WHEEL-FORCE DYNAMOMETER FOR MEASURING TIRE FORCES

Abstract

A wheel-force dynamometer (1) for the measurement of forces and torques acting upon a vehicle tire (2a) and a vehicle wheel (2) using force sensors (4, 24, 44). The vehicle wheel (2) is mounted and able to rotate on a wheel axle. The wheel-force dynamometer (1) has a wheel axle that is in the form of a hollow shaft (9, 29, 49) which is hydrostatically mounted on a rigid, fixed in position bearing journal (3, 23, 43).

Claims

1-17. (canceled)

18. A wheel-force dynamometer for measurement of force and torque acting upon a vehicle tire (2a) and a vehicle wheel (2) by force sensors (4, 24, 44), the vehicle wheel (2) being rotatably supported by a wheel axle, and the wheel axle being in a form of a hollow shaft (9, 29, 49) which is mounted on a rigid, positionally fixed bearing journal (3, 23, 43).

19. The wheel-force dynamometer according to claim 18, wherein the bearing journal is a hollow journal (3, 23, 43).

20. The wheel-force dynamometer according to claim 19, wherein the hollow journal (3, 23, 43) has an outer end, on a wheel side, an inner end and a supporting annular cross-section, and the supporting annular cross-section increases from the outer end toward the inner end.

21. The wheel-force dynamometer according to claim 18, wherein the bearing journal is a hollow journal, and a radial periphery of the hollow journal (3, 23, 43) varies so that, in an axially central zone, either the hollow journal (3, 23, 43) tapers in a manner of a cone or the hollow journal (3, 23, 43) thickens in a manner of a cone.

22. The wheel-force dynamometer according to claim 18, wherein the hollow shaft (9, 29, 40) is mounted relative to the bearing journal (3, 23, 43) by hydrostatic slide bearings (6, 7, 8, 26, 27, 28, 46, 47).

23. The wheel-force dynamometer according to claim 18, wherein the bearing journal (3, 23, 43) has a collar (3c), which is supported on a positionally fixed supporting structure (5, 25, 45).

24. The wheel-force dynamometer according to claim 23, wherein the force sensors (4, 24, 44) are arranged between the collar (3c) and the supporting structure (5, 25, 45).

25. The wheel-force dynamometer according to claim 22, wherein a first hydrostatic slide bearing is in a form of a radial bearing (6, 26) arranged at a wheel-side end of the bearing journal (3, 23) and a second hydrostatic slide bearing is in a form of a radial bearing (7, 27) arranged at an inside end of the bearing journal (3, 23).

26. The wheel-force dynamometer according to claim 25, wherein a third hydrostatic slide bearing is designed as an axial bearing (8, 28).

27. The wheel-force dynamometer according to claim 26, wherein the second and third hydrostatic slide bearings are in a form of a combined, L-shaped radial and axial bearing (7, 8).

28. The wheel-force dynamometer according to claim 21, wherein a first and a second hydrostatic slide bearing are in a form of conical bearings (46, 47), which are arranged at a location where the radial periphery of the bearing journal (3, 23, 43) changes.

29. The wheel-force dynamometer according to claim 26, wherein the axial bearing (28) is arranged inside the hollow bearing journal (23) and is connected to the hollow shaft (29) by a supporting shaft (34).

30. The wheel-force dynamometer according to claim 18, wherein an end of the hollow shaft (9, 29) is connected to a supporting disk (11, 31).

31. The wheel-force dynamometer according to claim 30, wherein the supporting disc (11, 31) is connectable to the vehicle wheel (2, 22).

32. The wheel-force dynamometer according to claim 31, wherein a wheel flange adapter is arranged between the supporting disk (11, 31) and the vehicle wheel (2, 22).

33. The wheel-force dynamometer according to claim 29, wherein the supporting shaft (34) is connected to the hollow shaft (29) by way of a supporting disk (31).

34. The wheel-force dynamometer according to claim 30, wherein a centering ring (13) is arranged on the supporting disk (11).

35. A wheel-force dynamometer for measurement of force and torque acting upon a vehicle tire and a vehicle wheel, the wheel-force dynamometer having force sensors arranged between a positionally fixed supporting structure and a first axial end of a rigid, fixed bearing journal, the bearing journal being supported by the supporting structure, a wheel axle having a wheel end that is connected to the vehicle wheel and opposite to the supporting structure, the wheel axle being hollow and rotationally supported, via hydrostatic slide bearings, on an outside surface of the bearing journal, the bearing journal being hollow and having an inside surface that is conically shaped such that an axial cross section of the bearing journal increases from a second axial end of the bearing journal toward the first axial end of the bearing journal.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Example embodiments of the invention are shown in the drawings and will be described in greater detail below, so that further features and/or advantages can emerge from the description and/or the drawings, which show:

[0019] FIG. 1: A first example embodiment of the invention for mounting a wheel on a wheel-force dynamometer by means of a hollow shaft and bearing journal,

[0020] FIG. 2: A second example embodiment of the invention, for a wheel mounting with an alternative axial bearing, and

[0021] FIG. 3: A third example embodiment of the invention for a wheel mounting with two conical bearings.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] FIG. 1 shows, as a first example embodiment of the invention, a wheel-force dynamometer 1, i.e. a device for measuring forces and torques on a rotating vehicle wheel 2, also just called the wheel 2 for short in what follows. In particular this is used for measuring the uniformity of tires and wheels at high speeds, namely measuring the High Speed Uniformity (HSU). The wheel-force dynamometer 1, or measurement device 1 for short in what follows, comprises a rigid bearing journal 3 supported via force sensors 4 on a positionally fixed supporting structure 5. The bearing journal 3 is in the form of a hollow journal and has an inside surface 3a which is partially conical and partially cylindrical, so that in the direction toward the supporting structure 5 it has an increasing supporting annular cross-section. The hollow journal 3 also has a substantially cylindrical bearing seat 3b and a relatively solid collar 3c by which the bearing journal 3 is supported. On the bearing seat 3b are arranged a first hydrostatic slide bearing 6 in the form of a radial bearing, a second hydrostatic slide bearing 7 in the form of a radial bearing, and a third hydrostatic slide bearing 8 in the form of an axial bearing. A hollow shaft 9 is supported radially and axially relative to the hollow journal 3 by the hydrostatic slide bearings 6, 7 and 8. The first and second hydrostatic slide bearings 6, 7 have on theft outer periphery lubrication pockets 6a, 7a, which are supplied with lubrication oil by a pressure oil delivery system (not shown), so that a permanent lubricant film is maintained between the radial bearings 6, 7 and the inside surface of the hollow shaft 9. At its end facing the collar 3c, the hollow shaft 9 has a pressure ring 10 which is attached on one side to the hollow shaft 9 and rests against the axial bearing 8. Thus, the hollow shaft 9 is fixed to the bearing journal 3 in the axial direction. The vehicle wheel 2 is fixed to the hollow shaft 9 by means of a supporting disk 11 arranged on and fixed to the end of the hollow shaft 9 facing toward the wheel 2. The wheel 2 has a tire 2a arranged on a wheel rim 2b, also called the rim 2b for short. The rim 2b is connected to the supporting disk 11 by a wheel flange adapter 12. In addition a centering ring 13 is provided, which ensures that the wheel 2 is centered relative to the hollow shaft 9. In the area of the first radial bearing 6, the hollow shaft 9 has a maximum outer diameter which is limited by the inside diameter of the wheel rim 2b; the fitting space present inside the rim 2b is thus used optimally in favor of a maximum modulus of resistance of the hollow shaft 9.

[0023] The mounting of the wheel 2 relative to the positionally fixed supporting structure 5 is designed as a rigid assembly so that the measurement device 1 has an as high as possible natural frequency. Thus, the measurement frequency at which the forces and torques are determined in a HSU measurement is substantially lower than the natural frequency of the measurement device. Resonances between the natural frequency of the measurement device 1 and the measurement frequencies can thereby largely be avoided, so that resonance-related measurement errors such as amplitude elevations or phase shifts are minimized.

[0024] During the measurement the wheel 2 rolls on a real or simulated road (not shown), for example a running drum, and is loaded with a defined wheel load. The forces and torques resulting from this are transmitted via the wheel rim 2b and the supporting disk 11 to the hollow shaft 9 and from there via the hydrostatic slide bearings 6, 7, 8 to the bearing journal 3, which is supported by means of its collar 3c via the force sensors 4 on the supporting assembly 5.

[0025] FIG. 2 shows a second example embodiment of the invention for a wheel-force dynamometer 21. In the figure, the same or analogous components as in FIG. 1 are denoted by the same indexes, but increased by 20. A hollow shaft 29 is mounted by means of two hydrostatic slide bearings in the form of a first radial bearing 26 and a second radial bearing 27, on a bearing journal 23 in the form of a hollow journal, which is supported via force sensors 24 on a positionally fixed supporting structure 25. The free end of the hollow shaft 29 on the wheel side is connected solidly to a supporting disk 31, The outer diameter of the hollow shaft 29 is only slightly smaller than the inside diameter of the wheel rim 22b; accordingly, the total radial fitting space available is used to good effect for a maximum diameter of the hollow shaft 29. Instead of the axial bearing 8 shown in FIG. 1, in the second example embodiment according to FIG. 2 an alternative axial bearing 28 is arranged in the inside space of the hollow journal 23. A supporting shaft 34 is connected to a bearing disk 34a, which is arranged and can slide between the two axial bearings 28. At the other end, the supporting shaft 34 has a collar 34b, which is connected to the supporting disk 31 and thus to the hollow shaft 29, Axial forces that act upon the hollow shaft 29 and hence upon the supporting disk 31 are supported in the axial direction by the supporting shaft 34, which is axially fixed by a pressure disk 30 attached to the bearing journal 23.

[0026] FIG. 3 shows a third example embodiment of the invention for a wheel-force dynamometer 41. In the figure the same or analogous components as in FIG. 1 are denoted by the same indexes, but increased by 40. A hollow shaft 49 is mounted relative to a bearing journal 43 by means of a first and a second hydrostatic slide bearings 46, 47 in the form of conical bearings 46, 47, which journal is supported via force sensors 44 on a positionally fixed supporting structure 45. In this case the conical bearings 46, 47 are arranged externally on the hollow journal. The free end of the hollow shaft 49 facing toward the wheel is connected solidly to a supporting disk 51. The outer diameter of the hollow shaft 49 is only very slightly smaller than the inside diameter of the wheel rim 42b. Thus, the total radial fitting space available favors a maximum diameter of the hollow shaft 29, As shown in FIG. 3, in the area of the conical bearings 46, 47 the hollow journal 43 has a radial periphery variation that tapers in a conical manner in an axially central zone. Due to the conical taper the prerequisite for designing the two slide bearings 46, 47 as conical bearings 46, 47 is provided. Thus, the example wheel-force dynamometer shown in FIG. 3 requires only two hydrostatic slide bearings 46, 47 in order to transmit all the forces and torques from the hollow shaft 49 to the hollow journal 43. Since the hollow journal tapers conically in an axially central zone, the pressure effect lines perpendicular to the cone extend outward. Thus the two conical bearings form an O-arrangement which can absorb torques particularly well.

INDEXES

[0027] 1 Wheel-force dynamometer [0028] 2 Wheel [0029] 2a Tire [0030] 2b Wheel rim [0031] 3 Bearing journal [0032] 3a Inside surface [0033] 3b Bearing seat [0034] 4 Force sensor [0035] 5 Supporting structure [0036] 6 First slide bearing [0037] 7 Second slide bearing [0038] 8 Third slide bearing [0039] 9 Hollow shaft [0040] 10 Pressure ring [0041] 11 Supporting disk [0042] 12 Wheel flange adapter [0043] 13 Centering ring [0044] 21 Wheel-force dynamometer [0045] 22 Wheel [0046] 23 Bearing journal [0047] 24 Force sensor [0048] 25 Supporting structure [0049] 26 First slide bearing [0050] 27 Second slide bearing [0051] 28 Third slide bearing [0052] 29 Hollow shaft [0053] 30 Pressure disk [0054] 31 Supporting disk [0055] 34 Supporting shaft [0056] 34a Bearing disk [0057] 34b Collar [0058] 41 Wheel-force dynamometer [0059] 42 Wheel [0060] 42a Tire [0061] 42b Wheel rim [0062] 43 Bearing journal [0063] 43c Collar [0064] 44 Force sensor [0065] 45 Supporting structure [0066] 46 First slide bearing [0067] 47 Second slide bearing [0068] 49 Hollow shaft [0069] 51 Supporting disk [0070] 53 Centering ring