US3761790A - Method and apparatus for moving a shaft into a predetermined angular position - Google Patents

Method and apparatus for moving a shaft into a predetermined angular position Download PDF

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Publication number
US3761790A
US3761790A US00195757A US3761790DA US3761790A US 3761790 A US3761790 A US 3761790A US 00195757 A US00195757 A US 00195757A US 3761790D A US3761790D A US 3761790DA US 3761790 A US3761790 A US 3761790A
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Prior art keywords
shaft
speed
braking
angular position
arrangement
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English (en)
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H Daab
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Quick Rotan Becker and Notz KG
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Quick Rotan Becker and Notz KG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/02—Driving main working members
    • B23Q5/04—Driving main working members rotary shafts, e.g. working-spindles
    • B23Q5/20—Adjusting or stopping working-spindles in a predetermined position
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q15/00—Automatic control or regulation of feed movement, cutting velocity or position of tool or work
    • B23Q15/20—Automatic control or regulation of feed movement, cutting velocity or position of tool or work before or after the tool acts upon the workpiece
    • B23Q15/22—Control or regulation of position of tool or workpiece
    • B23Q15/26—Control or regulation of position of tool or workpiece of angular position
    • D—TEXTILES; PAPER
    • D05—SEWING; EMBROIDERING; TUFTING
    • D05B—SEWING
    • D05B69/00—Driving-gear; Control devices
    • D05B69/22—Devices for stopping drive when sewing tools have reached a predetermined position
    • D05B69/26—Devices for stopping drive when sewing tools have reached a predetermined position with automatic means to reduce speed of drive, e.g. in one or more steps

Definitions

  • ABSTRACT A method and apparatus through which a moving shaft [30] F i Application priority Data is sftopped in a predetermined angular position.
  • a regulating circuit controls the braking ac- [58] Field tion so that it is dependent on a comparison of the ac- 1 12/219 tual output speed ofthe shaft and a desired input speed, as well as the comparison of a computed braking angle [56] References Cited and the predetermined angular position to which the shaft is'to be rotated. Position and speed sensors con- UNITED STATES PATENTS nected to the shaft provide signals representing the ini stantaneous output position and speed of the shaft. rcn emue t 3,125,050 3/1964 Bertrand 3l8/467 X 27 Claims, 14 Drawing Figures 2 3 5 94 6 w 3 7 I M0702?
  • the present invention relates to a method and apparatus for positioning a shaft into a predetermined angular location by using an electrical motor with an electrically-operated coupling.
  • the coupling connects the shaft to be positioned with the motor for purposes of imparting to the shaft a predetermined operating speed.
  • the coupling, as well as a brake winding through which the shaft is braked into the desired end position, are energized and controlled through a regulating circuit.
  • Conventional position control arrangements of the preceding species operate, in general on the basis that when the shaft is to be positioned, it is first braked to a lower speed from its higher operating speed and then a regulator maintains the lower speed of the shaft until a synchronizer becomes actuated or becomes operative for applying the final braking action to bring the shaft to a stop position, whereby the speed is then reduced to zero.
  • the stopping process for the shaft under this conventional method is not a continuous process.
  • the conventional procedure is a stepwise control with intermediate delay periods in the lower operating speed portion of the cycle.
  • the time interval during which the shaft to be positioned, operates at the lower braked speed is dependent upon the angular position which the operating shaft is to assume upon reaching the lower braked speed, and thus this time interval can be greater or smaller.
  • This time interval can, in fact, attain a value which corresponds to a full revolution of the operating shaft when rotating at the lower braked speed.
  • Another object of the present invention is to provide a shaft positioning arrangement which has a long operating life and may be readily maintained.
  • the objects of the present invention are achieved by providing a method under which the actual output speed of the shaft to be positioned is continuously measured.
  • a braking torque is applied which is lower than the maximum applicable braking torque, as computed in correspondence to a required braking angle which is related to the actual output position of the shaft.
  • the actual output position of the shaft is measured instantaneously and compared with the computed braking angle.
  • the signal obtained from the comparison of the angular positions, as applied to the regulator which also is controlled through a speed comparison which compares a desired input speed of the shaft with the actual output speed of the shaft.
  • the regulator then provides signals by which the shaft is positioned into the desired angular location.
  • the time interval delay incurred with the lower braking speed used in the conventional methods is avoided.
  • the operating shaft is braked, in accordance with the present invention to zero velocity in one predetermined procedural step which applies a predetermined braking function.
  • the halting procedure of the shaft is regulated and this is also not found in the conventional methods. In the latter, there is no regulation after braking to the lower speed and allowing the synchronizer to become operative.
  • the shaft is also positioned with c0nsiderably greater accuracy and precision, in accordance with the present invention, and therefore considerable improvement is obtained over the prior art.
  • the brake can be fully applied when the procedure for stopping the shaft is initiated.
  • the brake can then be partially applied until the desired braking angle is attained.
  • the braking action in such case, is applied with full force in order to obtain a speed versus angle function which passes through zero, whereby no time is spent during an intermediate speed in correspondence to the conventional lower speed interval.
  • the actual output shaft speed can be obtained from variations in the speed of the angle measuring sensor. It is also possible, instead, to derive the value for the angular position from the actual speed parameter. For this purpose, pulses from a speed measurement may be summed from a speed output generator.
  • the output signal of the comparator which compares the braking function angle with the actual position of the shaft is preferably connected to a regulator which also takes into account the actual output shaft speed and the desired input shaft speed for the purpose of generating a regulating signal for purposes of bringing the shaft to the desired stationary position.
  • a gate is connected to the sensor which determines the actual output speed of the shaft for inhibiting the transmission of the output from the computing device for as long as the actual shaft output speed is above a predetermined value. Until this value is obtained, the braking action takes place exclusively on the basis of u comparison of the actual output speed of the shaft with a desired input speed.
  • This gate causes to prevent transmission from the output of the computer which computes the braking function and applies it to a comparator for comparing against the actual output angular position of the shaft.
  • the gate serves to block the output of this comparator for as long as the preset desired input speed is different from zero.
  • the gate permit the transmission of the output from the comparator which has the computing function as one input and the actual position of the shaft as the second input.
  • the regulator can have connected before it a control stage which causes the control windings for the motor coupling to be deenergized as a function of reaching the desired input position for the shaft.
  • the operating shaft becomes then freely rotatable after having reached its desired, predetermined angular position, and can then, as desired, be rotated by, for example, hand.
  • an angular measuring device with a hall generator is used.
  • the latter becomes influenced through a magnetic disc coupled to the operating shaft.
  • This magnetic disc has a continously decreasing radius from a maximum value to a minimum value. A sudden step takes place from the transition of the minimum value to the maximum value,
  • Such an angular measuring sensor or device ir independent of frequency and speed. As a result, angular positions can be precisely reproduced and measured even at low speeds for the shaft.
  • this angular position sensor in accordance with the present invention, has no contacts, and this results in substantially high operating reliability and long operating life of the unit.
  • the sudden step in the magnetic disc profile can be used, in a simple manner, for marking the desired input angle of the operating shaft.
  • the angular position sensor fulfills the function of a sensor for determining the actual output shaft angular position and as a generator for providing the desired input angle.
  • the actual speed sensor for determining the output shaft speed it is possible to use basically any of theconventional sensing devices, as for example, a tachogenerator which provides a voltage as a function of speed, or a pulse train which has a pulse frequency dependent'upon the shaft speed.
  • the hall generator for measuring angular position can also be used for providing speed measurements.
  • the actual output shaft speed is provided through a computing device which computes the speed from the measured angular position. Since the speed is the time derivative of angular position, the actual output speed can be obtained basically from the actual output angle, through the computing device which may be designed in the form of a differentiating stage.
  • Such a differentiating stage is well known in the art and can be of varied' construction.
  • a direct differentiation can lead to instabilities in the regulating system.
  • Such instabilities may be avoided when, in accordance with a further embodiment of the present invention, the actual shaft output speed and the actual shaft angular position from which the speed is determined through a computing device, are connected to two operational amplifiers.
  • the first of these operational amplifiers is in the form of a summing amplifier, whereas the second amplifier is constructed in the form of an integrator with feedback coupling so that when an input voltage of x(t) is applied, the output of the summing amplifier provides a voltage in the form of y(r) x by J' y dr.
  • b is different from one, and the integrator becomes reset at the completion of each revolution.
  • the computing dwvice for the braking function is provided preferably with an operational amplifier having a feedback network, so that when an input voltage x(t) is applied to the amplifier, the latter provides an output voltage of the form y(t) e C.
  • the comparator for comparing the braking function with the actual output shaft angle, as well as the second comparator can be advantageously designed in the form of summing amplifiers. Operational amplifiers of such design can be constructed from low cost miniature components having high precision.
  • the present invention provides for this feature by providing a control device which is influenced by the input angle position generator, whereby the regulator receives a control signal after the operating shaft has been stopped in the first desired position. This control signal then causes the operating shaft to further rotate into a second position.
  • a control device which is influenced by the input angle position generator, whereby the regulator receives a control signal after the operating shaft has been stopped in the first desired position. This control signal then causes the operating shaft to further rotate into a second position.
  • Programming stages are preferably provided through which the components used in the preceding arrangement can be controlled, so that the stopping of the shaft in the second desired position is always preceded by a braking of the shaft to the first desired position.
  • the transfer from the first position to the second shaft position can be carried out through any desired one of a number of possible circuits.
  • a particularly simple operating circuit is made possible by providing that by means of the desired input speed generator, the command signal for the transfer from the first position to the second position is also obtained.
  • FIG. I is a block diagram and shows the controlling arrangement for positioning a shaft, in accordance with the present invention.
  • FIG. 2 is a block diagram of a second embodiment of the arrangement of FIG. 1;
  • FIG. 3 is a schematic diagram of a third embodiment of the present invention.
  • FIG. 4 is a schematic diagram of a computing circuit for computing a braking function used in conjunction with the arrangement of the present invention
  • FIG. 5 is a circuit diagram for a preferred embodiment of the computing curcuit of FIG. 4;
  • FIG. 6 is a functional schematic diagram of an arrangement for deriving a speed signal from an angular position signal to be used in conjunction with the arrangement of the present invention
  • FIG. 7 is a circuit diagram for the arrangement of FIG. 6;
  • FIG. 8 is a sectional elevational view of a preferred angular position sensor, in accordance with the present invention.
  • FIG. 9 is a plan view of a magnetic element used in the sensor of FIG. 8;
  • FIG. 10 is an enlarged sectional view of an angular measuring device taken along line XX in FIG. 11;
  • FIG. 11 is a partial sectional view taken along line XI-XI in FIG. 10;
  • FIG. 12 is an enlarged view of the measuring head used in the angular measuring device illustrated in FIGS. 8 to 11, when viewed from below;
  • FIG. 13 is a graphical representation of the waveform of the signal provided by the angular measuring device used in FIGS. 8 to 12 for measuring an actual shaft position
  • FIG. 14 is a circuit diagram for stabilizing the arrangement using the angular measuring device shown in FIGS. 8 to 12.
  • the brake characteristics of a motorized or motor-driven coupling are generally known in the art, or they may be determined empirically in a simple manner.
  • motor-driven coupling arrangements operate in a manner that when a constant voltage is applied to the brake winding of the coupling, a constant braking torque is applied to the driven shaft.
  • Equation 4 illustrates that a quadratic relationship prevails between the angular rotation of the brake shaft and the speed of the shaft when the applied braking torque is constant. Consequently, provided that the braking torque remains constant, then a predetermined angle of rotation of the brake shaft can be associated for each value of shaft speed, through the quadratic relationship.
  • the principle of the present invention involves the use of a computing element which takes into account the known braking characteristics of a motor driven coupling, and computes the braking angle or rotational angle of the shaft for the corresponding speed of the shaft. After having computed the angular rotation of the driven shaft to be braked, this computed angle is compared with an instantaneously measured position of the shaft, and the comparison is used to generate a regulating signal or parameter by which the braking coils for the shaft and/or coupling windings are energized, in order to produce the desired end results. Such end result is achieved by forcing the braked shaft to become stopped in an angular position which corresponds to the angle computed by the computing element.
  • the precision for positioning a shaft is only limited through the component parts which are used, particularly the angle transducer which is the element that senses the instantaneous angular position of the shaft to be braked.
  • the design of the computing element for the braking function is not to be based upon the maximum applicable braking torque. Instead, the design is to be based on a braking torque which permits regulation with an applied torque which is also below that of the maximum applicable torque. In carrying out the braking process, furthermore, no regulating deviations are to prevail which will require an instantaneous increase in the applied braking torque.
  • FIG. 1 shows in schematic form, a positioning arrangement, in accordance with the present invention.
  • the motor 1 which drives the coupling has a continuous maximum rotational speed applied to its rotating shaft 2, which, in turn, carries a driving disc 3.
  • a driven shaft 4 carries a coupling disc 5 and a driving pulley 6.
  • the coupling disc 5 can be made to move into contact with the driving disc 3.
  • the coupling disc 5 is brought to bear or press against a braking member 9.
  • Motorized drives of this type of construction are also known in the art, which have a subdivided coupling disc. Such subdivided coupling disc makes it possible to simultaneously engage the driven shaft with the driving disc and the braking member with more or less pressure.
  • the windings 7 and 8 are controlled through a regulating circuit 10.
  • a rotational speed sensing device 11 determines continuously the instantaneous rotational speed of the driven shaft 4. Through the application of an input speed signal generator 12, the desired input speed of the driven shaft 4 may be adjusted or set. The signals from the speed sensor 11 and the input speed signal generator 12 are compared in a comparator 13. The difference between the two signals being compared, is applied in signal form to the regulating circuit 10. The arrangement described up to this point, is known in the art, and operates in the manner so that the regulating circuit provides regulation whereby the driven shaft is caused to operate at a speed corresponding to the input speed determined by the generator 12.
  • the output speed sensing device 11 is connected to a computing circuit 14, which computes the braking angle or angle of rotation of the shaft corresponding to the instantaneous speed of the shaft, as measured by the sensor 11.
  • This braking angle or angle of rotation of the shaft represents the angle through which the shaft will rotate to become stationary upon the application of a torque which is less than the required maximum braking torque.
  • the computing circuit 14 can be designed, for example, so that the applied braking torque corresponds to a predetermined level of excitation of the braking winding 8.
  • the output signal from the computing circuit 14 is applied to a comparator 16 which has also a second input derived from an angle transducer 15. This angle transducer measures angular position of a shaft or change in that position.
  • the angular position sensor 15 measures continuously the angle which the driven shaft must pass through in order to attain the desired position at which the shaft is to be stopped. This measured output angular position derived from the sensor 15 is compared with the desired input angle as computed by the circuit 14.
  • the computing circuit 14 provides the desired input or positioning the shaft, in accordance with the required braking angle corresponding to the prevailing rotational speed of the shaft to be positioned.
  • the output signal from the comparator 16 is also'applied to an input of the comparator 13.
  • the input speed signal generator 12 is set to zero, when the shaft is in the desired position.
  • the circuit elements 14, 15 and 16 are simultaneously set into operation.
  • a gate can be connected between the output of the comparator l6 and the corresponding input to the comparator 13, so as to gate as desired, the signal from the comparator 16 to the comparator 13.
  • the deviation of the input speed signal generator from the output speed sensor is adjusted so as to become zero.
  • the regulator 10 has then a signal applied to it by the comparator 13, so as to energize the brake winding 8.
  • strong braking of the driven shaft 4 results, as well as of any shaft connected to this driven shaft. The closer the instantaneous measured speed of the shaft is to the desired and set input speed, and this set input speed is zero, the stronger is the influence of the output signal on the comparator 16 on the regulator 10.
  • the drive shaft is brought to the position computed by the circuit 14, and the shaft is braked by the regulator 10 in correspondence with a predetermined braking function.
  • Such braking action applied by the regulating circuit 10 takes place until the output signals from the circuit 11, 12 and those from the elements l4, 15 are all equal, whereby the output from the comparator 13 is zero.
  • FIG. 2 shows in schematic form another embodiment of the arrangement of FIG. 1. From the viewpoint of simplifying the diagram, only the windings 7 and 8 are shown for the motor-driven arrangement. Thus, the motor 1 and the mechanically coupled parts thereto are omitted from the embodiment of FIG. 2 in order to maintain this diagram in simple form.
  • FIG. 2 provides for a gate circuit 17 connected between the output of the comparator l6 and the corresponding input of the comparator 13. Connected to the output of the input speed sensor 11, furthermore, is a control circuit 18 for switching the gate 17 on and off.
  • Another gate 19 is connected in series with the signal line leading from the output of the comparator 13 to the input of the regulating circuit 10. This gate 19 is controlled through a line 20 in dependence on the output signal from the comparator 16.
  • the gate 17 blockes the transmission of the output signal from the comparator 16, to the corresponding or respective input of the comparator 13.
  • the gate 17 becomes opened bythe control circuit 18 first when the signal from the sensor 11 has dropped below a predetermined value during the process in stopping the driven shaft.
  • the gate 17 in combination with the control circuit 18 makes it possible to fully energize the brake winding 8 during a first portion of the shaft stopping process. During this first portion of a stopping process, the difference between the output signals from the sensors 11 and generator 12 is substantially large, and the brake winding 8 is thereby to be energized independent of the output signal from the comparator 16.
  • the gate 19 is controlled so that the output signal from the comparator 13 can be applied to the regulating circuit 10.
  • the blocking signal applied by line to the gate 19 is such that the gate 19 is switched to its blocking state.
  • the regulating circuit 10 becomes, thereby, switched off, and the two windings 7 and 8 are deenergized.
  • the driven shaft 4 is, as a result, disengaged from the driving disc 3, as well as from the brake member 9, a situation which is often advantageous.
  • the sewing machine shaft is released in for such an angular position sensor is shown in further detail in FIGS. 8 to 14.
  • the input speed signal generator 12 provides a signal for the desired input speed of the desired stop position and can then be further adjusted or positioned manually as desired.
  • the shaft In the positioning of shafts in accordance with the species under consideration, it is often required to move the shaft into a second position after it was stopped in a first position. This second position may be spaced from the first position by an angular amount which is less than 360.
  • the driven shaft in this case, the sewing machine shaft, is to be moved to an angle of 180 after it has attained its first position where it is stopped through braking action.
  • the second position thereby, is a 180 displaced from the first position.
  • FIG. 3 An arrangement for carrying out such a positioning operation, is schematically shown in FIG. 3.
  • FIG. 3 there are groups of elements and components which are used in the arrangement of FIG. 2, with the exception that no speed measuring device corresponding to the speed sensor Ill is provided in conjunction with the angular position sensor 15. Instead, the instantaneous speed of the shaft is obtained through a differentiating stage 24 connected to the output signal from the angular position sensor 15. Thus, as a result of differentiating the displacement Signal from the sensor 15, the speed parameter is obtained.
  • the comparator 13 has a summing amplifier 26, p
  • a gate circuit 27, furthermore, is provided, which is associated with the secend position or positions P2. Further gate stages 28 and 29 are associated with the first position of the shaft or position P1.
  • the output of the signal generator 12 is connected to a blocking stage or gate 30, the output of which is, in turn, connected to flip-flops 31 and 32.
  • a monostable multivibrator circuit 33 is connected to one output of the flip-flop 33, and an AND gate 34 is interconnected with the elements 30, 31, 32 and 33.
  • a time delay circuit 35 is, furthermore, provided in the circuit diagram of FIG. 3.
  • the angular position sensor 15 provides a saw-tooth voltage-signal, the amplitude of which commences to rise from an angular position corresponding to the position 1 of the shaft to be controlled. After the shaft executes a a rotation of 360, the saw tooth signal drops back from a maximum amplitude level to its initial value.
  • the function of this saw tooth signal is represented in FIG. 13.
  • a particularly advantageous design the driven shaft in the form of an analogue DC voltage of predetermined polarity. With the use of the input speed signal generator 12, it is possible to transmit simultaneously the command for the transition from position I to the position 2 for the shaft.
  • Such a command for this purpose is in the form of, for example, a-DC voltage of opposite polarity when the position to be taken into account is position 2.
  • a-DC voltage of opposite polarity when the position to be taken into account is position 2.
  • Ths flip-flop 32 has also applied to it the signal output from the gate 30, and provides, in turn, an output signal through the line 40, for switching gate 29 whereby this gate 29 will not transmit.
  • no signal can be transmitted to the summing amplifier 26, from the circuit or gate 27 corresponding to position P2 of the shaft.
  • the gate 28 associated with the first position of the shaft or F1 is free to transmit as a result of the signal on the line 41, but this has no effect upon the functional operation, since gate 17 is inhibited from transmitting its signal input.
  • the input speed signal from the device 12 is applied, furthermore, through the summing amplifier 26.Since the shaft, to be positioned, is still stationary, the instantaneous speed signal as derived from the differentiating network 24, and applied to the summing amplifier 26, is zero.
  • the resultant output signal from the summing amplifier 26 is applied, through the gate 19, to the regulating circuit 10 and influences the latter whereby the coupling winding 7 is energized.
  • the driven shaft 4 becomes, thereby, coupled to the shaft 2 of the motor, and the driven shaft 4 is, consequently, accelerated.
  • the input speed signal from the device 12 furthermore, inhibits the transmission of gate 117, simultaneously through the application of a signal to line 39,
  • the comparator 16 is also constructed in the form of a summing amplifier.
  • the angular position sensor 15 For every revolution of the driven shaft 4, the angular position sensor 15 provides a linearly increasing voltage from a minimum value to a maximum value. The slope of this linear function or the rate of increase in value of this function is, determined through differentiation by the differentiating stage 24 and the output signal from this stage 2d represents the actual. instantaneous output speedof the shaft 4. This actual output speed of the shaft 4 is compared with the desired input speed in the summing amplifier 26. As soon as the output signal from the summing amplifier 26 indicates that the difference between the actual output speed and the desired input speed is zero, then the desired input speed is obtained and the regulating circuit 10 will deenergize the winding 7. The summing amplifier 26 causes the regulating circuit 10 to maintain the driven shaft 4 at the desired input speed. In the case that the input speed signal generator 12 is set to the new input speed value, then the summing amplifier 26 and regulator l combine to operate so as to adjust the speed of the driven shaft 4 to the new value.
  • the positioning of the driven shaft at the position P1, or the first position is attained by setting the input speed signal generator 12 to zero. With this setting, the blocking signal applied to the line 39 is removed.
  • the gate '17 remains still in an untransmitting state, temporarily, as a result of the infuence of the gate control circuit 18.
  • the signal from the amplifier 16 is still blocked from being transmitted by the gate 17, as a result of the control circuit 18.
  • the summing amplifier 26 receives only the relatively high signal indicating the output instantaneous speed of the shaft 4, whereas the input speed signal is zero.
  • the regulator circuit 10 thereby applies full energization to the brake winding 8.
  • the driven shaft becomes subjected to maximum braking moment, independent of the output signal from the comparator 16, so that the driven shaft 4 becomes strongly braked.
  • the control circuit 18 becomes switched and as a result, the gate 17 is permitted to transmit the signal from the comparator 16.
  • the difference signal from the com parator 16 is transmitted to the summing amplifier 26.
  • the difference signal between the desired input angular position and the actual instantaneous output shaft position is superimposed upon the speed signals for the input and output shaft speeds, and this superimposing of the position signals upon the speed signals in this manner, causes attenuation or decrease in the excitation of the braking winding.
  • Further braking action, thereby, is applied in a regulated manner as a function of angular position, in accordance with the computed braking function provided by the circuit 14. As soon as the output speed signal and the output signal from the comparator 16 are both zero, then the position P1 for the driven shaft 4 is attained, and the shaft is held stationary.
  • the circuit 35 is designed so that it provides an output signal when its input corresponds to the instantaneous actual angular position of the shaft which is greater than'that for a predetermined time interval. This time interval is determined so that the circuit 35 will not become activated when the position P1 is passed through during rotation of the shaft 4 while under speed, as well as during braking. However, after the shaft has become stationary in the position P], then the circuit 35 becomes actuated. With actuation of this circuit 35, a signal is transmitted from the circuit to the input e2 of the flip-flop 31. This causes the flip-flop 31 to be reset, whereby the gate 19 is inhibited from transmitting through the line 38. The regulating circuit becomes, thereby, disconnected from the comparator 13. As a result, the coupling and brake windings 7, 8 are de-energized. The driven shaft 4 can, thereafter, be manually rotated as desired.
  • the speed signal generator 12 is set to the opposite direction, a signal of opposite polarity is applied to the flip-flop 32, by way of the gate 30.
  • the flip-flop 32 becomes thereby switched, and actuates the monostable multivibrator circuit 33 with the signal applied from the output A1 of the flip-flop 32.
  • the monostable multivibrator circuit 33 With the consequent switching of the monostable multivibrator circuit 33, the latter provides an output signal for a time interval which is larger than the time duration which is required for moving the driven shaft 4 from position 1 into position 2.
  • This output signal from the multivibrator 33 is applied to the flip-flop 31 at input c3, and the gate 19 is permitted to transmit, as a result of the signal upon line 38.
  • the gate 30 is switched so as to prevent transmitting of its signal from the device 12, as a result of the line 42, so that no signal from the speed generator 12 can reach the comparator 13.
  • the signal from the output A1 of the flip-flop 32 permits the gate 29 associated with position P2, to transmit as a result of this signal on line 40.
  • the transmitting state of the gate 28 associated with position P1 is continued.
  • the summing amplifier cannot receive any signal from the comparator 16 thereby.
  • the circuit gate 27 associated with position P2 compares the instantaneous output angular position of the shaft 4, as indicated by the sensor 15, with a reference voltage U As long as the actual position of the shaft 4 as represented by the signal from the sensor 15, is smaller than this reference voltage, the comparator 13 receives a signal by which the coupling winding 7 becomes energized. The driven shaft 4 commences, thereby to rotate anew. As soon as the angular position signal from the sensor 15 becomes equal to the value of the reference voltage U,, this gate circuit 27 transmits, through the gate 29, to the summing amplifier 26 a signal which when transmitted through gate 19 applies a braking commence signal to the regulator 10. As a result, the shaft 4 becomes braked and is held stationary in position P2.
  • the flip-flop 31 becomes reset.
  • the gate 19 becomes, thereby switched to the state where it does not transmit, and the regulating circuit 10 is disconnected from the output of the summing amplifier 26. Consequently, both windings 7 and 8 are deenergized.
  • the signal inhibiting states of the gates 28 and 30 must be discontinued so that these two gates are free to transmit.
  • the gate 29 associated with position P2 becomes again switched so that it will not transmit or it is in the inhibiting state.
  • the AND gate 34 makes certain that the flip-flop 32 becomes switched first after the shaft 4 is held stationary in the position Pl. Through this condition, it is achieved that the positioning of the shaft into a position P2 must always be preceded by a positioning of the shaft into a position P1.
  • equations 1 to 4 a quadratic relationship prevails between the brake angle and the speed of the shaft when constant braking torque is applied.
  • This quadratic relationship is relatively complicated from the circuit point of view.
  • the quadratic function can be approximated through w e' C
  • the preceding equation 5 can be reproduced in circuit form through the use of an operational amplifier 45 with feedback, as shown in FIG. 4.
  • a germanium diode when driven in the conductive state, has an output function which is proportional to the logarithm of the current through the diode, minus the logarithm of the saturation current.
  • the feedback network 46 shown in FIG. 4 can be constructed inaccordance with making use design illustrated in FIG. 5.
  • the feedback circuit 46 can consist of a resistor 48 connected between the output and input of the operational amplifier 45, and a germanium diode 48 connected between the output of the amplifier and ground potential.
  • Equation 7 can be produced through two operational amplifiers in accordance with.
  • the first amplifier 49 in FIG. 6, is arranged as a summing amplifier, whereas the second amplifier 50 is designed as an integrator.
  • FIG. 6 schematic arrangement of FIG. 6 may -be obtained through the detailed description of the circuit diagram of. FIG. 7.
  • the angular position sensor has a particularly important part in the arrangement. From the viewpoint of'operating reliability and high operating life, it is desirable that the angular position sensor be of the contactless type.
  • the sensor has a rotational member or body 60 which is mounted on one end of the shaft 4, not shown in FIG. 8.
  • the rotational member 60 is held to the shaft 4 through a set screw which is threaded in a bore 61 of the member 60.
  • a ball bearing 62 is mounted upon a portion of the body 60 which has a smaller diameter, and is located towards the right in the drawing of FIG. 8.
  • the outer ring of the ball bearing 62 is seated in a stationary part of a housing 63.
  • a measuring head 65 is secured by means of screws 64 to the housing portion 62.
  • the angled element or bracket 66 carries a U- shaped outer screening member 78, as well as an oppositely-lying U-shaped interior screening member 79.
  • the interior screening member is oriented with respect to the outer scanning member 78 by the amount of 90.
  • the width of the interior screening member corresponds essentially to the oppositely lined outer edges of the measuring strips 75, 76.
  • pole pieces or elements 80, 81 In the space between the ends of the outer screening 78, on the one hand, as well as the ends of the inner screening 79 and the measuring strips 75, 76, on the other hand, are two pole pieces or elements 80, 81. These pole pieces are clamped, through a screw 82, between an insulating element 83 or 841 and a magnetically conductive ring 85 or 86. These pole pieces, furthermore, rotate together with the rotational member 60 and thereby together with the shaft 4 to be regulated in movement. Between the rings 85, 86 is a ring-shaped permanent magnet 87 which is axially polarized.
  • the pole pieces 80, 81 are of this shaft illustrated in FIG. 9. Their outer edge, as shown in that FIG. 9 form a spiral which satisfies the condition that dw/dr const.
  • the rings 85, 86 form an enclosure for the magnet 87, which prevents that the pole pieces 80, 811 become saturated. These rings 85, 86, furthermore, reduce strongly the stray magnetic flux and determine the field strength or field intensity at the pole pieces through their defined magnetic reluctance.
  • the hall generator 72 and the measuring strips 75, 76 the magnetic flux is measured between the pole pieces 80, 8l'within the region of the measuring strips 75, 76.
  • this magnetic flux and thereby the voltage provided by the hall generator 72 are proportional to the angu- .lar rotation of the shaft 4 which is transmitted directly to the rotational member 60.
  • a voltage is available as shown in FIG. 13. It may be seen, thereby that by adjusting the angular position of the rotational member 60 in relation to the shaft 4,-the desired input angle (which corresponds to position P11 in accordance with FIG. 3) may be obtained in a predetermined and simple manner.
  • the input speed signal generator 13 can be designed directly on the basis of the arrangement described above in conjuntion with the angular position sensor 15, with the exception that the rotational member 60 is not connected to the driven shaft 4. In this case, the rotational member 60 is instead to be connected to a positioning member or element which is actuated or adjusted manually by being set either by hand or by foot.
  • a further input speed signal generator for the device 12 is also well known in the art in the form of a device which operates on the contactless principle.
  • FIG. 14 shows the hall generator for measuring angular position through the sensor 15, when connected with a stabilizing circuit which improves particularly upon the desired angular input position signalling, within the frame of the present invention.
  • the sensor 15 is in the form of the construction illustrated by FIGS. 8 to 12.
  • the angular position sensor 15 provides a linearly increasing saw-tooth voltage from a lowest level U,, to a maximum level U,.
  • the voltage values corresponding to U and U as, for example, zero volts and +6 volts, respectively, are held constant. Values between these two extreme limits are also thereby precisely determined.
  • the output signal from the operational amplifier 90 is applied to integrators with substantially large time constants. These integrators consist essentially of a resistor 91, a diode 92, and a capacitor 93 for one network, and a diode 94 and capacitor 95 for another network.
  • the output voltages from the integrators are compared wth reference voltages of which one consist of ground potential and the other is determined by a Zener diode 96.
  • the operational amplifier 90 becomes correspondingly influenced through the transistors 97, 98 and a resistor 99.
  • the operational amplifier becomes influenced by a corresponding variation of the operating point of the amplifier.
  • the regulated variation of the voltage value U varies the hall generator current, through transistors 100, 101 and 102. If, for example, a positive voltage appears across the diode 94 during a longer time interval, then this implies that the amplification is too low. As a result, the hall generator current is increased by way of the three transistors 100, 101, 102.
  • the arrangement in accordance with FIG. 14 allows the elimination of all temperature and component manufacturing variations.
  • the actual output speed of the shaft 4 can also be determined through the use of a speed measuring tachometer.
  • a speed measuring tachometer for example, has a permanent magnetic disc connected to the driven shaft 4.
  • the permanent magnetic disc has a peripheral surface of an alternating sequence of magnetic North and South poles.
  • a magnetic coil is located in proximity of the permanent manetic disc and has induced within it a voltage, the amplitude and frequency of which, are essentially proportional to the rotational speed of the driven shaft 4.
  • the actual ouput angular position of the shaft can be derived from the measured speed through the tachometer, or tachogenerator, by applying the speed signal to an integrator or integrating stage.
  • Such an integrating stage sums the pulses from the tachogenerator.
  • the integrator becomes reset through a synchronizer during each rotation of the shaft 4, in correspondence to a predetermined, desired stopped position of the shaft 4.
  • the synchronizer for this purpose is well known in the art.
  • the advantage of a speed tachometer or tachogenerator resides on the basis that a substantially high output voltage can be derived without noise effects, which can be applied directly as the actual output value, to the regulator circuit 10.
  • a synchronizer in accor-' dance with the conventional design, a reproducable voltage signal can be obtained from the hall generator for the desired input position for the shaft, for each revolution of the shaft.
  • a method for moving a shaft to a predetermined angular position comprising the steps of: applying a source of rotary motion to said shaft for rotating said shaft at an angular speed corresponding to the speed of said source; measuring the instantaneous angular speed of said shaft; computing from the instantaneous speed of said saft a braking angle throughout which said shaft is to be braked to stop said shaft at said predetermined angular'position, said braking angle being dependent on said instantaneous speed; removing said source of rotary motion from said shaft and permitting said shaft to continue rotating without continued application of said source; comparing the instantaneous angular position of said shaft with said braking angle; comparing said instantaneous speed of said shaft with a predetermined desired speed; and braking said shaft dependent on said comparing steps so that said shaft becomes stopped at said predetermined angular position.
  • An arrangement for carrying out the method of claim 1 for moving a shaft to a predetermined angular position comprising, in combination, a source of rotational motion for rotating said shaft at an angular speed corresponding to the speed of said source; coupling means between said source and said shaft; braking means connectable to said shaft for braking said shaft and decreasing the speed of said shaft, said braking means being applied to said shaft when said shaft is decoupled from said source; speed measuring means connected to said shaft for measuring the instantaneous speed of said shaft; first comparator means connected to said speed measuring means for comparing said instantaneous speed with a desired input speed of said shaft; computing means connected to said speed measuring meas for computing a braking angle function; second comparator means connected to said computing means for comparing a braking angle function with said predetermined angular function; and regulating means connected to said comparator means for regulating said braking means in dependency on said braking angle function, whereby said shaft is braked so that said shaft is stopped at said predetermined angular position.
  • said speed measuring means comprises speed computing means for computing the instantaneous speed of said shaft from the angular position of said shaft.
  • said speed computing means for computing said instantaneous speed of said shaft comprises two operational amplifiers connected in series, one of said operational amplifiers being a summing amplifier and the other one of said amplifiers being an integrating amplifier, said two amplifiers being further connected so that when applying an input signal of the form x(t) to said summing amplifier the output signal of said summing amplifier is of the form of y(t) x by I y dt.
  • said computing means comprises an operational amplifier with feedback network interconnected to said operational amplifier so that upon applying an input signal of the form of x(t) to the input of said operational amplifier, an output signal from said amplifier is obtained in the form of y(t) e C.
  • said second comparator means comprises an operational amplifier with feedback network whereby said operational amplifier functions as a summing amplifier.
  • said first comparator means comprises an operational amplifier with feedback network interconnected to said operational amplifier, whereby said operational amplifier functions as a summing amplifier.
  • said braking means comprises an electromagnetic brake having a winding energized by said regulating means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Textile Engineering (AREA)
  • Stopping Of Electric Motors (AREA)
  • Control Of Position Or Direction (AREA)
US00195757A 1970-11-05 1971-11-04 Method and apparatus for moving a shaft into a predetermined angular position Expired - Lifetime US3761790A (en)

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US (1) US3761790A (de)
JP (1) JPS549266B1 (de)
CH (1) CH528779A (de)
DE (1) DE2054501B1 (de)
ES (1) ES395738A1 (de)
FR (1) FR2113634A5 (de)
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HK (1) HK10678A (de)
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Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3906315A (en) * 1974-01-15 1975-09-16 Aerojet General Co Closed-loop, precision-stop induction motor control circuit
US3921770A (en) * 1973-05-23 1975-11-25 Quick Rotan Becker & Notz Kg Arrangement for driving two output shafts
US3949582A (en) * 1975-04-11 1976-04-13 Eaton-Leonard Corporation Positioning servo and controlled mechanism
US3958166A (en) * 1972-03-16 1976-05-18 National Research Development Corporation Speed adjusting apparatus
US3972297A (en) * 1974-01-30 1976-08-03 Union Special Corporation Sewing machine position and speed sensing system
US4013933A (en) * 1973-03-23 1977-03-22 Matsushita Electric Industrial Co., Ltd. Needle position detector for industrial type sewing machines
US4080914A (en) * 1975-09-23 1978-03-28 Hitachi, Ltd. Sewing machine with improved non-ravel seaming controller
FR2374770A1 (fr) * 1976-12-20 1978-07-13 Quick Rotan Becker & Notz Kg Mecanisme de positionnement
US4108090A (en) * 1977-03-21 1978-08-22 The Singer Company Programmable variable speed for sewing machine
US4136304A (en) * 1975-05-30 1979-01-23 Brown, Boveri & Co. Ltd. Control device for a braking mechanism using an energy-storing spring
DE2830624A1 (de) * 1977-07-13 1979-02-01 Hitachi Ltd Schutzeinrichtung fuer elektrische naehmaschine
US4147120A (en) * 1977-09-14 1979-04-03 Union Special Corporation Auxiliary feed mechanism for sewing machines
US4161921A (en) * 1976-07-23 1979-07-24 Aisin Seiki Co., Ltd. Motor control system for sewing machine
US4195585A (en) * 1977-03-30 1980-04-01 Hitachi, Ltd. Protection apparatus for electric sewing mechine
US4246523A (en) * 1978-02-09 1981-01-20 Kabushiki Kaisha Komatsu Seisakusho Brake timing control method and apparatus therefor
US4254724A (en) * 1978-06-14 1981-03-10 Maschinenfabrik Carl Zangs Aktiengesellschaft Method for the determination of the switching moments for special functions of automatic sewing-machines
DE2938040A1 (de) * 1979-09-20 1981-04-09 Quick Elektromotoren-Werk GmbH, 6100 Darmstadt Positionierantrieb
FR2474713A1 (fr) * 1980-01-29 1981-07-31 Quick Rotan Elektromotoren Generateur de valeur de consigne pour commandes d'entrainement
EP0045649A2 (de) * 1980-07-31 1982-02-10 Matsushita Electric Industrial Co., Ltd. Drehgeschwindigkeitsmesseinrichtung für Nähmaschinen
EP0053938A1 (de) * 1980-12-09 1982-06-16 Matsushita Electric Industrial Co., Ltd. Vorrichtung zum Regeln der Antriebsgeschwindigkeit bei einer Nähmaschine
US4364002A (en) * 1978-12-30 1982-12-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control of operation of loom
US4392098A (en) * 1981-10-16 1983-07-05 Pt Components, Inc. RPM Sensor for electronic motor braking
EP0083068A1 (de) * 1981-12-24 1983-07-06 Quick-Rotan Elektromotoren GmbH Drehzahlgeregelter Nähantrieb
US4513676A (en) * 1982-08-30 1985-04-30 Microdynamics, Inc. Method and apparatus for automatically decelerating and stopping a sewing machine motor
US4516514A (en) * 1982-09-25 1985-05-14 Matsushita Electric Industrial Co., Ltd. Circuit arrangement for controlling sewing machine speed and for positioning sewing needle
US4648339A (en) * 1984-05-30 1987-03-10 Mitsubishi Denki Kabushiki Kaisha Speed control apparatus for sewing machine
US4658742A (en) * 1983-01-24 1987-04-21 Institutul De Cercetare Stiintifica Si Inginerie Technologica Pentru Industria Electrotechnica-Icpe Electronic controlling equipment for driving systems with electromagnetic couplings for industrial sewing and/or overcasting machines
US4776528A (en) * 1987-09-03 1988-10-11 Eastman Kodak Company Apparatus for positioning a takeup reel to receive the lead end of a web
US4947772A (en) * 1987-11-06 1990-08-14 Janome Sewing Machine Co. Ltd. Finish-up stitching control in an electronic sewing machine
EP0526852A1 (de) * 1991-08-07 1993-02-10 Western Atlas Inc. Tischantrieb mit Reibungskupplung
DE19518390A1 (de) * 1995-05-19 1996-11-21 Inofex Gmbh Verfahren und Einrichtung zur Steuerung und Regelung von Antriebssystemen, vorzugsweise für Fleischereimaschinen, in denen heterogene mehrstufige Stoffumwandlungsprozesse ablaufen
US5838124A (en) * 1997-08-28 1998-11-17 Barber Colman Systems and methods for braking of actuator and brushless DC motor therein
US5847530A (en) * 1997-08-28 1998-12-08 Barber Colman Systems and methods for torque control of actuator and brushless DC motor therein
US5872434A (en) * 1997-08-28 1999-02-16 Barber Colman Company Systems and methods for actuator power failure response
US20080159467A1 (en) * 2006-12-27 2008-07-03 Uwe Kassner Method for determining the rotation speed of rotating shaft
US20090101227A1 (en) * 2005-05-24 2009-04-23 Lindauer Doriner Gesellschaft Mbh Method for Operating a Projectile Loom
EP1856584B1 (de) 2005-03-11 2016-07-27 Atlas Copco Rock Drills AB Sensoranordnung eines getriebes zur positionierung

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JPS59136093A (ja) * 1983-01-25 1984-08-04 Mitsubishi Electric Corp ミシンの速度制御回路
JPS61249494A (ja) * 1985-04-27 1986-11-06 ジューキ株式会社 ミシンの布送り量自動変更装置
CN114543590A (zh) * 2022-02-25 2022-05-27 盾石磁能科技有限责任公司 用于双重加速系统控制的方法、装置、终端及存储介质

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US3582739A (en) * 1968-07-09 1971-06-01 Quick Rotan Becker & Notz Kg Synchronizer for presetting the stop position of a rotary shaft
US3659172A (en) * 1970-02-12 1972-04-25 Hitachi Ltd Motor controlling device

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US3125050A (en) * 1964-03-17 Bertrand
US2537269A (en) * 1948-03-18 1951-01-09 Ex Cell O Corp Spindle positioning device
US2753502A (en) * 1952-12-02 1956-07-03 Bardons And Oliver Inc Electric motor control for spindle positioner
US2767363A (en) * 1953-09-10 1956-10-16 Sperry Rand Corp Limit-stop control system
US3226621A (en) * 1962-04-28 1965-12-28 Georgii Kobold Elektro Motoren Sewing machine drive
US3412260A (en) * 1963-09-20 1968-11-19 Frankl & Kirchner Electrical drive means, particularly for sewing machines
US3439249A (en) * 1967-01-16 1969-04-15 Warner Electric Brake & Clutch Control for actuating an electric brake to stop a driven load upon loss of electrical power
US3582739A (en) * 1968-07-09 1971-06-01 Quick Rotan Becker & Notz Kg Synchronizer for presetting the stop position of a rotary shaft
US3659172A (en) * 1970-02-12 1972-04-25 Hitachi Ltd Motor controlling device

Cited By (41)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3958166A (en) * 1972-03-16 1976-05-18 National Research Development Corporation Speed adjusting apparatus
US4013933A (en) * 1973-03-23 1977-03-22 Matsushita Electric Industrial Co., Ltd. Needle position detector for industrial type sewing machines
US3921770A (en) * 1973-05-23 1975-11-25 Quick Rotan Becker & Notz Kg Arrangement for driving two output shafts
US3906315A (en) * 1974-01-15 1975-09-16 Aerojet General Co Closed-loop, precision-stop induction motor control circuit
US3972297A (en) * 1974-01-30 1976-08-03 Union Special Corporation Sewing machine position and speed sensing system
US3949582A (en) * 1975-04-11 1976-04-13 Eaton-Leonard Corporation Positioning servo and controlled mechanism
US4136304A (en) * 1975-05-30 1979-01-23 Brown, Boveri & Co. Ltd. Control device for a braking mechanism using an energy-storing spring
US4080914A (en) * 1975-09-23 1978-03-28 Hitachi, Ltd. Sewing machine with improved non-ravel seaming controller
US4161921A (en) * 1976-07-23 1979-07-24 Aisin Seiki Co., Ltd. Motor control system for sewing machine
FR2374770A1 (fr) * 1976-12-20 1978-07-13 Quick Rotan Becker & Notz Kg Mecanisme de positionnement
US4108090A (en) * 1977-03-21 1978-08-22 The Singer Company Programmable variable speed for sewing machine
US4195585A (en) * 1977-03-30 1980-04-01 Hitachi, Ltd. Protection apparatus for electric sewing mechine
DE2830624A1 (de) * 1977-07-13 1979-02-01 Hitachi Ltd Schutzeinrichtung fuer elektrische naehmaschine
US4147120A (en) * 1977-09-14 1979-04-03 Union Special Corporation Auxiliary feed mechanism for sewing machines
US4246523A (en) * 1978-02-09 1981-01-20 Kabushiki Kaisha Komatsu Seisakusho Brake timing control method and apparatus therefor
US4254724A (en) * 1978-06-14 1981-03-10 Maschinenfabrik Carl Zangs Aktiengesellschaft Method for the determination of the switching moments for special functions of automatic sewing-machines
US4364002A (en) * 1978-12-30 1982-12-14 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control of operation of loom
DE2938040A1 (de) * 1979-09-20 1981-04-09 Quick Elektromotoren-Werk GmbH, 6100 Darmstadt Positionierantrieb
FR2474713A1 (fr) * 1980-01-29 1981-07-31 Quick Rotan Elektromotoren Generateur de valeur de consigne pour commandes d'entrainement
EP0045649A3 (en) * 1980-07-31 1982-07-07 Matsushita Electric Industrial Co., Ltd. Speed detector for sewing machines
EP0045649A2 (de) * 1980-07-31 1982-02-10 Matsushita Electric Industrial Co., Ltd. Drehgeschwindigkeitsmesseinrichtung für Nähmaschinen
EP0053938A1 (de) * 1980-12-09 1982-06-16 Matsushita Electric Industrial Co., Ltd. Vorrichtung zum Regeln der Antriebsgeschwindigkeit bei einer Nähmaschine
US4392098A (en) * 1981-10-16 1983-07-05 Pt Components, Inc. RPM Sensor for electronic motor braking
EP0083068A1 (de) * 1981-12-24 1983-07-06 Quick-Rotan Elektromotoren GmbH Drehzahlgeregelter Nähantrieb
US4513676A (en) * 1982-08-30 1985-04-30 Microdynamics, Inc. Method and apparatus for automatically decelerating and stopping a sewing machine motor
EP0103364B1 (de) * 1982-08-30 1987-11-04 Microdynamics, Inc. Verfahren und Vorrichtung zum Verlangsamen der geschwindigkeit und Anhalten eines Nähmaschinenantriebsmotors
US4516514A (en) * 1982-09-25 1985-05-14 Matsushita Electric Industrial Co., Ltd. Circuit arrangement for controlling sewing machine speed and for positioning sewing needle
US4658742A (en) * 1983-01-24 1987-04-21 Institutul De Cercetare Stiintifica Si Inginerie Technologica Pentru Industria Electrotechnica-Icpe Electronic controlling equipment for driving systems with electromagnetic couplings for industrial sewing and/or overcasting machines
US4648339A (en) * 1984-05-30 1987-03-10 Mitsubishi Denki Kabushiki Kaisha Speed control apparatus for sewing machine
US4776528A (en) * 1987-09-03 1988-10-11 Eastman Kodak Company Apparatus for positioning a takeup reel to receive the lead end of a web
US4947772A (en) * 1987-11-06 1990-08-14 Janome Sewing Machine Co. Ltd. Finish-up stitching control in an electronic sewing machine
EP0526852A1 (de) * 1991-08-07 1993-02-10 Western Atlas Inc. Tischantrieb mit Reibungskupplung
DE19518390A1 (de) * 1995-05-19 1996-11-21 Inofex Gmbh Verfahren und Einrichtung zur Steuerung und Regelung von Antriebssystemen, vorzugsweise für Fleischereimaschinen, in denen heterogene mehrstufige Stoffumwandlungsprozesse ablaufen
DE19518390C2 (de) * 1995-05-19 1999-02-18 Inofex Gmbh Verfahren und Schaltungsanordnung zur Steuerung und Regelung eines Antriebssystems für die Verarbeitung eines Rohstoffes, vorzugsweise für Fleischereimaschinen
US5838124A (en) * 1997-08-28 1998-11-17 Barber Colman Systems and methods for braking of actuator and brushless DC motor therein
US5847530A (en) * 1997-08-28 1998-12-08 Barber Colman Systems and methods for torque control of actuator and brushless DC motor therein
US5872434A (en) * 1997-08-28 1999-02-16 Barber Colman Company Systems and methods for actuator power failure response
EP1856584B1 (de) 2005-03-11 2016-07-27 Atlas Copco Rock Drills AB Sensoranordnung eines getriebes zur positionierung
EP1856584B2 (de) † 2005-03-11 2023-06-07 Epiroc Rock Drills Aktiebolag Sensoranordnung eines getriebes zur positionierung
US20090101227A1 (en) * 2005-05-24 2009-04-23 Lindauer Doriner Gesellschaft Mbh Method for Operating a Projectile Loom
US20080159467A1 (en) * 2006-12-27 2008-07-03 Uwe Kassner Method for determining the rotation speed of rotating shaft

Also Published As

Publication number Publication date
HK10678A (en) 1978-03-03
DE2054501B1 (de) 1971-12-30
NL7114265A (de) 1972-05-09
GB1339468A (en) 1973-12-05
IT939854B (it) 1973-02-10
ES395738A1 (es) 1973-11-16
CH528779A (de) 1972-09-30
NL162151C (nl) 1980-04-15
JPS549266B1 (de) 1979-04-23
FR2113634A5 (de) 1972-06-23
NL162151B (nl) 1979-11-15

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