AU6928481A - Creation of Inventions and Patents with Artificial Intelligence

AU6928481A – Method and apparatus for controlling differentially driven wheel slip
– Google Patents

AU6928481A – Method and apparatus for controlling differentially driven wheel slip
– Google Patents
Method and apparatus for controlling differentially driven wheel slip

Info

Publication number
AU6928481A

AU6928481A
AU69284/81A
AU6928481A
AU6928481A
AU 6928481 A
AU6928481 A
AU 6928481A
AU 69284/81 A
AU69284/81 A
AU 69284/81A
AU 6928481 A
AU6928481 A
AU 6928481A
AU 6928481 A
AU6928481 A
AU 6928481A
Authority
AU
Australia
Prior art keywords
slip
wheels
value
wheel
signal
Prior art date
1980-05-07
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)

Granted

Application number
AU69284/81A
Other versions

AU545575B2
(en

Inventor
Robert G. Miller
Allen D. Myers
Weldon L. Phelps
Alfred W. Sieving
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

Caterpillar Inc

Original Assignee
Caterpillar Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
1980-05-07
Filing date
1980-05-07
Publication date
1981-11-26

1980-05-07
Application filed by Caterpillar Inc
filed
Critical
Caterpillar Inc

1980-05-07
Priority to AU69284/81A
priority
Critical
patent/AU545575B2/en

1981-11-26
Publication of AU6928481A
publication
Critical
patent/AU6928481A/en

1985-07-18
Application granted
granted
Critical

1985-07-18
Publication of AU545575B2
publication
Critical
patent/AU545575B2/en

2000-05-07
Anticipated expiration
legal-status
Critical

Status
Expired
legal-status
Critical
Current

Links

Espacenet

Global Dossier

Discuss

Classifications

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES

B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force

B60T8/17—Using electrical or electronic regulation means to control braking

B60T8/175—Brake regulation specially adapted to prevent excessive wheel spin during vehicle acceleration, e.g. for traction control

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force

B60T8/17—Using electrical or electronic regulation means to control braking

B60T8/176—Brake regulation specially adapted to prevent excessive wheel slip during vehicle deceleration, e.g. ABS

B60T8/1761—Brake regulation specially adapted to prevent excessive wheel slip during vehicle deceleration, e.g. ABS responsive to wheel or brake dynamics, e.g. wheel slip, wheel acceleration or rate of change of brake fluid pressure

B60T8/17616—Microprocessor-based systems

B—PERFORMING OPERATIONS; TRANSPORTING

B60—VEHICLES IN GENERAL

B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force

B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration

B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition

B60T8/48—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems

B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems

Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC

Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS

Y10S303/00—Fluid-pressure and analogous brake systems

Y10S303/06—Axle differential control

Description

Description
METHOD AND APPARATUS FOR CONTROLLING DIFFERENTIALLY DRIVEN WHEEL SLIP
Technical Field
This invention relates to vehicle drive sys- terns of the type having spaced apart drive wheels which are driven through a differential from a common power source and, more particularly, to a method and apparatus for controlling slip between the differentially driven wheels due to a loss of traction at one wheel by dis- crete proportional applications of braking force to the wheel with the lesser traction.
Background Art
It is well known that the standard vehicle having spaced apart drive wheels or wheel-sets which are powered by a single engine through a differential drive experiences difficulties when one of the two dif¬ ferentially driven wheels loses traction. Conditions which give rise to a loss of traction exist commonly in construction sites and other off-road locations as well as on normal roads during wet, snowy or icy weather.
A truck or automobile having one of two differentially driven wheel-sets on ice and the other on ground pro¬ viding good traction is often unable to move due to the fact that the action of the differential drive system directs all power to the wheel having no traction. The result is a slip condition wherein the wheel without traction rotates at twice its normal speed relative to the drive shaft and the wheel with traction remains stationary. To alleviate the slip or loss of traction condition, various mechanical anti-spin devices have been developed and put into commercial use. Such

devices, however, can- produce an abrupt transfer of all driving power to the wheel’ or wheel set having traction. This abrupt and full power transfer’ can create such mechanical .stresses as, to shorten the useful life of the drive train and/or. cause catastrophic failure. In addition, mechanical’ anti-spin units often fail to ac¬ commodate the wheel speed differential which arises during normal turning of the vehicle and hence give rise to excessive, tire wear due to drag effect. An alternative approach to the slip problem due to loss of traction in differentially driven vehicles involves the provision of separately actuable drive wheel brakes whereby the operator can selectively apply a brak¬ ing force to the spinning or slipping wheel thus to effec a balancing of power as between the slipping and nonslipping wheels; i.e., the application of the braking force to the slipping wheel simulates increased rolling resistance and results in a more even distribution of power as between the two differentially driven wheels. Systems of this type are common on farm vehicles but are not believed to be practical on large transport or off- road vehicles such as trucks and road graders.
More sophisticated approaches to slip control using the selectively actuable wheel brake systems are known in the prior art. These systems include a speed sensor disposed on or adjacent each of the differentially driven wheels for generating speed signals, means for comparing the two signals to develop a slip signal and selectively operated solenoid means or solenoid operated valves to actuate either the left or right wheel brake when a slip condition is detected. One such system is disclosed in the U.S. patent to Devlin, number 4,066,300 issued January 3, 1978. Anothersuch system is disclosed in the U.S. patent to Eger, Jr. et al, number 3,025,772 issued March 20, 1962. Both the Devlin and Eger, Jr. et al systems involve abrupt application and release of

brake forces to the slipping wheel. This approach, un¬ less utilized with very light braking forces, and at low speeds, can be detrimental to operator control of the vehicle unless the operator is given an opportunity to participate in the overall actuation of the slip control system.
The present invention is directed to over¬ coming the problems of the prior art and to provide an improved vehicle slip control system,
Disclosure of the Invention
In one aspect of the invention an apparatus is provided for automatically balancing the power trans¬ fer between two differentially driven vehicle wheels when one of the wheels loses traction,by applying a proportionally varying braking force to the wheel which loses traction,during a slip control time period. This system comprises means for applying braking forces to the wheels on a selective and individual basis, means for generating a slip signal corresponding to any difference between the rotational speeds of the wheels, and means for actuating the braking means on the faster rotating wheel in a manner which is modulated proportionally to the degree of slip represented by the slip signal; i.e., the difference in rotational speeds. In another aspect of the invention, a method is provided for achieving improved operation of an anti- slip system of the type which applies a braking force to the wheel or wheel set which loses traction, thus to balance the power transfer between two differentially driven vehicle wheels. This method comprises a series of steps which can be carried out by apparatus also

disclosed herein, the steps including the development of a slip signal, the application of a braking force to the wheel which has lost traction, and the further new and improved steps of defining a plurality of slip signal value bands, periodically redetermining the relationship between the slip signal value and each of said bands and incrementally varying the braking force, i.e., either increasing or decreasing, in accordance with an incremental variation- alue which corresponds to the band within which the slip signal value falls at any given time.’
Brief Description o Drawings
Fig, 1 is a schematic diagram of a vehicle drive system embodying an anti-slip control system in accordance with the invention;
Fig. 2 is a block diagram of a wheel slip control system in accordance with the invention and comprising a micro processor to perform mathematical calculations and comparisons; Fig. 3 is a more detailed block diagram of a portion of the overall system of Fig. 2;
Fig. 4 is a,n operational.” flow chart from which programming for the micro processor in the embodi¬ ment of Fig. 2 may be readily developed, and Fig. 5 is a chart of brake hold off pressure versus time and is. utilized in describing the operation of the embodiment of Fig. 2.
Best Mode for Carrying Out the Tnvention Fig. 1 illustrates an embodiment of the invention as applied to the detection and control of slip due to loss of traction in a vehicle having road wheels 200 and 202 driven by a single engine (not shown) through a drive shaft 204, a differential unit 206 and half-axles 208 and 210 respectively. The drive system
OMPI

is per se conventional and no details need be given.
Wheels 200,- 202 are stopped by spring engaged emergency/parking brake pistons or hydraulically engaged service brake pistons of brakes 212, 214. The brakes are spring biased so that when no hydraulic pressure is present, the emergenc /parking brakes engage and stop the wheels. During operation of the vehicle the brakes are maintained in the disengaged position by luid pressure as disclosed in U.S. Patent 3,927,737 issued December 23, 1975 to P. F. M. Prillinger and assigned to the assignee of this invention. The brakes are normally actuated via a service brake line 237 coming from the rear wheel service brake and retarder master cylinders (not shown) . The service braking system, per se, is well known and does not form part of this inven¬ tion. The brakes are also actuated through the parking/ emergency brake lines 236, 238 as described in detail below.
The slip control system comprises’ a left wheel speed pickup in the form of an electromagnetic trans¬ ducer 216 which operates to provide pulses in coopera¬ tion with a gear-like device 218 which is mounted in the axle housing to be rotationally driven by axle 208. Signals from pickup 216 are applied to one input of an electronic control system 220, the details of which are hereinafter described. The right wheel speed signals provided by means of a pickup 222 operate in conjunction with a gear-like device 224 which rotates with the axle 210. The right wheel speed signal is applied to another input of electronic control 220. Finally, a drive shaft speed signal is generated by pickup 226 and gear-like device 228 which rotates with the drive shaft 204. The drive shaft speed signals are applied to a third input of electronic control 220. Control 220 operates upon the three signal inputs to determine the existence, magnitude and loca-
-vs C. ■ iz. A (j ~ T’T”

tion of wheel slip during a loss of traction situation. The power transfer between the two differentially driven vehicle wheels 200 and 202 is balanced by applying a proportional braking force to the wheel which loses traction. This is accomplished by means of location selection valve 230 and proportioning valve 232, both of which are connected to receive output signals from- the control 220. The valves 230 and 232 operate in combination with a supply 234 of oil under pressure, the fluid lines from supply 234 running both through the proportioning valve 232 and around the proportion¬ ing valve to the 4-way solenoid operated valve 230 which directs full pressure to one of the parking . brakes 212,214, and modulated or proportionally con- trolled fluid pressure to the other. In this instance brake pressure is applied by relieving fluid pressure in one or the other of the two brake lines 236 and 238. This is a consequence of the selection of spring biased brakes 212,214 and could be straightforwardly implemented in the reverse fashion, i.e. brake pressure might be increased in direct rather than inverse ratio to the applied fluid pressure.
Fig. 2 illustrates the preferred implementa¬ tion of the electronic control 220 of Fig. 1, In this implementation a solid state micro processor 242 of the type available from such sources as Motorola and Fair- child is utilized to perform system control functions; most notably, to establish a plurality of slip value bands, each band having defined slip signal values and each band having associated therewith a rate at which brake force in terms of fluid pressure is applied or removed. The micro processor is readily programmed to respond to signals from the left, right and drive shaft pickups 216, 222 and 226, respectively, to generate a slip signal and to compare the slip signal to the limits of each of the bands, thereby to determine the partic-
OfΛP W

ular band within which the slip signal resides at any given time. To this end micro processor chip 242 is operatively interconnected with a band value memory 244 and a timer 246 which establishes a timing cycle hereinafter described. Pickups 216, 222 and 226 are connected through an input protection and filter circuit 240 which provides appropriately digitized input signals to the micro processor chip 242. A retard brake pressure switch 248 and a service brake pressure switch 250 are connected through input protection and filter circuit 252 to the micro processor 242 for resetting the anti-spin control to OFF when the service brakes or retarder are actuated, much the same as an automobile cruise control is reset OFF when the service brakes are applied. This feature gives the vehicle operator uncontested control of the braking function when he is using the service brakes.
Completing the description of the block diagram of the system as shown in Fig. 2, micro processor 242 has three illustrated outputs, the first output going through a pulse width modulated servo valve driver 254 to the servo operated proportioning valve 232. The second output goes to the solenoid driver 233 associated with the left direction shuttle valve 230a and the third output goes through solenoid driver 235 to the right direction shuttle valve 230b. It will be appreciated that the outputs to the solenoids 230a and 230b are represented in Fig. 2 as a single line for purposes of simplicity. Fig. 3 illustrates a preferred implementation of the pulse width modulated servo valve driver 254 in greater detail. The pulse width modulation servo valve driver 254 comprises a duty cycle generator 256 in the form of a digital to pulse width converter, such as Motorola integrated circuit number 6840. An oscillator 258 is connected to the duty cycle generator 256 to pro-

vide a base frequency. . The output of the duty cycle generator is a width modulated pulse train at a fre¬ quency of 100 Hz and this signal is applied’ oan ampli¬ fier 260 which increases the power of the signal. The 5 signal is applied:to a proportioning valve 262, such as the proportional controller model number 82 which is available from the Fema Corporation of Portage, Michigan. The proportional controller is in turn connected to the control. valve 232 in. a manner well known to those skil-
10 led in the art to vent the pressure from supply 234 and the’reby modulate the brake fluid pressure in whichever of the lines 236 and 238 is selected by valve 230. Referring now to FIGURE 4, a flow chart defining the internal programming for the micro proces-
15 sor 242 and associated memory 244 is shown. From this flow chart a programmer of ordinary skill can develop a specific set of instructions for a general purpose micro, processor so as to define the necessary slip signal value bands, timing cycles, and brake fluid
20. pressure values which are essential to the full imple¬ mentation of the invention as hereinafter described. It will be appreciated that while the best mode of the invention comprises the properly programmed micro processor, the programming of which is disclosed in
25 Fig. 4 and the result of which is the creation of novel hardward associations within the micro processor and its associated devices, it is possible to implement the invention utilizing more traditional hardwired circuits. For example, slip signal values may be generated by
30 means of tachometer generators and voltage comparators and the result applied to a series of biased comparator amplifiers representing a series of contiguous slip valve” bands. The outputs of the amplifiers may be summed through conventional logic and applied to a
35 stepper motor, ladder network or other summing device operatively interconnected with the proportioning valve.
C\:?

Industrial Applicability
Referring now tσ Figures 1, 4 and 5, an example of industrial, applicability will be described with reference to the’ operation of a vehicle having 5 differentially driven .wheels 200 and 202,. a drive shaft 204 and a differential unit 206 through which the wheels 200 “and 202 receive power from a single engine. It is further assumed that the vehicle on which the wheels 200 and 202 are mounted has a turning capability which,
10. when employed to full effect, results in a maximum wheel speed differential of 1.5.
By way of preliminary summary, the operation of the embodiment of Figures 1. and 2, when programmed in accordance with the flow chart of Fig. 4, involves
15 the definition and storage of five speed differential or slip bands and the further definition of braking forces, expressed in brake fluid pressure increments, associated with a speed differential value for each band. In addition, a relatively high slip value •
20 threshold is set for entering into the slip control mode while a relatively low slip threshold value is estab¬ lished for exiting from the slip control mode. Two final factors play important roles in the operation of the system: first, a timing period is established where-
25 by the slip value is periodically redetermined and, to the extent it remains within a given band, a brake pres¬ sure increment, either positive or negative, is ef¬ fected at the end of each clock time until the slip value moves to another band; secondly, an indication of
30 slip is always cross-checked by comparing the speed of the spinning wheel to the speed of. the drive shaft 204 so that the functional failure of one wheel speed pick¬ up is not misinterpreted as a slip condition. This latter function is dependent upon the phenomenon of the
35 differential drive wherein a 100% slip condition results in a ratio of slipping wheel speed to drive shaft speed which is double the ratio existing under no-slip.

straight- head conditions.. Assuming a 1:1 rear axle ratio, one can simplify this: expression by saying that the 100% slipping wheel speed is twice that of the drive shaft. Having briefly summarized the functional characteristics of the properly programmed system a full description of operation will now be given.
Flow cha t block 264 (Fig. 4) represents the sampling of data from .the left and right speed signal pickups 216 and 222; it will be appreciated that such data is ‘placed in given address locations by the micro processor so that it is available for later retrieval and processing for calculation purposes. As a first condition it is assumed that one of the axle speed signals is equal to zero. If this is the case the routine progresses along the right side of the flow diagram in Figure 4. Block 266 represents input of the drive shaft speed signal from pickup 226, it be¬ ing understood that this signal is also placed in a predetermined storage location by- the micro processor. The input or drive shaft speed signal is compared in block 268 with the non-zero wheel speed signal and if the ratio of the wheel speed to drive shaft speed is equal to or less than 1.5 it is assumed that the wheel showing zero speed is actually turning and the zero indication is the result of a. pickup failure. The program then calls for a return to the original input point; in addition it may be desirable to set an output signal condition which alerts the operator to the apparent transducer failure.
If the rotating wheel speed is greater than 1.5 times the drive shaft speed, as indicated by comparison steps .268, the program progresses to the evaluative step represented by flow chart bloc3s 270a, 270b and 270c. If the condition represented by block 270a is satisfied the program progresses to block 272a
0”

which is an event counter requiring several successive cycles of positive signal conditions before the “brake latch” condition, i.e.. the activation of the slip con¬ trol ■ system is begun. It has been found that such a delay is advisable from the standpoint of efficient system operation so as to filter out short term aber- ations in wheel speed condition. If the event counter has not reached the delay time α the program progresses to block 274a which involves incrementing the counter. From this point the program returns to the original input condition.
«
If the condition represented by program block 270b is satisfied the program progresses to blocks 272b and 274b in the manner previously described. If either block 272a or 272b produces a positive signal condition the program progresses to block 276 which involves a determination of the input signal switch conditions controlling the service brake, the retarder and/or the vehicle speed. In addition, it may be advisable to check brake pressure.
If the speed signal condition represented by block 270c is satisfied the program advances to blocks 278, .280, 282 and 284 to release the parking brakes 212 and 214 and reset the timer. The same result occurs if the output of program block 276 is positive.
If the output of program block 276 is negative the program progresses to block 286 to determine whether the slipcontrol■ system is activated. If the result is positive the effect is the same as entering band 5, i.e. the most severe slip condition band and progressing to block 294 which increases the wheel brake force by decreasing the wheel brake hold-off pressure by the pressure increment X for every timed interval estab¬ lished by the micro processor timer. If program block 286 indicates that the slip control system is not operative the program progresses to block 288 which
-jjυRtΛTT

activates the system and thence through blocks 290 and 292 to begin the timing cycle and reduce the brake hold off pressure to a value just sufficient to maintain the brakes in the off position. On the next pass through the above sequence, a positive result will be obtained at block 286 and in block 294 brake hold off pressure will be decremented X psi. The control will continue to repeat this sequence at timed intervals until either the zero speed wheel starts to turn or else the brake hold off pressure is decremented to nearly zero psi
(<10 psi). In the latter case, brakes are then re¬ leased completely. former control follows path from block 264 to,block 296 and beyond as described in following paragraphs'. Assuming result of calculation indicates that neither" wheel 200 nor 202 is stopped; i.e. vehicle moving, program branches to representing a subroutine. essence, subroutine involves deter- mining location actual slip value within each five bands represented by small table shown on upper left side Fig. 4. Note contiguous, limit one band abuts lower next highest which required for activation 1.7. Program blocks 298, 300 302 represent determinations faster rotating proper disposition shuttle valve 230 so direct modulated brake pressure speed unmodulated wheel. The advances 304 determine whether or not sufficient time period has elapsed begin operation system. If insufficient 306 simply increments counter begins process over again. bloc 308 scans various signal conditions might disqualify Operation If, however, 5 qualifies selected 310, .312, 314, 316 318. condition first - mined 'time α elapsed, can only enter slip, mode via 5; ratio 0 high rate low must be 1.7 greater. However, hereinafter described, the.vehicle preferably exits sequencing through 4 -through 1 produce smooth transition back un- 15 controlled mode. Assuming enters 318 positive indication reached 286 force periodically incremented upwardly reducing the 20. hold off indicated 294 increment X (psi) every timing cycle until entry into another band. This where step 400 psi repre- 25 sents an abrupt drop three additional incremental drops approximately 33 in¬ crease parking spring action with increment. After large the 30 example 4; i.e., been reduced point less than greater equal 1.5. this 320 35 322 cause increased smaller Y cycle. Accordingly, system approaches full gradual curve become toward condition. As also 5, reaching values' qualify successive 3, ,2 1, causes gradually increasing reductions uncontrolled psi. To end 3 mirror image band' incre¬ mental, increases pressure; 2 band.5 causing larger (X) cremental force. Band no counterpart still reduc¬ tions W diagram 5. From foregoing it apparent operates detect apply braking slipping incrementally modulate either positively negatively accordance degree detected use drive shaft provides failsafe wherein false zero transducers immediately recognized appropriately disabled. Vehicle turning giving rise 1.5 but both wheels turning, do modes since necessary satisfied. On other hand, once entered new threshold established such will normally exit satisfying requirements 1.1. It appreciated those skilled art essential incorporate all steps .the flow chart given system, utilize micro processor. implementation deemed best implementing invention due broad widespread commercial availability suitable processor circuits, >Download PDF in English

None

Contact information