EP0503972A2

EP0503972A2 - Elevator rail profile estimation and elevator control method

Info

Publication number: EP0503972A2
Application number: EP92302211A
Authority: EP
Inventors: Randall K. Roberts
Original assignee: Otis Elevator Co
Current assignee: Otis Elevator Co
Priority date: 1991-03-13
Filing date: 1992-03-13
Publication date: 1992-09-16
Anticipated expiration: 2012-03-13
Also published as: EP0503972B1; DE69211040T2; EP0503972A3; HK206296A; DE69211040D1

Abstract

An elevator hoistway rail profile is made during an elevator car learning run by summing (32) a doubly integrated (36) car horizontal acceleration signal with a relative rail-car displacement signal (Xb) and storing the summed signal (XR) according to the vertical position (Y) of the car in the hoistway. Elevator car horizontal vibrations are actively controlled by retrieving data stored in memory indicative of the out-of-straightness of the guide rails.

Description

This invention relates to elevators and, more particularly, to ride quality.
Maintaining or improving the ride quality of elevators will require implementation of new technologies, especially as the elevator speeds are increased. Reducing lateral motion of the car platform is important for improving ride quality. Such motion can be caused by rail-induced forces which are transmitted to the car through the rail guides due to rail irregularities.
If one were to design an automatic control system for reducing such lateral motion one could choose an open loop system.
At least one attempt to address rail-induced forces using an open loop control is known from the prior art. In U.S. Patent No. 4,750,590, in order to compensate for lateral oscillation of an elevator car, Matti Otala discloses what appears to be an open-loop elevator control system with solenoid actuated guide shoes. The disclosure purports to show how to use the concept of first ascertaining the out-of-straightness of the guide rails for storage in a computer memory and subsequently controlling the guide shoes by recalling the corresponding information from memory and correcting the guide rail shoe positions accordingly.
However, the method shown in Otala's disclosure, of merely attaching acceleration meters to the elevator car, would not, as suggested by his disclosure, provide sufficient information to create a "deviation table" for a compensation system. It would merely create an acceleration table. How a "deviation table" is made from acceleration meters is not shown or suggested.
There are two principal disturbances which contribute to the levels of vibration in the car: (1) rail-induced forces which are transmitted to the car through the rail guides due to rail irregularities, and (2) direct-car forces such as produced by wind buffeting, passenger load, distribution or motion.
The various parameters of the elevator car's suspension system are so affected by unrepeatable direct-car forces that the underlying acceleration measurements, without more, would not be meaningful. In other words, the underlying accelerations are a nonlinear function of the car load, its distribution, the movement of passengers, and a myriad of other direct car forces. Something more is needed to interpret the sensed acceleration signals in a meaningful context in order to be enabled to compile a displacement table that truly reflects the rail profile.
On the other hand, the teachings herein show why it is necessary, and how to actually quantify the cause of the first system disturbance, i.e., elevator guide rail irregularities.
According to one aspect of the present invention, there is provided
a method for measuring horizontal deviations from vertical of an elevator car rail, comprising the step of relating a vertical position signal to a sensed car horizontal acceleration signal and a sensed signal indicative of the horizontal displacement of the car from the rail.
According to another aspect of the present invention, there is provided
a method for estimating an elevator hoistway rail profile, comprising the steps of:
summing a relative horizontal displacement signal indicative of an elevator car's relative position with respect to said rail and a doubly integrated acceleration signal indicative of said car's horizontal displacement from a vertical inertial referent and providing a summed signal; and
storing said summed signal according to the magnitude of a vertical position signal indicative of said car's vertical position in said hoistway.
According to a further aspect there is provided apparatus for estimating an elevator hoistway rail profile, comprising:
means responsive to a sensed acceleration signal having a magnitude indicative of horizontal acceleration of an elevator car, for doubly integrating said acceleration signal for providing an integrated signal having a magnitude indicative of horizontal displacement of said car from an inertial reference frame;
means for providing a relative displacement signal having a magnitude indicative of relative horizontal displacement between an elevator car and an elevator rail; and
signal processing means responsive to a vertical position signal having a magnitude indicative of said car's position in said hoistway and responsive to said displacement signals for storing horizontal position information derived from said displacement signals according to the magnitude of said vertical position signal.
The invention further provides a method of controlling rail-induced horizontal vibrations of an elevator car, comprising, on a learning run of the car, sensing car horizontal acceleration and providing a doubly integrated displacement signal indicative of the car's horizontal displacement from a vertical inertial referent, sensing the relative position of the car with respect to the rail and providing a horizontal displacement signal indicative thereof, and storing position information derived from said displacement signals in accordance with the vertical position of the elevator car; and on a subsequent controlled run of the car controlling an actuator in accordance with said stored position information.
Thus, according to the present invention, a signal indicative of an elevator car's horizontal displacement from a vertical inertial referent while the car is in vertical motion is compared to a signal indicative of the displacement between the car and rail and the resultant signal is related to another signal indicative of the vertical position of the car. The comparing and relating steps may be carried out as a number of samples throughout the vertical hoistway span in order to establish a rail profile which may be electronically stored in a lookup table or might even conceivably be done more or less continuously in an analog implementation.
The signal indicative of the car's horizontal displacement may be a doubly integrated acceleration signal from an accelerometer. Its sensing axis may be perpendicular to vertical and parallel to the side-to-side or front-to-back directions. The difference between such a signal and a signal indicative of the displacement between the car and rail is an actual indication of the rail profile, i.e., its bumpiness or "deviations" from vertical.
Thus, in light of the insights provided by the present invention, it will now be understood by those skilled in the art that a mere acceleration reading only gives one piece of information that is referenced to an inertial reference frame or a conceptual plumb line. Since the guide moves with respect to a referent such as the car, such needs to be measured. In the case of a wheel, since its movement with respect to the rail may be assumed to be fixed (e.g., a relatively stiff or even, for our purposes, incompressible wheel) or known (e.g., a sliding guide with actual sliding contact with the rail or an electromagnet actuator with a sensed electromagnetic gap), its movements with respect to the cab need to be known in order to be relatable to the same plumb line or inertial referent. This information is needed to create an actual rail profile with real rail displacement information.
The guide rail profile estimation invention disclosed in this patent is unique in that it provides a way for generating rail profiles with instrumentation that can be located only in or on the car, eliminating the need for plumb-lines or expensive optical equipment. The measurement instrumentation may consist of, e.g., three single axis accelerometers, four relative displacement transducers, and a vertical position measurement of the car in the hoistway. These signals are provided and may be stored in computer memory during a full vertical span run of the elevator car. A series of rail estimation steps may then be executed to process the data to synthesize rail profiles in the form of rail displacements (from plumb-line) as a function of the vertical position. This system permits rapid characterization of hoistway rail irregularities. Or the whole process could be done "on-the-fly", i.e. the profile calculated during the vertical span run of the elevator car.
It would also be possible to store the relative displacement signal and double integrated acceleration signal for each vertical position, and to retrieve them and combine them later in a controlled run of the elevator.
In order to be in a position to ameliorate rail-induced disturbances, whether by an automatic compensation system, by manual means, or in order to be in a position to merely evaluate rails at a particular site, the disclosed "rail profile estimation"approach can actually be used to generate a profile of guide rails, that is, a graph, database, lookup table or the like, of rail displacement versus elevator vertical position. Whether used as part of an active suspension system to minimize car motion during elevator operation or for purposes of rail installation, re-alignment, etc., the disclosed rail profile estimation methods may be used on new elevators or may be used at existing installations. This disclosure shows an embodiment utilizing a wheel guide as the hardware used in part of the information gathering process but other types of guides, such as shown by Otala or in our European application 0467673, may be used as well.
The disclosed method provides a rail profile that may be used in an active system to reduce lateral car vibration levels by up to approximately 90%. Such compensation may be employed on new equipment or retrofitted to existing installations. The disclosed method has been validated as being highly robust and repeatable across a wide spectrum of speeds, directions, suspension stiffnesses, suspension preloads and car payloads.
These and other objects, features and advantages of the present invention will become more apparent in light of the following detailed description of a preferred embodiment thereof, given by way of example only, with reference to the accompanying drawings in which:

Fig. 1 illustrates a central teaching of the present invention;
Fig. 2 shows a method of relating a sensed car acceleration signal to sensed horizontal and vertical displacement signals;
Fig. 3 shows a prior art roller guide;
Fig. 4 shows the rollers of Fig. 3 from above as they would typically be situated on a rail;
Fig. 5 shows the roller guide of Fig. 3 instrumented for measuring front-to-back displacement of the car from a rail;
Fig. 6 shows the roller guide of Fig. 3 instrumented for measuring side-to-side displacement of the car from a rail;
Fig. 7 is an illustration of rail estimation hardware, according to the present invention;
Fig. 8 illustrates steps suitable for execution on a digital signal processor, such as is shown in Fig. 7, for estimating a rail profile along a single axis, according to the present invention;
Fig. 9 is similar to Fig. 2 except more detailed;
Figs. 10(a), 11(a) & 12(a) show car acceleration vs. vertical position for a car load of 228 kilograms located, respectively, at the cab floor center, 94 centimeters to the left of center and 94 centimeters to the right of center;
Figs. 10(b), 11(b) & 12(b) show a horizontal car position with respect to the rail vs. car vertical position for a car load of 228 kilograms located, respectively, at the cab floor center, 94 centimeters to the left of center and 94 centimeters to the right of center;
Figs. 10(c), 11(c) & 12(c) show estimated-car deviation from true vertical, being doubly integrated and filtered versions of the acceleration plots of Figs. 10(a), 11(a) & 12(a), respectively; and
Figs. 10(d), 11(d) & 12(d) show estimated rail profiles vs. car vertical position which may be obtained by summing the signals of Figs. 10(b), 11(b) & 12(b) with those of Figs. 10(c), 11(c) & 12(c), respectively ;
Fig. 13 shows in (a) a top view of a roller guide, such as that shown in Fig. 3, modified to be used in an open-loop active suspension system, (b) a side view of a roller guide of (a), and (c) shows a back view of the guide of (a);
Fig. 14 shows another way to connect the front to back rollers;
Fig. 15 shows an open-loop active suspension system, according to the present invention; and
Fig. 16 shows a series of steps which may be carried out on the signal processor of Fig. 15 providing a smooth ride for the elevator car, as it moves up and down the hoistway.

Fig. 1 illustrates a central teaching of the present rail estimation invention as carried out on an elevator using conventional wheel guides. It should be understood, however, that the teachings hereof are applicable to other types of guides as well and are not restricted to merely roller-guide types of installations. An elevator car 10 for travelling up and down vertically as indicated by a vertical distance y in a hoistway is shown having a wheel guide 12 with a wheel 14 for riding on a rail 16 attached to a hoistway wall 11 and a spring 18 attached at one end to the wheel and the other to the car. Although this teaching is illustrated for side to side horizontal translations, it will be realized that the same basic principle is applicable to front to back translations as well.
With the car at rest, a horizontal distance x_a between a vertical reference line 20, e.g., a vertical inertial reference or "plumb line" down the center of the hoistway, and a vertical centerline 22 of the car can be defined to zero. However, assuming the opposite rail is completely smooth, during vertical motion of the car, due to direct and rail induced forces, the car will experience various horizontal translations which will cause the distance x_a to be nonzero. The magnitude of x_a may be measured, e.g., using an accelerometer 24 and doubly integrating its output signal (a).
The horizontal translations will cause a distance x_b between the wheel and the car to change and the magnitude of x_b may be measured using a position sensor 26. It may be assumed that the wheel is relatively incompressible and has sufficient preload to prevent loss of contact with the rail durnig elevator operation. Thus, the summation of x_a and x_b will represent the deviation of the rail's surface from the reference line 20: $x_{r} {= x}_{a} {+ x}_{b} {+ r}_{w},$

where,
x_r = rail displacement,
x_a = car displacement,
x_b = relative wheel to car displacement, and
r_w = effective wheel radius (constant).
In this way, an actual rail deviation table may be compiled. The table will be indicative of rail displacement from a true vertical reference line.
Fig. 2 illustrates a way to make such a rail deviation table. A horizontal position signal on a line 30 from a position sensor such as sensor 26 is summed in a summing junction 32 with another position signal on a line 34 from a signal conditioner 36 which double integrates an acceleration signal on a line 38 from an accelerometer such as the accelerometer 24. A vertical position signal on a line 40 indicative of the car's vertical position in the hoistway is provided, along with the summation signal from the summing junction 32 on a line 42, to be paired therewith to form a table of positional data indicative of the magnitude of horizontal rail deviation from true vertical along the hoistway. An analog representation of such a table is shown in a box 44 by way of a graph on a Cartesian coordinate system although it should be realized that the table will typically be stored by way of samples in a digital memory for access by a digital signal processor.
A car may be instrumented to measure the side to side displacement x_b depending on the type of guide. For an example of a typical guide, Fig. 3 shows a ten inch (25.4 cm) Otis roller guide 48 which may be found installed on numerous high speed elevators throughout the world. The guide is fixedly mounted on a car and front and back rollers 50, 52 roll on opposite faces 54, 56, respectively, of the hoistway rail 16, as shown in Figs. 1 & 4 adjacent the car. The side to side roller 14 rolls on a distal face 58 of the rail.
The front to back roller 50 has its axle fixedly attached at a point 60 to an arm 62 which rotates about a point 64. An adjustable spring 66 preloads the roller 50 to exert a selected force against rail face 54. Rollers 52 and 14 are set up similarly to roll on faces 56, 58, respectively. A side-to-side dashpot 70 is shown connected between an arm 72 and a bracket 74. The original design of the roller guide as shown in Fig. 3 made similar provision for front-to-back dashpot for the arm 62 and an arm 76 but the dashpots, at least for some cases, were apparently later found to be unnecessary. Consequently, at least some later versions were manufactured without openings and holes for such dashpots as well as without the openings 70, 80 and the holes 82, 84. For more details see US patent 3,099,334 of 30 July 1963.
It will be realized that the particular guide shown is not the only type of guide which may be instrumented to measure the relative displacement between the car and rail. Other types of rails such as sliding guides, electromagnet guides and many other types of guides are certainly within the scope of the invention. It is only necessary to instrument the selected type of guide in such a way as to measure the relative displacement between the car and rail.
Fig. 5 shows a sectional view of the wheel guide of Fig. 3 from the rear. The underside of arm 76 (without a through hole 84 or slot 80) is machined down to a planar surface 90 for sliding contact with a plunger 92 of a displacement transducer 94 mounted on a bracket 96 affixed to the body of the guide. If a line 98 in the plane 90 were extended as shown it would intersect a pivot point 100 for wheel 52 similar to pivot point 64 already described with respect to wheel 50. By setting up this geometry, one can readily linearize any test readings obtained to relate actual wheel displacement to measured rocker arm movement. For example, a shim of a certain thickness inserted between the wheel 52 and the rail face 56, temporarily disconnecting spring 60, might result in a displacement of the plunger 92 by a measurable factor of that thickness, for example, approximately twice. Any inaccuracy introduced by the sliding action of the tip of the plunger 92 against the surface 90 may be neglected. A signal on a line 102 from the sensor 92, 94 is provided.
Fig. 6 is a side sectional view as shown in Fig. 5 from the left of the guide of Fig 3, instrumented for measuring side-to-side displacement of the car relative to the rail. A displacement sensor 104 is mounted in a way similar to that described above for sensor 92, 94 on a bracket 106 attached to the guide body for providing a signal on a line 108 indicative of the displacement of the car from the rail surface 58.
It will be observed that the instrumentation of Fig. 5 provides for measuring the front to back displacement only of the deviation of rail surface 56 and not that of its opposite 54. This assumes uniform thickness of the rail which is an acceptable assumption.
Fig. 7 is an illustration of rail estimation hardware which may be used for carrying out the rail estimation method, according to the present invention. Although the embodiment shown is for gathering a plurality of rail profiles, it should be realized that, in essence, the invention applies to rail estimation in a single axis as shown in Fig. 1, which may of course be practised, as shown in Fig. 7, in several axes at the same time. The hardware shown in Fig. 7 includes a signal processor 109 which is provided in order to carry out four basic steps as illustrated in Fig. 8:

(1) Acceleration Sensing. This may be accomplished, as indicated in a step 109a, by using one or more accelerometers depending on the number of profiles to be gathered, for example, three accelerometers 110, 112, 114, located, e.g., at either the top (shown) or bottom of an elevator car frame 116 oriented to measure, respectively, left front-to-back (l-f-b) acceleration as indicated by a signal on a line 117a, side-to-side (s-s) acceleration as indicated by a signal on a line 117b and right front-to-back (r-f-b) acceleration as indicated by a signal on a line 117c;
(2) Sensing car Position With Respect To Rail. Using, for example, one or more relative position sensors, as indicated in a step 118a, in this case four sensors 92, 94; 104 (as shown previously in Figs. 5 & 6; not shown explicitly in Fig. 7 because the rocker arms, e.g., 62, 76 obscure them in the plan view shown) on the roller guide on the right of the Figure and two others (also not shown) for the left guide, used as relative displacement transducers (e.g., LVDTs (linear variable differential transformers), linear potentiometers, gap sensors or the like), for both s-s and f-b displacement measurement at each guide and providing a left side-to-side displacement signal on a line 118, a left front-to-back displacement signal on a line 120, the right side-to-side displacement signal on the line 108, and the right front-to-back displacement signal on the line 102;
(3) Obtaining Vertical Position of Car. An indication or measure of the vertical car position is required, such as by means of our Primary Position Transducer (see U.S. Patent 4,384,275 to Masel et al) or some other manufacturer's vertical position indicating or measured position signal on a line 121 (Fig.7), as indicated in a step 122, and
(4) Relating Sensed Acceleration to Sensed Car Position with respect to the Rail To Obtain Rail Displacement from Vertical. As indicated by a step 124, the signal processor 109, data collection computer or the like is used to record the concurrent acceleration, car horizontal position with respect to the rail and car vertical position signals and to process data in such signals using the rail estimation methods disclosed above or in more detail below.

As indicated in a step 126, a decision is made as to whether the car has as yet traversed the full length of the hoistway. If not, the steps 109a, 118a, 122, 124, 126 are executed again until such time as the rail profile has been obtained.
With regard to the number and positioning of accelerometers, it should be understood that the number and positioning shown is a matter of choice since the acceleration of any point on a plane in the car may theoretically be inferred from merely three accelerometers in that plane. Three accelerometers are shown, one in the center and two on either side near the guides as a matter of computational choice, in this particular case dictated by the decision to treat the left and right front-to-back translations independently of each other. That decision dictated further that they should be placed relatively close to the guides. It should be understood, however, that one could use two such accelerometers together, even placed differently, as manifestations of a single, rotational acceleration (yaw) about a vertical axis. A rotational sensor could even be used.
Similarly, although a particular arrangement and choice of position sensors is shown, it should be realized that other types and arrangements may be used as well. For example, if it is desired to establish a rail profile for a system in which a pure electromagnet actuator is normally fixedly attached to the car with a variable gap between it and the rail, a gap sensor may be used to detect the variations in the gap as the elevator moves vertically. In this way, a similar positional indication of the displacement between the car and rail is obtained.
In any event, data is gathered for one or more runs of the elevator car which may, but need not, span its full operational range. The run may be at full, "contract" speed but need not be. This data may be processed as shown in Fig. 8 to generate one or more rail profiles.
Fig. 9 is a more detailed illustration of the processing method shown in Fig. 2 for rail profile estimation in a single axis. This method of estimation may accomplished, for example, by executing a series of steps which are as follows and which may be set up to run in a flow chart for execution on the signal processor 109 in a manner similar to that shown in Fig. 8:
In steps 150 & 152 integrate and detrend (subtract mean and first moment) the accelerometer output signal on line 117b twice;
In a step 154, high pass filter (third order Butterworth with 0.5 Hz breakpoint) the resultant signal, reversing time after the filtering operation to allow additional processing which will minimize phase shift or skew in data;
In a step 156, detrending the result of the filtering and reversal operation of step 154;
In a step 158, again high pass filter the resultant signal from step 156, again reversing time after the filtering operation to allow additional processing which will minimize phase shift or skew in data;
In a step 160, detrend the LVDT or potentiometer signal on the line 108;
In steps 162, 164 low pass filter (third order Butterworth with 20.0 Hz breakpoint) this signal twice, reversing time after each filtering operation to allow additional processing which will minimize phase shift or skew in the LVDT data;
In a step 166, summing the processed accelerometer and LVDT signals to formulate an effective estimate of rail displacement as a function of time; and
In steps 168, 170, low pass filter the vertical car position measurement twice, reversing time after each filtering operation to allow additional processing which will minimize phase shifts in this estimate of car position, creating in a step 172 a vertical position reference for the rail profile.
Table I summarizes the various functions that may be carried out in the above described steps as shown in Fig. 9:
The multi-pass filtering technique described is one method of smoothing data and is discussed in some detail in Applied Optimal Estimation, Chapter 5, "Optimal Linear Smoothing", Gelb, A., editor, MIT Press 1974. Other methods of data smoothing also exist, as discussed for example in Optimal Filtering, Chapter 7, "Smoothing of Discrete-Time Signals", Anderson, B.D.O., and J.B. Moore, Prentice-Hall, 1979, which could also be utilized.
The selection of filter break points in the smoothing algorithms of the rail estimation system logic is driven by the signal-to-noise characteristics of the sensors and the requirements of the rail estimate for enhancing ride quality. The lateral accelerometer measurements can be corrupted by two types of noise: (1) low frequency noise due to thermally induced electronic drifts and gravity vector misalignments and (2) high frequency electronic noise. Displacement transducers, such as the LVDTs or PPT, are subject to high frequency electronic noise. These parasitic noise effects, however, can be mitigated by filtering to result in rail estimates that are valid within a band of mid-range frequencies, such as the 0.5 to 20 Hz range. This selection of the filter range was determined to be the best compromise between noise reduction and rail estimation requirements based on a developed set of ride quality specifications (International Organization for Standardization (ISO), Guide for the Evaluation of Human Exposure to Whole-Body Vibration, Draft International Standard ISO/DIS 2631, Geneva, ISO, 1972), which indicates that humans are most affected by vibration in this frequency range.
The acceleration signals are filtered to remove the low frequency noise below 0.5 Hz. Double integration effectively removes the high frequency noise of those signals. The displacement signals are filtered to remove the high frequency noise above 20 Hz. The resultant rail estimate captures rail anomalies which are present in the frequency range to which humans are most susceptible.
Figs. 10, 11 and 12 are plots of several of selected signals of Fig. 9, for a high-speed elevator installation (Hoistway No. 4 in the Otis Elevator Company's Bristol, Connecticut Test Tower) for loads of 228 kg at the center of the cab, 228 kg at 94 cm to the left of center and 228 kg at 94 cm to the right of center, respectively, each Figure containing:

(a) the acceleration signal on line 117b plotted against car vertical position;
(b) the car horizontal relative displacement signal (with respect to the rail) on line 108 plotted against car vertical position;
(c) the doubly integrated and filtered acceleration signal on line 165a;
(d) the sum of the signals on lines 165a and 165b, in each case being a rail profile prediction for the respective load positioning.

As will be apparent, for the three different runs represented by Figs. 10, 11 & 12, the acceleration and relative displacement data are not repeatable. Thus, if one were to take the approach suggested by Otala, i.e, make an acceleration table, one could not base future behavior on the accelerations gathered during the learning run.
Moreover, as may be seen by comparing Figs. 10(c), 11(c) & 12(c), even if one were to take Otala's idea one step further and doubly integrate the acceleration signal to at least create a dimensionally correct deviation table, such would not be usable as these plots are not repeatable either.
Only when we follow the teachings of the present invention by summing the signal from any one of the Figs. 10(b), 11(b) or 12(b) with the respective signal from Fig. 10(c), 11(c) or 12(c), may we obtain a repeatable rail profile as shown in Figs. 10(d), 11(d) or 12(d).
Fig. 13(a) shows a top view of a roller guide, such as the passive roller guide of Fig. 3 modified into an active roller guide. It will be observed, especially by viewing Fig. 13(b) and (c), which are respectively side and back views of the roller guide of Fig. 13(a), that the three vertical springs, e.g., spring 66 of Fig. 3, have all been removed and replaced by actuators 180, 182, and a tie rod 184 attached by means of vertical rods 186, 188 in lieu of rocker arms 62, 76, respectively. The tie rod assembly obviates the need for two separate front-to-back actuators.
The actuator 180 is connected to rod 188 through a spring 190 and, similarly, actuator 182 is connected to rocker arm 72 by a spring 192.
Open-loop control signals on lines 194, 196 are provided to actuators 180, 182, respectively, to control the front-to-back and side-to-side vibrations on one side of the car. A similar actuator is situated on the other side of the car for the other rail as shown in Fig. 15.
Before turning to Fig. 15 in detail, it will be observed in Fig. 14 that a tie rod 198, Otis Part No. 96BY1, could be connected to the bottom of the rocker arm 62, 76 by means of a pair of sleeves 200, 202, Otis Part No. 130HLI, with a 3/8 inch (0.95 cm) nut 204, 206 at each end. The sleeves could be attached by means of a bolt 208 and C-clamp 209 combination, Otis Part Nos. 172DRA and 177JP8.
Of course, for this case, the three vertical springs, e.g., spring 66, would also be removed and the actuator 180 and spring 190 would be attached, e.g., to the rocker arm 76 instead of putting in a special rod 188.
Returning now to Fig. 15, an elevator car 210 is shown in plan view (viewed from the bottom of the car) situated between opposite hoistway walls 212, 214, having rails 216, 218 attached thereto, respectively. A pair of roller guides 220, 222 are shown mounted on the bottom of the car, but may be mounted on the top as well. Passive guides may be mounted on top and active guides on the bottom as an alternative method.
The roller guides 220, 222 are shown in schematic form, each having similar parts which numerals for only one of them identified in conformance with the same numbers used for Fig. 3 and Fig. 13 (the guide 220 on the left, except if the actuator 180, spring 190 combination swapped from wheel 52 to wheel 50 for convenience of illustration).
A signal processor 230, which may be a general purpose signal processor similar to that shown in Fig. 7, provides the control signals on the lines 194, 196 to the actuators 180, 182, respectively. Similar control signals 232, 234 are provided to a similar pair of actuators 236, 238 connected by way of springs 240, 242 to a tie rod 244 and a rocker arm (not shown) for a wheel 246. Wheels 248, 250 are connected to the tie rod 244 by means of rods similar to those shown previously in connection with Fig. 13(c).
The signal processor 230 is responsive to an elevator vertical position signal on a line 252 for retrieving for each of the actuators, a signal indicative of rail deviation at that particular height for that particular axis of control. The signal processor 230 provides four separate actuation signals on lines 194, 196, 232, 234 to the respective actuators 180, 182, 236, 238 for providing a counteracting force acting on the car due to the rail irregularity previously learned to be at that particular vertical position.
As shown in Fig. 16, this process is a repetitive process which may be utilized while the car is in vertical motion by entering at a step 260 and executing the previously described steps of obtaining vertical position, as shown in a step 262, retrieving rail deviation data is shown in a step 264, and providing an actuation signal (for each axis controlled) to the particular actuator to counteract the expected rail-induced force to be acting on the car due to a rail irregularity at that particular vertical position, as shown in the step 266. A step 268 determines whether or not the car is still in vertical motion and, if so, continues repeating steps 262, 264, 266 to keep the car stabilized as long as the car is in motion. If not, return is made via a step 270 to a main program. The whole process may be re-entered at step 260 upon detecting the car starting up again.
The relative motion between the elevator car and its wheels must be constrained to prevent metal to metal contact between the rails and the elevator safeties. This condition is most affected by an imbalance in the elevator car which results in the transmission of excessive lateral forces into the passive suspension elements. Present elevator suspensions ensure that this amount of excursion in the wheel travel is prevented by incorporating adjustable rubber snubbers 280, 282, 284, as shown in Fig. 3, which are set to a gap less than that between the rail and the mechanical safeties.
The active rail compensation system can be made to prevent excessive car/wheel deflections during imbalances in the elevator car payload by sensing this deflection with, e.g., a sensor 286 that provides a signal on a line 288, as shown in phantom in Fig. 13(b), for each positioning actuator, and adjusting the command to the positioning actuators. This leveling action could be initiated as a low frequency adjustment to the actuators. For example, prior to car acceleration, a snapshot could be taken of the rail to wheel deflections and a signal correction signal could be sent to all actuators to center the car for the indicated loading condition. This would have the net effect of mitigating the car imbalance and thereby extend the allowable travel in each of the car suspension points.
Those skilled in the art will recognize that one could, instead of integrating the sensed acceleration signals during the learning run and storing same as deviation values, store the acceleration signals and integrate them when needed. Similarly, the relative displacement sensor disclosed herein for measuring the distance between the car and rail could be replaced by another type of sensor such as an accelerometer which could be conditioned later to obtain the equivalent displacement information.
Although the invention has been shown and described with respect to a preferred embodiment thereof, it should be understood by those skilled in the art that the foregoing and various other changes, omissions and deletions in the form and detail thereof may be made therein without departing from the scope of this invention as defined by the claims.
Although the invention has been shown and described with respect to a preferred embodiment thereof, it should be understood by those skilled in the art that the foregoing and various other changes, omissions and deletions in the form and detail thereof may be made therein without departing from the scope of this invention as defined in the claims.

Claims

A method for measuring horizontal deviations from vertical of an elevator car rail, comprising the step of relating a vehicle position signal to a sensed car horizontal acceleration signal and a sensed signal indicative of the horizontal displacement of the car from the rail.
A method for estimating an elevator hoistway rail profile, comprising the steps of:
summing a relative horizontal displacement signal indicative of an elevator car's relative position with respect to said rail and a doubly integrated acceleration signal indicative of said car's horizontal displacement from a vertical inertial referent and-providing a summed signal; and
storing said summed signal according to the magnitude of a vertical position signal indicative of said car's vertical position in said hoistway.
A method as claimed in claim 2, comprising the steps of:
sensing a relative horizontal displacement between an elevator car and an elevator rail and providing a horizontal position signal having a magnitude indicative thereof;
sensing horizontal acceleration of said car and providing an acceleration signal indicative of the magnitude thereof;
doubly integrating said acceleration signal and providing an integrated signal indicative of the magnitude thereof;
summing said horizontal displacement signal and said integrated signal and providing a summed signal having a magnitude indicative of the sum of said position and integrated signal magnitudes;
Apparatus for estimating an elevator hoistway rail profile, comprising:
means responsive to a sensed acceleration signal having a magnitude indicative of horizontal acceleration of an elevator car, for doubly integrating said acceleration signal for providing an integrated signal having a magnitude indicative of horizontal displacement of said car from an inertial reference frame;
means for providing a relative displacement signal having a magnitude indicative of relative horizontal displacement between an elevator car and an elevator rail; and
signal processing means responsive to a vertical position signal having a magnitude indicative of said car's position in said hoistway and responsive to said displacement signals for storing horizontal position information derived from said displacement signals according to the magnitude of said vertical position signal.
Apparatus as claimed in claim 4 wherein said signal processing means include-: means for summing said integrated signal and said relative displacement signal and for storing resulting rail profile deviation signals according to the magnitude of said vertical position signal.
Apparatus as claimed in claim 4 or 5 comprising:
acceleration means disposed on the car for providing acceleration signals indicative of horizontal acceleration of the car;
displacement means disposed on the car for providing displacement signals indicative of the relative displacement of the car from the rail;
primary position sensing means for providing position signals indicative of the position of the car along the rail of the hoistway; and
signal processing means responsive to said acceleration means, said displacement means and said sensing means for successively storing mutually contemporaneous sets of said acceleration signals, said displacement signals, and said position signals.
Apparatus according to claim 6 wherein said signal processing means comprises:
means for providing a plurality of signals, each indicative of the approximate position of the rail with respect to a vertical reference at a given point along the rail uniquely indicated by said position signals, each derived from the sum of a corresponding one of said displacement signals with the double integral of said acceleration signals.
A method for controlling rail-induced horizontal vibrations of an elevator car, comprising the step of retrieving stored rail deviation data in response to an elevator car vertical position signal, wherein said rail deviation data was previously stored, according to said vertical position signal, by relating a sensed car horizontal acceleration signal to a sensed signal indicative of the horizontal displacement of said car from said rail.
The method of claim 8, wherein said relating comprises summing said horizontal displacement signal and said acceleration signal doubly integrated being indicative of said car's horizontal displacement from a vertical inertial referent.
A method of controlling rail-induced horizontal vibrations of an elevator car, comprising, on a learning run of the car, sensing car horizontal acceleration and providing a doubly integrated displacement signal indicative of the car's horizontal displacement from a vertical inertial referent, sensing the relative position of the car with respect to the rail and providing a horizontal displacement signal indicative thereof, and storing position information derived from said displacement signals in accordance with the vertical position of the elevator car; and on a subsequent controlled run of the car controlling an actuator in accordance with said stored position information.
A method as claimed in claim 10 comprising summing said displacement signals and storing resulting rail deviation information.