to the figures, where the same reference numerals consistently denote corresponding parts in the different views, a shaft and hub connection assembly 10 is provided for transmitting torque, such as in motor vehicle drives. The shaft and hub connection assembly 10 can be installed in various torque transmission devices, including half-shafts, cardan shafts, gearboxes, wheel hubs, electric motors, and axle interfaces.

[0019] As in Fig. As best shown in Figure 1, the shaft and hub connection arrangement 10 comprises a shaft 12 extending along and rotatable about an axis A between a proximal end 13 and a distal end (shaft end) 14. A plurality of teeth 15 may be formed at the proximal end. A male connecting section 16 is defined adjacent to the distal end 14. A first flange 18 extends outward from the shaft 12 adjacent to the male connecting section 16 at a distance from the distal end 14 and extends annularly around the shaft 12. The distal end 14 defines a recess 20 extending axially therein along the axis A. The recess 20 is used as a centering feature during a rolling operation of the teeth 15 and can provide a common interface between a standard half-shaft IC shaft, which is toothed at both ends and has a polygonal shape.It also improves material flow in dies when polygonal surfaces 38 of the male connecting section 16 (discussed in more detail below) are formed, and offers mass savings.

[0020] A hub 22 extends along the shaft 12 and is rotatable about the axis A, terminating axially at a connecting end (hub end) 24. The hub 22 has a second flange 26 at the connecting end 24 for positioning in an axially adjacent end-to-end relationship with the male connecting section 16 of the shaft 12. The hub 22 defines a female connecting section 28 at the connecting end 24, preferably in the form of a pocket 28, for receiving and coupling with the male connecting section 16 to allow torque to be transmitted between the shaft 12 and the hub 22. It should be understood that the male connecting section 16 could alternatively be located on the hub 22 and the female connecting section 28 could be located on the shaft 12 without deviating from the scope of the present invention.

[0021] As in Fig. As best shown in Figure 2, a seal 30 is arranged axially between the first and second flanges 18, 26 to prevent fluids from passing between them. A fastening mechanism 32, preferably in the form of a clamp 32, fixes and pre-tensions the first and second flanges 18, 26 against each other. However, other fastening mechanisms can be used, such as a threaded section and nut / bolt.

[0022] The male connecting section 16 has a generally polygonal radial outer surface 34 ( Fig. 4B, Fig. 4C, Fig. 5), and the female connecting section 28 has a generally polygonal radial inner surface 36 ( Fig. 3B, Fig. 3C and Fig. 5) wherein the male and female connecting sections 16, 28 generally have the same size and shape as each other, such that the male connecting section 16 is nested within the female connecting section 28 to transmit torque therein. The polygonal shape in this case is defined along a plane extending transversely through axis A. The radially outer surface 34 exhibits a plurality of outer faces 38 and the radially inner surface 36 exhibits a plurality of substantially corresponding inner faces 40 to provide the nesting relationship between the male and female connecting sections 16, 28.According to the exemplary embodiment, six outer surfaces 38 and six inner surfaces 40 are provided; however, more or fewer outer and inner surfaces 38, 40 can be provided in different lengths and angles to suit specific design requirements without deviating from the scope of the present invention. As will be discussed in more detail below, the term "polygonal," as used herein, does not require flat / planar outer and inner surfaces 38, 40. Rather, they are preferably slightly curved or include other minor irregularities.

[0023] As in Fig. As best shown in Figure 4C, the outer surfaces 38 of the male connecting section 16 are each slightly concave in one circumferential direction with a first circumferential radius R1. Accordingly, as in Fig. Figures 3B-3C best show that the inner surfaces 40 of the female connecting section 28 are slightly convex in shape in the circumferential direction at a second circumferential radius R2. The first and second circumferential radii R1, R2 are essentially the same as each other to provide uniform contact and uniform torque transmission between the male and female components 16, 28 during their rotation. It should be understood that alternatively, the outer surfaces 38 could be convex, while the inner surfaces 40 could be concave, without deviating from the scope of the present invention.

[0024] As in Fig. As best shown in Figure 2, the outer surfaces 38 of the male connecting section 16 taper radially inward and axially between the first flange 18 and the distal end 14 at a first angle A1. Similarly, the inner surfaces 40 of the female connecting section 28 taper radially inward as they extend axially away from the terminal end 24 essentially at the first angle A1, such that axially driving the male connecting section 16 into the female connecting section 28 wedges the male connecting section 16 into the female connecting section 28, thereby tightening the connection between the outer and inner surfaces 38, 40. This tapered arrangement of the outer and inner surfaces 38, 40 provides a self-centering and backlash-free coupling between the male and female connecting sections 16, 28.

[0025] As in Fig. 4C and Fig. As best shown in Figure 5, a multitude of outer transition areas 42 are located at the junction between adjacent outer surfaces 38 of the male connecting section 16 in the circumferential direction, in order to connect the adjacent outer surfaces 38 to one another. The outer transition areas 42 are each intersected at an outer radius R3. Similarly, with reference to Fig. 3B-3C and 5, a multitude of inner transition areas 44 are located at the junction between adjacent inner surfaces 40 of the female connecting section 28 in the circumferential direction, in order to connect the adjacent inner surfaces 40 to each other. The inner transition areas 44 are each intersected at an inner radius R4. As in Fig. As shown in Figure 5, a gap G1 is located radially between the outer and inner transition regions 42, 44. As shown, the gap G1 can be provided by making the outer radius R3 slightly larger than the inner radius R4, thus defining the gap G1 in between. The gap G1 helps ensure that all contact between the male and female connection sections 16, 28 occurs along the outer and inner surfaces 38, 40, as opposed to along the outer and inner transition regions 42, 44, thereby avoiding problems commonly associated with corner contact, such as material compliance and sloppy contact. This allows for greater tolerances during the manufacture of the male and female connection sections 16, 28, as flexibility is provided in the radial direction between the outer and inner transition regions 42, 44.In other words, the thickness of the gap G1 can vary during manufacturing without affecting the performance of the connection. Interconnecting, i.e., intersecting, the outer and inner transition regions 42, 44 reduces stress concentrations in the inner transition regions 44 of the female connection section 28 and allows a greater torque to be transmitted between the male and female connection sections 16, 28 of any given size.

[0026] As in Fig.As best shown in Figure 2, the male connection section 16 has a first axial radius R5 defined between the first flange 18 and each radially outer surface 34. Similarly, the female connection component 28 has a second axial radius R6 defined between the second flange 26 and each radially inner surface 36. A gap G2 is defined in the axial direction between the first and second axial radii R5, R6 to further ensure that complete contact occurs between the male and female connection sections 16, 28 along the outer and inner surfaces 38, 40, and to further provide tolerances during the manufacturing of the male and female connection sections 16, 28. The gap G2 can be provided by the first axial radius R5, which is larger than the second axial radius R6, to define the gap there between them.

[0027] In light of the foregoing, in constant velocity joint applications, the shaft and hub connection assembly 10 allows the constant velocity joint connection to be separated from the axle / transaxle differential connections and housing seals, thus avoiding the disadvantages mentioned above with prior art connection assemblies. Furthermore, the shaft and hub connection assembly 10 provides a modular external connection that is reliable, simple in design, and easy to manufacture. Particularly preferred are the male and female connection sections 16, 28 configured to provide only surface contact along the outer and inner surfaces 38, 40 due to the arrangement of the matching first and second circumferential radii R1, R2, the axially tapered first angle A1, the mismatched outer and inner radii R3, R4, and the mismatched first and second axial radii R5, R6.This allows the contact pattern between the outer and inner surfaces 28, 40 to remain largely unchanged despite geometric errors during manufacturing, thus increasing the durability of the connection arrangement 10. Furthermore, larger tolerances are provided for the manufacturing of the male and female connection sections 16, 28, while still ensuring a good connection between them. Additionally, the outer and inner surfaces 38, 40, the first and second circumferential radii R1, R2, the axially tapered angle A, the mismatched outer and inner radii R3, R4, and the mismatched first and second axial radii R5, R6 are simple to design and therefore do not require specialized tooling for machining. From a quality control standpoint, they are easily inspected to ensure accurate manufacturing.In addition, the overlapping conical arrangement of the outer and inner surfaces 28, 40 provides self-centering and prevents play during operation.

[0028] Obviously, many modifications and variations of the present invention are possible in light of the above teachings and can be implemented differently than specifically described, while remaining within the scope of the appended claims. These preceding statements should be interpreted to cover every combination in which the inventive novelty exerts its benefit. It should be understood that the term "essentially," as used herein, permits minor variations / irregularities.

Claims

[1] Shaft and hub connection arrangement (10) for transmitting torque, comprising: a shaft (12) which extends along a and is rotatable about an axis (A) and terminates axially at a shaft end (14); a hub (22) which extends along the and is rotatable about the axis (A) and terminates axially at a hub end (24); a first flange (18) which extends outwards from the shaft (12) at a distance from the shaft end (14) and extends in a ring shape around the shaft (12); a second flange (26) extending from the hub (22), adjacent to the hub end (24), to be positioned in an adjacent axial end-to-end relationship with the first flange (18); a fastening mechanism (32) which engages with the first and second flanges (18, 20) and preloads them against each other; wherein one of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a male connecting section (16), and the other of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a female connecting section (28) for receiving and being coupled with the male connecting section (16); wherein the female connecting section (28) has a radially inner surface (36) defined by a plurality of inner surfaces (40); wherein the male connecting section (16) has a radially outer surface (34) defined by a plurality of outer surfaces (38) nested within the plurality of inner surfaces (40) to couple the male and female connecting sections (16, 28) together; wherein the radially outer surface (34) of the male connecting section (16) has a plurality of outer transition regions (42), each of the plurality of outer transition regions (42) being arranged between and connecting adjacent persons of the plurality of outer surfaces (38) in a circumferential direction along an outer radius (R3); and the radially inner surface (36) of the female connecting section (28) has a plurality of inner transition regions (44), each of the plurality of inner transition regions (44) being arranged between and connecting adjacent persons of the plurality of inner surfaces (40) in the circumferential direction along an inner radius (R4); and a first gap (G1) defined between adjacent areas of the plurality of outer and inner transition regions (42, 44) to provide tolerances in the radial direction during the manufacture of the male and female components. [2] Shaft and hub connection arrangement (10) according to claim 1, wherein the outer radius (R3) is larger than the inner radius (R4) to define the gap (G1) between the outer and inner transition areas (42, 44). [3] Shaft and hub connection arrangement (10) according to claim 1, wherein the outer surfaces (38) of the male connection section (16) are concave along a first circumferential radius (R1) and wherein the inner surfaces (40) of the female connection section (28) are convex along a second circumferential radius (R2) which is substantially the same as the first circumferential radius (R1). [4] Shaft and hub connection arrangement (10) according to claim 1, further comprising: a first axial radius (R5) defined between the first flange (18) and one of the radially outer and inner surfaces (34, 36), and a second axial radius (R6) defined between the second flange (26) and the other of the radially outer and inner surfaces (34, 36); and a second gap (G2) defined between the first axial radius (R5) and the second axial radius (R6) such that total contact occurs between the male and female connecting sections (16, 28) along the outer and inner surfaces (38, 40). [5] Shaft and hub connection arrangement (10) according to claim 4, further comprising a seal (30) arranged axially between the first and second flange (18, 26) to prevent fluid from passing between the first and second flange (18, 26). [6] Shaft and hub connection arrangement (10) according to claim 1, wherein the fastening mechanism (32) is a clamp. [7] Shaft and hub connection arrangement (10) according to claim 1, wherein the outer and inner surfaces (38, 40) each taper radially inwards, so that axial movement of the male connection section (16) into the female connection section (28) wedges the male connection section (16) into the female connection section (28). [8] Shaft and hub connection arrangement (10) according to claim 1, wherein the shaft end (14) of the shaft (12) defines a recess (20) extending axially in the shaft (12). [9] Shaft and hub connection arrangement (10) according to claim 1, wherein both the radial outer surface (34) of the male connection section (16) and the radial inner surface (36) of the female connection section (28) have a generally polygonal shape. [10] Shaft and hub connection arrangement (10) according to claim 9, wherein the plurality of outer surfaces (38) of the radial outer surface (34) comprises six outer surfaces and wherein the plurality of inner surfaces (40) of the radial inner surface (36) comprises six inner surfaces. [11] Shaft and hub connection arrangement (10) for transmitting torque, comprising: a shaft (12) which extends along a and is rotatable about an axis (A) and terminates axially at a shaft end (14); a hub (22) which extends along the and is rotatable about the axis (A) and terminates axially at a hub end (28); wherein one of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a male connecting section (16), and the other of the shaft end (14) of the shaft (12) and the hub end (24) of the hub (22) defines a female connecting section (28) for receiving and being coupled with the male connecting section (16); wherein the female connecting section (28) has a radially inner surface (36) defined by a plurality of inner surfaces (40); wherein the male connecting section (16) has a radially outer surface (34) defined by a plurality of outer surfaces (38) and are nested within the plurality of inner surfaces (40) to couple the male and female connecting sections (16, 28) together; a first flange (18) extending outwards from the shaft (12) at a distance from the shaft end (14); a second flange (26) extending from the hub (22), adjacent to the hub end (24) and positioned in an axial end-to-end relationship with the first flange (18); wherein a first axial radius (R1) is defined between the first flange (18) and one of the radially outer and inner surfaces (34, 36), a second axial radius (R2) is defined between the second flange (26) and the other of the radially outer and inner surfaces, and a gap (G1) is defined between the first axial radius (R1) and the second axial radius (R2), such that total contact occurs between the male and female connection sections (16, 28) along the outer and inner surfaces (38, 40). [12] Shaft and hub connection arrangement (10) according to claim 11, wherein the first axial radius (R1) is larger than the second axial radius (R2) to define the gap (G1). [13] Shaft and hub connection arrangement (10) according to claim 11, wherein the radially outer surface (34) of the male connection section (16) has a plurality of outer transition regions (42), each of the plurality of outer transition regions (42) being arranged between and connecting adjacent persons of the plurality of outer surfaces (38) in a circumferential direction along an outer radius (R3), wherein the radially inner surface (36) of the female connection section (28) has a plurality of inner transition regions (44), each of the plurality of inner transition regions (44) being arranged between and connecting adjacent persons of the plurality of inner surfaces (40) in the circumferential direction at an inner radius (R4), and wherein a first gap (G1) is defined between adjacent persons of the plurality of outer and inner transition regions (42, 44),to provide tolerances in the radial direction during the manufacture of the male and female components. [14] Shaft and hub connection arrangement (10) according to claim 11, wherein the outer and inner surfaces (38, 40) each taper radially inwards, so that axial movement of the male connection section (16) into the female connection section (28) wedges the male connection section (16) into the female connection section (28). [15] Shaft and hub connection arrangement (10) according to claim 11: wherein each of the plurality of outer surfaces (38) of the male connecting section (16) is shaped either concave or convex along a first circumferential radius (R1); and Each of the multiple internal surfaces (40) of the female connecting section (28) is shaped oppositely concave or convex along a second circumferential radius (R2) which is essentially the same as the first circumferential radius (R1). [16] Shaft and hub connection arrangement (10) according to claim 15, wherein the shaft end (14) of the shaft (12) defines a recess (20) which extends axially in the shaft (12).

Images