JPS60216237A - Method and machine for determining unbalance of wheel - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a method and apparatus for determining the unbalance of a rotating member, particularly a wheel, and more particularly to a method and apparatus for dynamically measuring the unbalance of a rotating member. The present invention relates to a possible method and apparatus. Although the invention is discussed below with particular reference to wheel balancing, it will be appreciated that aspects of the invention are applicable to other types of rotating members, such as rotors and the like. It will be understood that when this application refers to a "wheel," what is actually being counterbalanced is usually a wheel/tire combination, and that "wheel" includes this combination.

BACKGROUND OF THE INVENTION Two basic types of systems are currently available for determining the unbalance of a wheel with mounted tires. One of these types of systems is a static reed, in which the wheels and tires remain stationary, while any imbalance thereof is determined. For example, the wheels can be supported horizontally by a leveling type support having a bubble or similar such indicator that is displaced from a central reference point by the unbalance of the tire. By placing appropriate weights at strategic points around the rim of the wheel, the operator can vary the position of the bubble indicator until it is brought to the reference point.

Weights are then fixed to the wheels at these strategic points.

A second basic type of wheel balancing system, a dynamic balancing system, has been developed that provides a more complete indication of wheel unbalance and the manner in which the unbalance is corrected (m
anner).

In dynamic wheel balancing systems, the wheels to be balanced are mounted on a shaft that is brought up to a predetermined rotational speed.

Once the wheels have reached this required speed, a measurement is made of the lateral movement of the axle or the force exerted by the axle due to wheel imbalance. From these measurements an indication of the magnitude of wheel imbalance and the location of the imbalance can be generated.

While a dynamic balancing system can determine the position of an imbalance in a single plane, the method detects the balanced centrifugal forces existing in two planes, approximately the inner and outer planes of the wheel; can be distinguished and corrected. A more precise correction of the imbalance is thus achieved. The wheels are then removed from the balancing device.

Typically, the rotational speed of the wheel is 4 during the dynamic unbalance measurement.
It is kept constant at 0Or, p, tn or more. Such speeds have been used for several reasons. One is that it is easier to measure unbalanced forces at high speeds because the magnitude of unbalanced forces increases with the square of rotational speed. At high speeds, very favorable signal-to-noise ratios are easily obtained. Another reason was the commonly held but incorrect theory that the wheels should be balanced at a rotational speed that approximates road speed.

Borner and Jockson US Pat. No. 4,43
No. 5,982 discloses improvements in dynamic balancing devices)
In this, the rotational speed of the measurement is reduced to less than 3BOrpm, and the measurement of unbalance is performed by isolating the wheel drive system and "coasting" the wheels.
J -T--, ``Re, wawawawawataru.

Published British Patent No. 8,833,0356 to Borntr and Jookaon describes yet another improvement, in which the required rotational speed is further reduced to 100
rpfn and the wheels can be rotated and freewheeled.

Machines embodying the Borner-Jackson patents and applications are sold on the market. These balancing devices are characterized by their unbalance measurement when they are coasting down to a speed equal to one or several predetermined measures. This manually driven machine i-1 performs its function particularly well in this regard. However, this machine often
es) F) 4 = handled by an inexperienced person, but the wheel is turned by hand substantially beyond the required preset measuring speed (h
αnd 5pun) and incurs a lengthy wait to slow the wheels to that speed.

PROBLEM SOLVED BY THE INVENTION In these machines, and in other dynamic balancing devices known to the applicant, the carrier for the rotatable shaft on which the wheels are mounted is fixedly mounted on a pace or platform. The wheels are manually lifted onto the axle and added so that they leave the floor and rotate. This is a simple configuration which is quite useful when the wheels to be balanced are the wheels of a motorcycle or light vehicle. However, when the wheels are large and heavy, ie, large automobile or truck wheels, positioning and mounting can be difficult and dangerous.

Separate lifting equipment, such as a jack or forklift, positions the wheels and greatly increases wheel time and expense.

Another problem that arises when balancing large and heavy wheels is that the wheels are not easily portable, and it is often preferable to move the balancing device toward the wheels rather than vice versa. While the hand powered machines described above are portable, other balancing devices used heretofore are generally large piece devices that require permanent factory installation.

SUMMARY OF THE INVENTION It is therefore a general object of the present invention to solve the problem of unbalanced wheels, etc., which have the accuracy of other dynamic wheel balancing devices, but are operable without the limitation that they belong to them. An object of the present invention is to provide a new method and apparatus for determining the .

Another object of the present invention is to dynamically determine the unbalance of a wheel without requiring or using a predetermined rotational speed for performing the unbalance measurement, thus performing the measurement in a substantially uniform time. The objective is to provide a new device for

Yet another object of the present invention is to dynamically determine wheel imbalances on which wheels can be mounted so as to substantially reduce the effort and hazards associated with large wheel mounting in conventional operations. It is an object of the present invention to provide a novel method and apparatus for.

Yet another object of the present invention is to provide a novel table device for dynamically determining wheel imbalance that is portable, mobile, and suitable for field use.

In accordance with these and other objects, the present invention provides a novel wheel-based thresholding system that does not use preset measurement speeds and thus can determine wheel imbalance at any speed within a speed range. This includes a multiplying D/A converter that receives each one or more output signals provided by one or more force-measuring transducers of the balancing device and provides them to a microprocessor. It has been found that this can be achieved by a balancing device that uses an electronic measuring circuit that includes a measuring device. The microprocessor compares the above output signal to a threshold level and sends a command signal to the transducer to rotate the input signal by a certain amount or at a high speed (resulting in a relatively low amplitude input signal). These input signals, regardless of whether they are rotated or rotated (representing larger amplitude input signals), are processed within the microprocessor once they have been appropriately amplified so that they are within its operating range. It is possible to

Furthermore, the present invention has discovered that the wheel balancer can be implemented at very low speeds by means of an upwαrd adjustment of the small signal obtained at low speeds. This can be advantageously applied to balancing devices, such as truck wheels, where it is difficult, awkward, and dangerous to install thick wheels.

Additionally, the present invention provides a new system for a new dynamic balance wheel that does not require an operator to manually lift the wheel onto a rotatable balance shaft. This system includes a horizontal rotatable balance shaft adapted to support the wheels to be balanced. Preferably, this shaft is movable upwardly and downwardly relative to the base of the counterbalancing device and the ground, and the base itself is movable horizontally on the ground by means of wheels, rollers or skids. The balancing device is thus a mobile unit that can be brought to the wheel standing vertically and the balancing axis adjusted to a height that aligns exactly with the center of the wheel. After the wheels are attached to the axle, the axle is lifted until the wheels are off the ground. The wheel is then rotated and its imbalance determined. At that time, you can stop the rotation of the wheel. The wheel can be stopped by simply counteracting the wind resistance and bearing friction that slows it down, the counterbalancing device can be equipped with a braking mechanism, or preferably the rotating wheel can be stopped by simply counteracting the wind resistance and bearing friction that slow it down, or preferably the rotating wheel can be stopped by simply counteracting the wind resistance and bearing friction that slow it down, or preferably the rotating wheel can be stopped by simply counteracting the wind resistance and bearing friction that slows it down. The contact is stopped by lowering the wheel until it stops. The necessary weights to correct the imbalance are then attached to the vehicle. When the wheel is lowered to brake its rotation, the wheel must be raised entirely in order to properly position the correction weight. The axle with the attached wheel is then lowered until the wheel is again on the ground, then the wheel is removed from the balance shaft and the balance device can be moved away from the wheel. In a preferred embodiment of the principles of the invention, the vertical movement of the shaft relative to the base is somewhat oblique to a vertical plane passing through the horizontal counterbalance axis. This geometry allows the full weight of the wheel to be preloaded (p de agoαd) or the base of the balancer to self-lock (5elf 1ock) with a force that exceeds the maximum force of unbalance experienced in the balance. be. This accurately sustains the vibrations caused by an unbalanced rotating wheel and minimizes spurious movements and vibrations not caused by unbalanced forces on the wheel as the wheel is being rotated.

This shape and the preload to achieve it
d) increases the mobility of the device. ■ The rotatable balance shaft and its associated bearing support structure, as well as electronic equipment that is relatively precise and sensitive in nature, can be removed from the relatively sturdy and heavy base; can be transported without fear of damaging the counterbalance head, and the counterbalance head can be transported itself with better protection. The preload compensates for the gap and accounts for the play between the counterbalancing head assembly and the pace (
take up), whereby the gap between these two units creates a very large ease of incidental reassembly.

These aspects of the present invention relating to the use of non-preselected (7Lon-selected) balance speeds are advantageous for balancing large truck wheels, and thus the present invention relates to adjustable position axes. Although these aspects work with great advantage in combination, it will be appreciated that both of these aspects can be implemented separately. Thus, for example, the use of non-preselected speeds can be incorporated into a balancing system such as that described in Jackaon and Borner, US Pat. No. 444,885. Similarly, adjustable positioning axes can be used with other measurement circuits.

The manner in which the present invention achieves the foregoing objects and attendant advantages will become more fully understood upon reading the following detailed description of the preferred embodiments of the invention, as illustrated in the accompanying drawings.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1 of the present application, the wheel balancer head 8 illustrated therein includes a frame 10 which provides all mechanical and electrical support for the balancer head. Provides suitable structural support for the components. Frame 10 essentially comprises an elongated tube having a generally square or rectangular cross section. A tubular housing 12 is suspended from the top wall of frame 10 so that it can conduct forces in only one direction. The support mechanism for the housing 12 includes a pair of metal strips 14 and 16, which
It is sufficiently flexible to allow freedom of movement in two horizontal directions, ie in the direction indicated by A--B in FIG. The metal strip is stiff enough to resist elastic compression or stretching, thereby inhibiting vertical movement of the housing 12. Furthermore, the strips 14 and 16 are fixedly attached to both the frame 10 and the housing 12, so that they cannot pivot in a vertical plane, thereby preventing the longitudinal movement of the frame, i.e. relative to A-B. Suppress vertical movement. Additional supports for the housing 12 are mounted vertically to allow the necessary freedom of movement of the housing.

The balance shaft 20 is suitably journalled for rotation within the housing 12 by bearings 22 . A mounting flange or plate 24 is attached to one end of the axle 20 and provides a suitable support surface, whereas the wheel 25 to be counterbalanced is mounted on the axle 20. come into contact with A frustoconical hub mechanism can be screwed onto the axle 20 to lock the wheel to be balanced in place or otherwise lock the wheel in place as illustrated in FIGS. 2 and 3. can be bolted to plate 24 using bolts and lub nuts.

A timing disk 30 is mounted to the end of the shaft 20 opposite the mounting plate 240. The disk 30 has a number of radial slots or marks arranged around its periphery, which cooperate in a known manner with an electro-optical encoder 32 to ensure that the disk 30 is aligned with the shaft 20.
provides a pneumatic pulse signal regarding the rotational position and speed of the

The lateral forces caused by the unbalance of the wheels generated and measured by the rotating shaft 20 of the frame 1
0 and protrudes through one of the side walls of the housing 1.
2 is sensed by a piezoelectric transducer 34,36 that engages 2.

The base of the housing 12 may include a boss 40 that projects from the side of the housing 12 so that the housing engages only the transducer elements 34 and 36 and is not supported on any other portion of the frame 10. Guarantee that. A pair of spring-loaded pins 41 attached to the frame 10 and engaging the housing 12 bias the housing downwardly and laterally into engagement with the four transducers. ing.

As is known in the art of dynamic tire balancing, transducers for sensing lateral movement of a rotating shaft due to wheel imbalance essentially detect the rotation of the shaft about a vertical axis passing through the center of the shaft. To be measured, it must be positioned two intervals apart along the length of the axis.

Timing - encoder 32 and transducer 34
and 36 are mounted on a single printed wiring board 45 which also supports and suitably interconnects all other electronic components for the wheel balancer. These electronic components include appropriate conventional circuitry which relates to their position relative to the inner and outer rims of the wheel and the rotational position of the wheel to which the output signals of the transducers are to be balanced. Correlates information to provide an indication of wheel imbalance and measured wheel imbalance. That information can be displayed on a suitable display 48 mounted on printed wiring board 45. Distribution board 45 includes circuitry for performing unbalance measurements at a non-predetermined rate, which circuitry will be further described with reference to FIGS. 4 and 5. The distribution board 45 can be attached to the frame 10 or to an external cover (not shown) for the balance device 5.

Additionally, the balance shaft 20 holds the crank 42 and
This crank 42 is provided to rotate the shaft 20 and the wheel 25 in order to determine the imbalance of the wheel 25. The crank 42 only drives the wheel in one direction when the wheel is rotating, and disengages from the wheel in the other direction to prevent dangerous rotation of the crank (f'reg-w
It is preferable that the design is as follows. This can be accomplished, for example, by attaching a sleeve 43 attached to the crank 42 to the counterbalance shaft 20 by a wrap spring 44 or any other suitable one-way latte device.

Balancing head assembly 8 is mounted to base 50 as shown in FIGS. 2 and 3. This base 50 is designed to allow head assembly 8 to be moved up and down to align axis 20 with the center of wheel 25 and to align wheel bolts 26 with corresponding bolt holes on wheel 25 for attachment by lug nuts 28. ing.

This is so as to allow precise alignment of the counterbalance head with the wheel lugs etc. when the head assembly 8 is mounted on the shelf 52.
It will not turn off unless it is set by a control that allows relatively fine adjustment, such as plus or minus millimeters. One means for making adjustments is through the use of a threaded shaft 76 driven through a nut plate 78 on the upright post 56 by a pair of crank driven miter gears.

The crank 58 can be equipped with a handle 71. Miter gears 72 and 74 are surrounded by gear cover 60. The bearing and structure by which the shaft holding miter gear 72 is mounted to carriage 54 is common practice and will not be discussed in the text for brevity. As the drive miter gear 72 is rotated, it further rotates the drive gear 74, which in turn rotates the threaded shaft 76, causing it to move up and down by the interaction of the nut plate 78 with the shaft. A stop nut 80 is provided at the end of the shaft 76. Upright post 56 is attached to an essentially "U" shaped cross member 61 made of cross member 61 and arms 62 and 64. This "U'' shaped structure has wheels or rollers 66 and 68, and
These come into play when the balance devices are tilted upwards again and the balance devices can be moved correctly to the wheels. The skid (5
kid) or a rigid wheel 70A as shown in FIG.
are provided on the cross member to facilitate final positioning of the balancing device by means of wheels, while providing a solid base for the balancing device during balancing operations.

Note that the nut plate 78 is simply placed on top of the upright post 56, and the opening in the upright post 56 is large enough to pass the nut in the nut plate 58. Thus, the entire assembly of balancer head 8 with associated teletable 52 and vertical positioning mechanism can be lifted away from upright 56 for transport or storage as desired. This decomposition allows precise,
And the delicate counterbalance head can be separated from the heavy and durable pace.

Note that preferably upright post 56 is not perpendicular to cross member 61 when viewed along axis 20. The angle "A" from the vertical is shown as 10 degrees,
It may be within the range of about 3 degrees to about 20 degrees, especially 5 degrees to 15 degrees. This angle is such that when the wheel is mounted on the axle 20, its weight loads the shelf 52 and shaft 54 against the upright post 56, and the upright post 56 is formed from the cross member 61 and the arms 62 and 64. Apply a screw force that applies a load to the lower structure. This load, which is much larger than the unbalanced force of a balancing beetle, can take up any play or clearance within the vane structure, and can disrupt vibrations and harmonics within the balancing device itself. Minimize.

In operation, the wheels to be balanced are removed from the track or placed in a vertical position.

This balancing device is located close to the wheels.

The operator adjusts the vertical position of the balancer head by rotating crank 58 until the wheel lugs are aligned with the corresponding holes in the wheels. Then the balancing device is wheel lug 2
6 engages the wheel hole and is pushed forward until the wheel nut 28 is applied to retain the wheel. The exact method for attaching the wheels to axle 20 is not central to the implementation of the present invention. Bolt plates and associated bolts may be used in place of wheel bolts 26 and lug nuts 28. Similarly, for wheels with a precisely defined center hole, the wheel may have a center hole or center hole as is known in the art.
Hole cone system (cents day hole-eng)
agttLg cona system). Once the wheel is installed, the crank 5B is then rotated to lift the tire upwards until it is off the ground and the wheel is free to rotate.

The operator determines the distance of the transducer from the inner rim of the wheel to be measured (i.e., the transducer offset);
and information regarding the distance between the inner and outer rims of the wheel and the diameter of the wheel. Typically, this information can be determined economically based on standard wheel sizes, and a mechanism for entering such information,
For example, potentiometer 46 (FIG. 1) can be modified according to standard wheel sizes. Once the appropriate information is in place, the wheel is actuated by grasping the wheel or crank 42 by hand and applying rotational force to it.

Wheels rotate to a speed greater than the required minimum speed (5 pi
n 1Lp ), a signal is given to the operator to indicate that no further rotation force needs to be applied. This speed need not be greater than 180 revolutions per minute, and is preferably substantially less. The counterbalance device measures the unbalanced force and signals the operator that this is over. The wheel is then slowed down, for example by lowering the wheel until the tire is pulling over the ground. Once stopped, the wheels are lifted again and the weights required for balancing and their positions are displayed on the display 48 and weights can be applied to the wheels to balance them.

According to yet another aspect of the invention, the measuring circuit is preferably capable of performing unbalance measurements at any given speed within a relatively wide range of rotational speeds. This type of circuit is particularly useful in dynamic balancing devices of this type, where the rotation is seen by hand at 7 degrees on the wheel and thus the speed can be varied widely depending on the force applied by the operator. I can do it. The change in rotational speed from one measurement to the next is particularly widely used in balancing devices adapted to accommodate various tire sizes, such as those described with respect to FIGS. 2 and 3. There is.

Referring to FIG. 4, in a circuit implementing this principle, the output signals from piezoelectric transducers 34 and 36 are amplified by amplifiers 102 and 104, respectively. The amplified output signals from these amplifiers are passed through a pair of multiplying digital-to-analog converters (AfDACs) l 06 and 10.
8.

In operation, the MDAC multiplies each analog input signal by a coefficient determined by the digital signal and then provides the multiplied signal to microprocessor 110. In microprocessors, analog input signals are converted to digital form by internal converters.

AI D A C is first set (before that time the first measurement is taken) and multiplies the signal by a factor determined according to the value of the wheel speed and also by the wheel diameter. The wheel diameter diameter is fed into the microprocessor by a hand-adjusted potentiometer 112. Wheel speed is measured. This factor is the signal multiplier (s
ignal multiplication) can be determined empirically for different wheel types.

When the input signal is so large that it is outside the operating range of the microprocessor, the MDAC directs the transducer input signal to be reduced, ie, multiplied by a factor less than one. Optionally F), the MDAC also
It can also be used to increase the amplitude of low level signals caused by slow rotational speeds, for example. - Once the vertical input signal is properly adjusted, the microprocessor acts on it in a conventional manner to determine the unbalance condition of the wheels. By limiting the range of operations over which the microprocessor must work, more accurate results are achieved at less cost. For example, an inexpensive microprocessor with a small (e.g., 8-pin) internal A/D converter may have an A/D converter with a large converter for widespread application.
It can be used in place of a D converter.

Comparison of the input signal with the threshold value and appropriate adjustment of its level can be performed approximately in about 3 to 5 revolutions of the wheel. It is therefore possible to perform this operation with each wheel measurement without losing a large amount of time, especially compared to the time it takes to slow down to a constant measurement speed when a large wheel is initially over-rotated. Thus, this rotating wheel balancing device can be effectively used to balance a variety of tires of different sizes, each of which can rotate at different speeds.

More specifically, the output signals from transducers 34 and 36 are passed through amplification stages 102 and 104 and then through appropriate filter stages (filter-4ng 5tat).
e) through b, 2-channel MDAc106/108
provided to. The MDAC multiplies these two input signals separately according to an 8-bit command signal received from the microprocessor 110 via the data bus.
y), and yielding two adjusted output signals. These output signals are preamplified (p
After reamplification and processing, it is provided to the microprocessor.

After the input signals have been adjusted to the correct levels within the microprocessor's operating range, the microprocessor typically uses those signals along with signals from encoder 32 to indicate the angular position of the wheel and its direction of rotation. It is used to determine the unbalanced condition of the wheels according to the algorithm being implemented. These algorithms use appropriate constants and calibration values.
value) is stored in memory rotation 125 addressed by control signals sent from the microprocessor via data bus 120. Once the unbalance is measured, the microprocessor controls the appropriate driver 126 to operate the display unit 128 to provide an indication of the amount of weight that must be applied to balance the wheels. The microprocessor is of various LE
The operation of D130 is controlled to guide the operator to place the weight in the correct position when rotating the wheel.

In addition to these LEDs, the microprocessor may also include a suitable buzzer 132 or other audible or visual indicator to signal when the wheel has reached a sufficient rotational speed to enable measurements to be taken. can operate.

It will be understood by those skilled in the art that this invention may be embodied in other specific forms without departing from its spirit or essential characteristics. Accordingly, the presently disclosed embodiments are considered to be illustrative in all respects and should not be limited thereto. The scope of the invention is indicated by the appended claims rather than by the foregoing description, and all changes that come within the meaning and range of equivalence thereof are intended to be embraced therein.

[Brief explanation of the drawing]

FIG. 1 is a perspective view of a typical shaft and measurement head arrangement for generating electrical signals related to unbalanced forces; FIG. Figure 3 is a perspective view of an adjustable positioning shaft wheel balancer constructed using a balancing head; Figure 3 is a front elevational view of the balancer as shown in Figure 2; 8. Wheel balancer head 10
・・・・・・・・・・・・Frame 12・・・・・・・
...Housing 14.16 ...Metal strip 20 ...Balancing shaft 25 ...
・・・・・・・・・Wheel 30・・・・・・・・・・Timing disc 34
．． 36...Piezo electric transducer 45.
・・・・・・・・・・・・Printed wiring board 4B・・・・
・・・・・・Display device 50・・・・・・・・・・・・
Base 54... Carriage 56...
...... Upright column 72.74 ... Miter gear 76 ...... Cleaning D of threaded shaft flashing surface (no change in content) Procedural amendment (method) March 15E, 1985! Japan Patent Office Manabu Shiga 1. Indication of the case 1985 %rlFm + No. 5992 2. Name of the invention Method and machine for determining wheel imbalance 3.
Relationship with the case of the person making the amendment Patent applicant and one other person4, agent 〒107 Drawings

Claims (1)

[Claims] 1. A method for determining the unbalance of a wheel, comprising: (1) standing the wheel on the ground in a substantially vertical position; (1) vertically aligning a rotatable horizontal shaft with the center of the wheel; positioning said shaft in engagement with a core wheel; mounting said wheel on said rotatable horizontal shaft; and raising said rotatable horizontal shaft until said wheel is off the ground; imparting rotation to said wheel and said shaft to a speed sufficiently large to produce a measurable force of balance; measuring the unbalanced force transmitted by said shaft; and unbalance data regarding the measured force. A method comprising the steps of: determining the unbalanced data; and displaying the unbalanced data. 2. A method according to claim 1, wherein the imparting rotation is carried out manually and the speed achieved is no greater than 180 rpm. 3. The method according to claim 2, wherein the wheel and shaft are allowed to rotate and decelerate by inertia. 4. A method for determining wheel unbalance is to stand a core wheel on the ground in a nearly vertical position; align a rotatable horizontal shaft vertically with the center of the wheel; upon engaging and positioning; upon mounting said wheel on said rotatable horizontal shaft; and upon raising said rotatable horizontal shaft until said wheel is off the ground; allowing measurement of the annular lance conveyed by said shaft; When the wheel and the shaft are rotated to a speed large enough to produce a force of , thereby stopping rotation of the wheel. 5. A rotatable horizontal shaft adapted to support a wheel to be balanced, means for measuring the unbalanced force transmitted by the shaft when the wheel is rotating, and the measured force. and means for determining and displaying the unbalanced force relative to the wheel, said machine comprising: means for determining and displaying the unbalanced force relative to said wheel; means for adjusting the vertical position of the horizontal shaft; and means for raising the horizontal shaft supporting the wheel to a height at which the wheel can be lifted off the ground. A machine characterized by: 6. A wheel imbalance determining machine as claimed in claim 5, wherein said machine is movable horizontally towards said vertically standing wheels. 7. The machine is movable, and the rotatable shaft, the means for measuring unbalance forces, and the means for determining and displaying unbalance data are arranged to horizontally move the machine. 7. A wheel unbalance determining machine as claimed in claim 6 in a balancing head unit which is separably mounted on a movable base. & A wheel imbalance determination machine as claimed in claim 5, wherein said larger means for adjusting the vertical position of said horizontal axis includes a carriage for moving the upright body up and down with respect to said axis. 9. The upright body is parallel to the surface of the vertical wheel and is angled from a vertical plane passing through the horizontal axis, thereby causing the weight of the wheel to self-lock the pace. 9. The wheel unbalance determining machine according to claim 8, wherein the wheel unbalance determining machine is preloaded. 10. The wheel unbalance determination machine of claim 9, wherein said upright body represents said vertically standing wheel. 11. The wheel imbalance determination machine of claim 10, wherein said upright body is at an angle of about 10 degrees from said vertical plane. 12 additionally provided with means for lowering the horizontal shaft supporting the wheel while the wheel is rotating to a level where the rotating wheel contacts the ground and stops rotating; A wheel unbalance determination machine according to claim 5. 13. A balancing head containing a rotatable horizontal shaft, itself adapted to support the wheel to be balanced, and measuring the unbalanced forces transmitted by the shaft when the wheel is rotating. and means for displaying unbalance data regarding the measured force. means provided for adjusting the vertical position of the counterbalancing head to align the center of the wheel in position; and means for raising the wheel to a height that allows the wheel to be lifted off the ground. A machine characterized by comprising: