Classifications

• • G—PHYSICS
  • G01—MEASURING; TESTING
  • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
  • G01M1/00—Testing static or dynamic balance of machines or structures
  • G01M1/14—Determining imbalance
  • G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
  • G01M1/28—Determining imbalance by oscillating or rotating the body to be tested with special adaptations for determining imbalance of the body in situ, e.g. of vehicle wheels

Definitions

• the invention relates to a device according to the preamble of claim 1, as known from DE 33 32 978 AI.
• a device of this type for measuring forces which are generated by an imbalance of a rotor it is known to rotatably mount the measuring shaft in two bearing units which are axially spaced apart and which are supported by force sensors against a hollow bearing housing.
• This measuring shaft bearing is supported by a fixed frame.
• the measuring shaft is supported in a bearing having a force transducer on a stationary frame.
• two bearing levels in which the force transducers are also arranged, are provided for the mounting of the measuring shaft.
• a balancing machine for rotating bodies is known from EP 0 058 860 B1, in which the measuring shaft is rotatably mounted on an elastically flexible flat part arranged vertically on the machine bed.
• the rotary bearing of the measuring shaft is provided on the upper edge of the flat part.
• Position deflections of the flat part are detected by an arm extending at a right angle to the flat part by transducers whose force introduction directions are perpendicular to one another.
• One sensor takes the static one
• a vibration measuring (supercritical) measuring system is known with a bearing for the rotor on diagonally positioned leaf springs, the extensions of which form a virtual intersection in one of the compensation planes of the rotor to be balanced.
• the two diagonally positioned leaf springs are supported against a base plate by means of an intermediate plate on perpendicular leaf springs arranged parallel to one another.
• the vibrations of the leaf springs resulting from a rotor imbalance are detected by means of vibration transducers and converted into corresponding measurement signals.
• the forces measured by the force transducers in the two bearing levels are therefore dependent on the respective distance that the rotor has from the two force transducers. Since these distances are different, there is a change in the sensitivity of one of the two transducers due to different effects, such as temperature, aging, impact, overload, transporter vibration, moisture influence and the like. , a disproportionate error in the compensation masses calculated for the respective compensation levels.
• the object of the invention is to provide a device of the type mentioned in the introduction, in which a change in sensitivity of a measuring transducer has only a minor effect on the mass balancing to be carried out in the balancing planes, for example by means of balancing weights to be applied, due to the dynamics of force explained above.
• the rigid intermediate frame on which the measuring shaft is supported in a bearing plane having a force sensor, is supported on the stationary frame by means of a further force sensor.
• the two force sensors are thus located in two bearing systems for force-measuring imbalance detection, with each force sensor being assigned to one of the two bearing systems.
• the two bearing systems are located between the measuring shaft and the rigid frame, for example the balancing machine, on which the unbalance measurement and the unbalance compensation are carried out on a motor vehicle wheel.
• the force transducers can be in different storage levels, but in the area of the rigid intermediate frame, or in a common storage level.
• the design of the two bearing systems mentioned above provides at least one further support for the measuring shaft, which has the property of a virtual bearing point in a further bearing level.
• Two such storage levels with such virtual storage locations can also be provided.
• the virtual storage locations can go to both
• the two force transducers are preferably arranged in a common bearing plane, which runs perpendicular to the axis of the measuring shaft.
• the forces introduced as reaction forces in the force transducers are aligned parallel to one another, in particular coaxially, and are located in the common bearing plane.
• the force transducers can be located in the axial extent of the intermediate frame in different bearing levels.
• a preferred embodiment consists in that the measuring shaft is supported on the intermediate frame in a first bearing plane having the force transducer and in a second bearing plane having the virtual support point, and that the intermediate frame is supported on the fixed frame in one bearing plane via the second force transducer and further is articulated on the stationary frame by means of a parallel guide.
• the bearing level can be located between the rotor, in particular the motor vehicle wheel, and the bearing level, which has the two force transducers, or preferably between the two compensation planes of the rotor, in particular the motor vehicle wheel.
• the intermediate frame can be supported on the stationary frame via a pair of support levers and joints at the respective ends of the support levers.
• the measuring shaft can also be supported on the intermediate frame via a pair of support levers and joints at the lever ends.
• the axes of the respective joints run perpendicular to the plane in which the forces introduced into the force transducers and the axis of the measuring shaft lie.
• the A pair of support levers, which supports the intermediate frame on the stationary frame, can at the same time bring about the parallel guidance of the intermediate frame on the stationary frame. For this purpose, the support levers run parallel to each other.
• the support levers at an angle to one another, the apex of the angle preferably being in the axis of the measuring shaft or in the vicinity of this measuring shaft axis.
• the joints of the support levers then lie in the corners of a trapezoid of the layout of the support levers.
• This arrangement creates the virtual bearing point on the outer side of the rotor.
• the virtual bearing point of the measuring shaft on the intermediate frame, which lies within the rotor, in particular between the compensation planes, can likewise be formed by support levers arranged at an angle to one another, the joints of which lie in the corners of a trapezoidal layout of the support lever arrangement.
• the support levers are preferably designed as rigid flat parts, for example sheet metal parts, castings, rolled flat parts and the like, which together with the joints ensure that the desired, for example essentially linear and coaxial, force application takes place in the measuring transducers.
• the support lever arrangement which is formed from the flat parts, can be made in one piece, the flat parts being designed to be rigid and only the joints lying therebetween, which are essentially linear, are flexible.
• the joints can be formed by weak points, for example constrictions between the individual rigid flat parts. As a result, flexible joint axes are formed between the rigid flat parts.
• the virtual storage locations are also the measurement locations taken into account in the frame computer of the balancing machine, which represent virtual measurement locations.
• Fig. 1 shows a first exemplary embodiment
• Fig. 2 shows a second exemplary embodiment
• Fig. 3 shows a third exemplary embodiment
• Fig. 4 shows a fourth exemplary embodiment
• Fig. 5 shows a fifth exemplary embodiment
• Fig. 6 shows a sixth embodiment
• Fig. 7 shows a plan view of a measuring arrangement and bearing for the measuring shaft, as can be used in the embodiments of FIGS. 1, 3 and 5;
• FIG. 8 is a perspective view of the measuring arrangement of FIG. 7 seen from the top front;
• FIGS. 7 and 8 a perspective view of the measuring arrangement of FIGS. 7 and 8 seen from the side from above;
• Fig. 10 a seventh embodiment.
• a schematic representation of a rotor 1 is shown in the figures, which is used to measure the unbalance on a measuring shaft 2 is fixed in a known manner by clamping means, not shown.
• the measuring shaft 2 is rotatably mounted on a stationary frame 6. This can be the machine frame of a wheel balancing machine.
• the storage takes place with the help of a storage 3 to be described in detail, which also has force transducers 4, 5.
• the bearing 3 can have a tubular rotary bearing 26 in which the measuring shaft 2 is rotatably mounted.
• the rotary bearing 26, which receives the measuring shaft 2 is rigidly mounted in a first bearing plane 8 on an intermediate frame 7 via the force transducer 4.
• a virtual support point 24 is created in a further bearing plane 9 by support levers 13, 14, which form a pair of support levers and extend at an angle to one another.
• the support point 24 acts like a pivot axis which runs perpendicular to the axis 23 of the measuring shaft 2 and perpendicular to the direction of force introduction of the reaction forces resulting from the unbalance measurement into the force transducer 4.
• the support levers 13 and 14 are articulated (articulations 19 and 22) to the intermediate frame 7 and articulated (articulations 20, 21) to the rotary bearing 26 for the measuring shaft 2.
• the joint axes of the joints 19 to 22 run parallel to the pivot axis, which is formed in the virtual bearing point 24.
• the virtual bearing point 24 can be located between the rotor 1 and the bearing plane 8, in which the force sensors 4 and 5 are located (FIGS. 1 and 2).
• the virtual bearing point 24 can, however, also be located in the area of the rotor, in particular between balancing planes 27 and 28, in which the unbalance compensation is carried out, for example by applying balancing weights (FIGS. 5 and 6).
• the intermediate frame 7 is supported on the stationary frame 6 via the force transducer 5.
• the force transducer 5 can be arranged in the bearing plane 8 lying perpendicular to the measuring shaft 2. However, it is also possible to arrange the force transducer 5 offset in the axial direction of the measuring shaft 2 in another bearing plane.
• the intermediate frame 7 is supported on the stationary frame 6 via a pair of support levers (support levers 11 and 12).
• the support levers 11, 12 are articulated to the stationary frame 6 (articulations 15, 16) and articulated (articulations 17, 18 in FIGS. 1, 3, 5, 10 and 7 to 9 and articulations 19, 22 in Figures 2, 4 and 6) connected to the intermediate frame 7.
• the intermediate frame 7 is designed as a rigid bearing block or rigid and rigid bearing frame.
• the support levers 11 and 12 run essentially parallel to one another and parallel to the axis 23 of the measuring shaft 2.
• the support levers 11 and 12 thus form a parallel link guide to the substantially perpendicular to the axis 23 of the measuring shaft 2 directed force introduction of the reaction forces resulting from the unbalance measurement run into the force transducer " 5.
• the two support levers 11 and 12 are arranged at an acute angle to one another, the apex of which lies in the axis 23 of the measuring shaft 2 or in the vicinity of the axis 23.
• This apex forms a further virtual bearing point 25 in a bearing plane 10 which extends perpendicular to the measuring shaft 2 and which lies on the outside of the rotor 1.
• the virtual bearing point 25 and the bearing plane 10 lie in an extension of the measuring shaft 2, which is drawn in dash-dotted lines and which runs opposite the bearing 3 of the measuring shaft 2 to the longitudinal extension of the measuring shaft 2.
• the bearing point 25 and the associated bearing level 10 lie with respect to the bearing 3 on the side opposite the rotor 1.
• the virtual bearing point 25 also has the property of a swivel axis which is perpendicular to the axis 23 of the measuring shaft 2 and perpendicular to the direction of introduction of the force introduction into the force transducers 4 and 5. In the illustrated embodiments, this force is introduced in the bearing plane 8.
• the joint axes of the joints 15 to 22 run parallel to one another and perpendicular to the axis 23 of the measuring shaft 2 and to the direction of force introduction of the reaction forces into the Force transducers 4 and 5 in bearing level 8.
• bearing planes 9 and 10 with the virtual bearing points 24 and 25 are created on both sides of the rotor 2, namely on the inside width and the outside of the rotor.
• the virtual storage locations 24 and 25 have the properties of virtual measuring locations. Forces L assigned to the inner bearing point 24 are introduced into the force sensor 4 by the force transducer 5 and forces R assigned to the bearing point 25.
• the force transducers generate corresponding transducer signals L 'and R'.
• the one virtual bearing point 24, at which a centrifugal force L resulting from the rotor balance can act is located in the bearing plane 9 between the two compensation planes 27, 28, preferably approximately in the middle between the two compensation planes 27, 28.
• the other virtual bearing point 25 is located with respect to the bearing 3 of the measuring shaft 2 on the other side in the extension of the measuring shaft.
• a centrifugal force R resulting from the rotor imbalance acts here.
• the measuring sensors 4 and 5 deliver measuring signals R 'and L' proportional to the centrifugal forces R and L.
• the outer virtual bearing is infinite or at a relatively large distance of a few meters, for example between about 3 to 20 m and more, since the support levers 11 and 12 essentially cause the intermediate frame 7 to be guided in parallel.
• a centrifugal force resulting from the rotor imbalance (L in FIGS. 1 and 2 and S in FIGS. 5 and 6) is introduced at the virtual bearing point (virtual measuring location) in the bearing level 9 (virtual measuring level), it is initiated this force is only detected by the force transducer 5 and emits a proportional signal L 'or S'.
• the force transducer 4 emits no signal.
• the force transducer 5 will emit a signal that is only proportional to the centrifugal force size due to the parallel guidance of the intermediate frame 7.
• the force transducer 4 will emit a measurement signal M 'which is not only proportional to the centrifugal force magnitude and thus the unbalance magnitude, but also to the distance of the force introduction point from the bearing level 9 or the virtual bearing point 24.
• the intermediate frame 7 is supported on the stationary frame 6 with the aid of the pair of support levers formed from the support levers 11 and 12 and the tubular rotary bearing 26 of the measuring shaft 2 is supported with the help of the pair of support levers formed from the support levers 13 and 14 seen in the axial direction of the measuring shaft 2 one behind the other.
• the pairs of support levers of the embodiments of FIGS. 3 and 4 have the same direction of inclination. In the exemplary embodiment 11, 12, the direction of inclination is opposite to the direction of inclination of the pair of support levers 13, 14. In the embodiments of FIGS.
• the support frame 7 is supported on the fixed frame 6 and the pivot bearing 26 the measuring shaft 2 on the intermediate frame 7 with the respective pairs of support levers 11, 12 and 13, 14 side by side or one above the other.
• the joints 17, 19 and 18, 22 can coincide in the joint joints 19 and 22 on the intermediate frame 7, as shown in FIGS. 2, 4 and 6.
• the support levers 11 to 14 can be formed from flat parts which are rigid and rigid.
• the flat parts can be formed from one piece, the joints being characterized by linear weak points, e.g. are formed in the form of constrictions.
• a holding plate 33 which is part of the holding device 29, can also be formed from the piece that forms the flat parts for the support levers 11 to 14.
• the holding plate 33 is fixedly connected to the tubular rotary bearing 26, for example by welding.
• a support bracket 34 can also be provided as part of the holding device 29, which is also firmly connected to the holding plate 3 and the rotary bearing 26, for example by welding.
• the upper support bracket 34 is shown in the figures. A lower support angle can also be provided.
• the upper and lower support brackets can also consist of an angle piece, in which the pivot bearing 26 is guided through an opening in the angle piece and fixed, e.g. is connected to the contra-angle by welding. This creates a rigid and rigid connection between the holding device 29 and the pivot bearing 26 between the two joints 20 and 21.
• the joints 20 and 21 are located between the two support levers 13 and 14 and the holding plate 33.
• ten 37, 38 and 40, 41 be formed.
• the mounting plates 37, 38 are fixed, for example by screw connections or otherwise connected to the fixed frame 6.
• the fastening plates 37 and 38 form the fastening points for the support lever arm formed from the support levers 11 and 12, with which the intermediate frame 7 is supported on the stationary frame 6.
• the joints 15 and 16 formed by the line-shaped weak points or constrictions are provided between the fastening plates 37 and 38 and the flat parts which form the support levers 11 and 12.
• Weak points have a concave, in particular semicircular cross section.
• the two fastening plates 40 and 41 are formed from the one piece, which are fixed, for example by
• Screw connections, welding or the like are connected to side surfaces of the intermediate frame 7.
• the joints 17 and 18 are formed between the two fastening plates 40 and 41 and the support levers 11 and 12 due to the weak points or constrictions.
• the joints 19 and 22 are formed by weak points or constrictions.
• the parallel guidance of the intermediate frame 7 on the stationary frame results essentially from the fact that the baselines of the concave constrictions 15, 17 and 16, 18 on both sides of the support levers 11 and 12 approximately in parallel planes 35 and 36, in which the guiding function of the two support levers 11 and 12 is achieved.
• the respective constrictions 15, 17 and 16, 18 are located on opposite surfaces of the support levers 11 and 12 forming the flat parts.
• the support levers 11 and 12 are inclined at an extremely acute angle to one another, but, as already explained, the parallel link guidance by guiding function in the parallel planes 35 and 36 is achieved.
• corresponding measuring arrangements can be achieved in FIGS. 1 and 5.
• the support levers 11 and 12 can be inclined at a correspondingly larger angle to one another.
• the support levers 11, 12 in FIGS. 7 to 9 are directed towards one another at their rear ends.
• the rear constrictions or joints 15, 16 are closer to the axis of the measuring shaft 2 than the front constrictions or joints 17, 18.
• the two force transducers 4, 5 are arranged in an effective line, the force transducer 4 between the pivot bearing 6 and the inside of the intermediate frame 7 and the force transducer 5 between the outside of the intermediate frame 7 and the Mounting plate 41 (Fig. 9) and the fixed frame 6 are arranged.
• An electric motor 30 is provided for driving the measuring shaft 2, which drives the measuring shaft via a belt drive 31.
• the motor 30 is mounted on the pivot bearing 26 via a cantilever arm 32. Through this storage, the measurement result O 00/14503

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• Physics & Mathematics (AREA)
• General Physics & Mathematics (AREA)
• Testing Of Balance (AREA)
• Force Measurement Appropriate To Specific Purposes (AREA)

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Citations (8)

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• 1999
  • 1999-08-30 BR BRPI9908457-0A patent/BR9908457B1/pt not_active IP Right Cessation
  • 1999-08-30 JP JP2000569202A patent/JP4344096B2/ja not_active Expired - Fee Related
  • 1999-08-30 PL PL342762A patent/PL191114B1/pl unknown
  • 1999-08-30 ES ES99946065T patent/ES2173000T3/es not_active Expired - Lifetime
  • 1999-08-30 AT AT99946065T patent/ATE214477T1/de not_active IP Right Cessation
  • 1999-08-30 NZ NZ506942A patent/NZ506942A/xx unknown
  • 1999-08-30 AU AU58567/99A patent/AU751140B2/en not_active Ceased
  • 1999-08-30 DK DK99946065T patent/DK1108204T3/da active
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  • 1999-08-30 RU RU2000124867/28A patent/RU2245528C2/ru not_active IP Right Cessation
  • 1999-08-30 US US09/646,157 patent/US6430992B1/en not_active Expired - Lifetime
  • 1999-08-30 EP EP99946065A patent/EP1108204B1/de not_active Expired - Lifetime
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