US3851819A - Driving device for rotary chemical machine - Google Patents

Driving device for rotary chemical machine Download PDF

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Publication number
US3851819A
US3851819A US00383180A US38318073A US3851819A US 3851819 A US3851819 A US 3851819A US 00383180 A US00383180 A US 00383180A US 38318073 A US38318073 A US 38318073A US 3851819 A US3851819 A US 3851819A
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Prior art keywords
shaft
output shaft
rotary
timing wheel
rotary casing
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US00383180A
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English (en)
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T Tadokoro
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Tsukishima Kikai Co Ltd
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Tsukishima Kikai Co Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
    • B04B9/10—Control of the drive; Speed regulating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
    • B04B9/08—Arrangement or disposition of transmission gearing ; Couplings; Brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19605—Reversing means
    • Y10T74/19609—Governor control

Definitions

  • a rotary chemical machine such as centrifugal separator, particularly a centrifugal separator of the type having a discharger for discharging off the muddy material out of a separating basket thereof, ordinarily needs to be rotated at two different rotating speeds at least, such as, at high speed in low torque for separating liquid from solid material and at low speed in high torque for discharging solid material out of the separating basket.
  • the conventional centrifugal separator having a scrathing edge has two driving devices.
  • One of these is a driving device having two prime motors-a high-speed prime motor for driving in high speed range and a low-speed prime motor for driving in low speed range.
  • the other is the type having only one prime motor such as variable speed prime motor such as DC. electric motor, multi-pole induction motor or hydraulic motor.
  • the conventional driving device is suited for driving the centrifugal separator only in so far as its ability ti drive the separating basket at two different rotating speeds in as concerned, but in designing the conventional driving device, no due consideration is given to the below-mentioned operating conditions peculiar to the centrifugal separator and therefore, the design fails to give adequate performance.
  • the centrifugal separator needs to be operated in various torque and at various rotating speeds responsive to the moisture, viscosity of the fluid materials to be treated and quantity to be treated; but the conventional centrifugal separator does not satisfy such operating conditions.
  • the conventional driving device for the centrifugal separator is equipped with a prime motor which is ordinarily an induction electric motor having constant rotating speed, D.C. electric motor having variable speed characteristics, or multi-pole induction electric motor having step speed characteristics, but even if these prime motor could vary its speed, its output torque cannot be freely varied, and accordingly, the conventional driving device, which transmits the rotation of the prime motor directly to the basket, can not be well adapted for the afore-mentioned unique operating conditions of the centrifugal separator. Therefore, such conventional driving device of the centrifugal separator drives the basket with excessive torque in some cases, and with less excessive torque in other cases. This applies excessive load to the prime motor and its transmitting mechanism, and it is also difficult to operate the device as desired.
  • an object of the present invention to provide an improved driving device for a rotary chemical machine, which may be freely preset to the operating conditions of the machine.
  • a driving device for a rotary chemical machine such as a centrifugal separator which may provide a low torque high speed operation for separating liquid from slurry and a high torque low speed operation for discharging solid material out of the basketwith one prime motor.
  • a driving device for a rotary chemical machine having a rotary basket, normally and reversely rotatable, and a rotary shaft affixed to the rotary basket, which comprises a reversible prime motor having a cylindrical hollow input shaft driven thereby, an output shaft secured to said rotary shaft, a rotary casing rotatably mounted around said output shaft, a first one-way clutch interposed between the input shaft of said prime motor and said rotary casing for coupling the input-shaft of said prime motor to said rotary casing when the input shaft rotates in one direction, a second one-way clutch interposed between the input shaft of said prime motor and said output shaft for coupling the input shaft to said output shaft when the input shaft rotates in the other direction,.a reduction gear mechanism contained in said rotary casing and having a first sun gear integrally formed on said output shaft, a sleeve shaft rotatably mounted on the said output shaft coaxially adjacent to the sun
  • Another aspect of the driving device for the rotary chemical machine is attained by the provision of means for slidably alternating the operating position of said braking elements of said torque control mechanism.
  • very broad range of torque may be provided by displacing the position of the braking elements as they engage the non-restricting element at the output shaft of the driving device.
  • a driving device for the rotary chemical machine which comprises an electric braking 'mechanism instead of the previously described mechanical braking mechanism.
  • a driving device for the rotary chemical machine having a rotary basket normally and reversely rotatable and a rotary shaft affixed to the rotary basket, which comprises a reversible prime motor having an input shaft driven thereby, an
  • a driving device for the rotary chemical machine having a rotary basket and a rotary shaft secured thereto which comprises a reversible prime motor having a first high speed input shaft driven thereby and second low speed input shaft driven thereby, an output shaft secured to said rotary shaft which is connected to the same reduction gear mechanism as described in the immediately preceding paragraph, ie, the rotary casing containingthe embodiment mechanism and the output shaft for disengaging the coupling of the gear mechanism to the output shaft only when the first high speed driven timing wheel is coupled with the output shaft by the first one-way.
  • the third one-way clutch being mounted between the second low speed driven timing wheel and the planetary gear mechanism for coupling the second low speed driven timing wheel with'the planetary gear mechanism only when the second driven timing wheel is rotated in one direction, a torque control mechanism having a non-restricting element formed on the rotary casing as an extension of one wall thereof for rotation thereforth, and at least one pair of braking elements movable relative to each other toward or away from both surfaces of said non-restricting element.
  • FIG. I is a schematic view of one embodiment of a driving device for a rotary chemical machine according to the present invention.
  • FIGS. 2 to 4 are enlarged sectional views of the driving device for the rotary chemical machine constructed in detail of the device in FIG. 1;
  • FIG. 5 is a schematic view of another embodiment of the driving device for the rotary chemical machine constructed according to the present invention.
  • FIG. 6 is a partial sectional view of the driving device constructed in detail of the device in FIG. 5;
  • FIG. 7 is a schematic view of still another embodiment of the driving device for the rotary chemical machine of the present invention.
  • FIG. 1 schematically shows the entire structure of one embodiment of 'a centrifugal separator with abasket having a driving device constructed according to the present invention.
  • This separator has a basket 2 fixed to the lower end of a vertically extended rotary shaft 1 and rotatable together as generally well known.
  • the upper end of the rotary shaft 1 is rotatably supported by bearings 5 within a bearing box 4 fixed to a frame 3, and is connected to the lower end of an output shaft 7 through a coupling 6 so that the vibration of the basket 2 may not be transmitted thereto.
  • a driving device generally designated by numeral 8, comprises a reduction gear mechanism, generally designated by numeral 9, and a torque control mechanism 10, and is connected to only one reversible prime motor M such as, for example, an ordinary electric induction motor through a pair of clutches 11 and 12 and a starter compensating mechanism 13.
  • the driving device 8 comprises a rotary casing 14 which contains the reduction gear mechanism 9 such as a planetary gear mechanism and which is rotatably mounted around the output shaft 7 having the shaft coupling 6 at one end thereof.
  • the reduction gear mechanism 9 such as a planetary gear mechanism
  • the torque control mechanism 10 is for the purpose of imparting a desired torque to the output shaft 7 and comprises a control mechanism including a nonrestricting element for restricting part of the driving device 8 such as, for example, a brake disc 15.
  • the starter compensating mechanism 13 is for the purpose of preventing an overload from being applied to the electric motor M when starting the motor M, and may be, for example, a centrifugal clutch or any well known fluid clutch.
  • numeralrl6 denotes a cylindrical hollow input shaft driven through the starter compensating mechanism (not shown for clarity in depicting the invention in these figures) by the reversable motor M and connected through a pair of one-way clutches 11 and 12 to a rotary casing 14 and the output shaft 7.
  • the one-way clutch ll interposed between the input shaft 16 and the rotary casing 14 couples the input shaft 16 to the rotary casing 14 when the input shaft 16 rotates in one direction
  • the one-way clutch 12 disposed between the input shaft 16 and the output shaft 7 couples the input shaft 16 to the output shaft 7 when the input shaft 16 rotates in the other direction.
  • the output shaft 7 is formed integrally with a sun gear 17 forming part of the gear mechanism within the rotary casing 14, and is supported by bearings 18 within the rotary casing 14 so as to be freely rotatable with respect to the rotary casing 14.
  • a sleeve shaft 20 formed integrally with a sun gear 19 coaxially adjacent to the sun gear 17 is rotatable through needle bearings 21 on the output shaft 7, and one end of the sleeve shaft 20 projects externally from the rotary casing 14, and part of the torque control mechanism such as, for example, the brake disc is affixed to the flange 22 formed at the projecting end.
  • planetary idle gears 23 and 24 rotatably mounted on a stub shaft 25 and engaged with the sun gear 17 and the sun gear 19 respectively, within the rotary casing 14, and both ends of the stub shaft 25 are rotatably supported at the upper and lower end portions through needle bearings 26 provided within the rotary casing 14.
  • the planetary idle gear 24 cannot rotate with the result that the stub shaft 25 may not accordingly rotate about its own axis, but will rotate around the output shaft 7 integral with the rotary casing 14 and sleeve shaft 20. That is, the output shaft 7 may not be rotated in this mechanism unless the sleeve shaft 20 is not restricted.
  • the rotation of the rotary casing 14 rotates the stub shaft 25 around the output shaft 7 and simultaneously relatively rotates betweenthe sun gear 19 and the planetary idle gear 24, and thereby rotates the stub shaft 25 about its own axis.
  • the contrifugal separator is provided with a torque control mechanism for producing various amounts of torque at the output shaft 7 by varying the restricting force imparted to the sleeve shaft 20 responsive to the operating conditions of the centrifugal separator.
  • the torque control mechanism is arranged to engage the oppositely disposed surfaces of the control disc 15 and comprises several pairs of braking elements 27, 27 (one pair of braking elements being illustrated in FIGS. 2 and 3) which are movable relative to each other to control the rotation of disc 15.
  • the drive control device in particular has a dual-operated air cylinder 28, and a control device 29 therefore which controls the disc 15.
  • the control device 29 includes in the embodiment shown in FIG. 2, a solenoid valve 30 for controlling the quantity of air supplied to the air cylinder 28 and a circuit for controlling the opening of the solenoid valve 30.
  • the circuit includes an electric motor load detector 31 for detecting the amplitude of the load current of the electric motor M which is the input shaft 16.
  • the control 32 for operation of the braking elements 27, 27 is coordinated with a control calculator 33 which compares the value detected by the load detector 31 with a preset value established by the control to produce the output responsive thereto.
  • the control signal responsive to the preset values is imparted to the solenoid valve 30 which is then opened with the result that the braking elements 27, 27 are urged into contact with the brake disc with a predetermined pressure. Therefore, the braking torque which corresponds to the force applied to the braking elements 27 27 acts on the sleeve shaft 20, and the output shaft 7 is rotated by the torque corresponding to the preset value.
  • the solenoid valve 30 is controlled by the detected signal from the detector'31 with the result that the transmission of the excessive load to the electric motor M and to entire drive device is prevented.
  • FIG. 3 The alternative embodiment of a control device for controlling the torque applied to the output shaft 7 is shown in FIG. 3 and is broader thanthe device shown in FIG. 2.
  • the control device of FIG. 3 comprises a device for alternating the operating position of the braking element 27, 27.
  • This device includes an electric motor control 34, a screw shaft 35 directly coupled to the electric motor 34 and a slider 37 having a nut portion 36 threadable on the screw shaft 35, for movement of slider 37 positioned to slide on a stationary base 38 radially adjacent of the brake disc 15.
  • the electric motor control 34 is connected to the control calculator 33 of the control circuit, and is controlled by the signal therefrom.
  • FIG. 4 shows still another embodiment of the control device for controlling the torque applied to the output shaft of this invention.
  • the device of this embodiment comprises an electric braking mechanism instead of the mechanical braking mechanism designated in FIGS. 2 and 3 in order to avoid the wear of the braking element and to reduce the necessity of service and maintenance thereof.
  • This braking concept comprises an eddy current mechanism generally called eddy current retarder, and includes a pair of electromagnetic poles 39, 39 which are disposed opposite sides of the brake disc 15.
  • the poles 39, 39 are connected to the control calculator 33 of the control circuit in a manner similar to the solenoid 30 previously described and is controlled by the output signal value of the control calculator 33.
  • an eddy current is generated on the brake disc 15 by means of a magnetic flux generated by the poles 39, 39 and accordingly, a reaction torque is applied to the brake disc 15 with the result that the disc 15 is braked.
  • the braking force is proportional to the amplitude of the eddy current, i.e., the strength of the magnetic flux density generated by the poles 39, 39, the strength ofthe torque applied to the output shaft 8 may be varied responsive to the amplitude of the control signal for energizing the poles 39, 39.
  • FIG. 5 is a schematic illustration of another embodiment of this invention for a basket type centrifugal separator
  • the driving device 8 comprises a driven timing wheel 40, which is driven by a reversible electric motor M provided on the frame 3 through a drive timing wheel 41 and a belt 42.
  • the driving device 8 is substantially the same as those shown in FIGS. 2 to 4, but is varied as best seen in detail in FIG. 6, the description of which follows later.
  • Thedriving device 8 comprises a rotary casing 14 similar to the driving device designated in FIGS. 2 to 4, but is constructed somewhat differently. These ring gears 45 and 46 form a planetary gear mechanism 9, together with a pair of planetary gears which will be hereinafter described in greater detail.
  • the lower end of an output shaft 7 in the center of the rotary casing 14 is relatively rotatably supported with respect to the rotary casing 14 by a thrust bearing 47 provided at the lower end of the rotary casing 14, whilethe other end projects outwardly of the upper end of the casing l4'and is connected to the main shaft 1 of the basket by means of the shaft coupling 6 shown in FIG. 5.
  • the reduction gear shaft 50 has an arm 52 extending radially from one end thereof and a sun gear (hereinafter called the second sun-gear) coaxially with the shaft 50-at the other end. Secured to the arm 56 is one end of a stub shaft 54 having an axis parallel with the input sleeve shaft 16 and output shaft 7, and
  • a first planetary gear 56 rotatably supported by bearings 55.
  • the first planetary gear meshes with a planetary sun-gear 57 provided on the input sleeve shaft 16 and also with the first ring-gear 45 provided on the inner wall of the rotary casing 14.
  • An arm 58 extends radially of the shaft '7 in the vicinity of the bearing 47 and is provided with a second short stub shaft 59 aligned on the same axis as the first stub shaft 54 and provided with aone-way clutch 60 and a second planetary gear 61 which meshes with the second planetary ring-gear 46 on rotary casing 14 and with the second sun-gear 53.
  • This one-way clutch 60 couples the second planetary gear 61 with the second short stub shaft 59 when the input sleeve shaft 16 is rotated as designated by arrow A which rotates the second planetary gear 61 oppositely to the direction designated by the arrow A, while the one-way clutch 60 disengages the second planetary gear 61 from the second short stub shaft 59 when the input shaft 16 is rotated oppositely to the direction as illustrated by the arrow A, which, of course, rotates the second planetary gear 61 in the direction illustrated by the arrow A.
  • the one-way clutch 60 couples the second planetary gear 61 with the second short stub shaft 59, and neither of the brake discs 15 are restricted by the braking elements 27, 27.
  • the second planetary gear 61 is restricted so as not to rotate around its own axis, i.e., about the second short stub shaft 59. Since relative rotation of the second planetary gear 61 is stopped, the second ring gear 46 and second sun gear 53 on the reduction gear shaft 50 is held in unison with the output shaft 7, and is then stopped.
  • the first planetary gear 56 meshed with the first sun gear 57 tends to transmit rotary torque opposite to the rotation of the first sun gear 57.
  • the first ring gear 45 meshes with the first planetary gear 56 and rotary casing 14 is held in unison by the second planetary gear 61 the action of the clutch 60, at this time, the above rotary torque may not rotate the first planetary gear 56 about the first short stub shaft 54 and accordingly the rotation of the input sleeve shaft 16 is transmitted directly to the rotary casing 14' held in unison with the output shaft 7.
  • the output shaft 7 and rotary casing 14 are rotated directly together with the input sleeve shaft 16 in the state integration with the input shaft 16 and accordingly the output shaft 7 is rotated in the direction as designated by an arrow A. Consequently, the main shaft 1 of the basket directly coupled with the output shaft 7 is rotated in low torque at high speed for separating the solids from the liquid.
  • the driving device is switched to rotation in at a high torque at low speed for discharging the muddy substance out of the basket by a command from the control device (not shown).
  • This high torque and low speed operation is executed as follows:
  • the electric motor M is switched to reverse drive in FIG. 5 by a drive command from the control device (not shown) and simultaneously the solenoid valve 30 for operating the braking elements, is opened in a preset degree with the result that the braking elements 27, 27 are urged onto the brake discs 15, by a predetermined pressure, and thereby the rotation of the rotary casing 14 is restricted.
  • the first planetary gear 56 may not rotate the rotary casing 14 depending on the amount of'restriction as restricting element 15, 15 but, on the contrary, the first planetary gear 56 is rotated clockwise around the output shaft 7 meshing with the first ring gear 45 fixed to the casing 14 and accordingly in the direction as illustrated by the arrow B with the result that the arm 52 of the reduction gear shaft 50 supporting the first planetary gear 56 is rotated clockwise around the output shaft 7.
  • the second sun gear 53 on gear shaft 50 is also rotated clockwise and rotary torque in the direction as designated by an arrow A for rotating the second planetary gear 61 about the second short stub shaft 59 is transmitted to the second planetary gear 61 meshed with the second sun gear 53.
  • the oneway clutch 60 is disengaged by this torque, and accordingly, the second planetary gear 61 is not coupled to the second short stub shaft 59, but is freely rotated about the second short shaft 59 by the second sun gear 53.
  • This rotation of thesecond planetary gear 61 is converted to the torque for rotating or tending to rotate the rotary casing 14 in the direction as designated by the arrow A through the second ring gear 46.
  • the rotary casing 14 is restricted by the braking elements 27, 27 as aforementioned, the rotary casing 14 is not rotated or is rotated slowly depending on the amount of restriction by brakes 27, 27 but, on the contrary, the second planetary gear 61 is rotated in the direction as illustrated by the arrow B around the second ring gear 46. As a result, the arm 58 supporting the second planetary gear 61 and output shaft 7 are rotated in the direction as illustrated by the arrow B.
  • FIG. 7 shows still another embodiment of the driving device for the centrifugal separator of this invention having similar functions as those of the embodiments shown in FIGS. 1 to 6, in which the driving device 8 includes three one-way clutches 62,63, and 64.
  • This driving device 8 comprises a rotary casing 14 similar to the driving device shown in FIG. 6 and containing a planetary gear mechanism 9, the detail of which is omitted in FIG. 7, within the rotary casing 14.
  • This planetary gear mechanism 9 is connected through the three one-way clutches 62, 63 and 64 to. the output shaft 7, high speed driven timing wheel 65, and low speed input shaft 66.
  • a low speed driven timing wheel 67 is mounted on the low speed input shaft 66, and is connected to drive timing wheels 69 and 70 on a drive shaft 68 directly coupled with the reversible electric motor M together with the high speed driven timing wheel 65 through V belts 71 and 72, respectively.
  • the one-way clutch 62 for coupling the driven timing wheel 65 with the output shaft 7 is mounted between the high speed driven timing wheel 65 and the output shaft 7 only when the driven timing wheel 65 is rotated in one direction such as, for example, in the direction designated by the arrow A, and the one-way clutch 64 for coupling the low speed driven timing wheel 67 with the planetary gear mechanism 9 between the low speed driven timing wheel 67 and the planetary gear mechanism 9 only when the driven timing wheel 67 is rotated in one direction such as, for example, in the direction illustrated by an arrow A.
  • another one-way clutch 63 is interposed between the planetary gear mechanism 9 and the output shaft 7, and disengages the-connection of the planetary gear mechanism 9 to the output shaft 7 only when the high speed driven timing wheel 65 is coupled with the output shaft 7 by the one-way clutch 62.
  • the rotary casing 14 is connected to the torque control mechanism for imparting a desired torque to the output shaft 7 by restricting the braking elements 15, such as brake discs mounted to the casing 14 similar to the embodiment shown in FIG. 6. Since this torque control mechanism is entirely the same as that shown in FIGS. 2 and 3, the details are omitted.
  • liquid suspension material such as mud is poured into the basket 2 in the device shown in FIG. 7, and the separator is rotated so as to separate the liquid from the material.
  • the drive electric motor M rotates the drive timing wheel 69 in the direction designated by the arrow A so that the rotation of the drive timing wheel 69 rotates the high speed driven timing wheel 65 in the direction illustrated by an arrow A through the V belt 71.
  • the one way clutch 62 interposed between the high speed driven timing wheel 65 and the output shaft 7 couples the timingwheel 65 with the output shaft 7, while the one-way clutch 63 interposed between the planetary gear mechanism 9 and the output shaft 7 disengages the connection of the output shaft 7 to the planetary gear mechanism 9.
  • the one-way clutch 64 interposed between the low speed input shaft 66 andthe planetary gear mechanism 9 is not operated and accordingly the low speed input shaft 66 is not connected to the planetary gear mechanism 9 and consequently the low speed input shaft 66 is idled with respect to the planetary gear mechanism 9.
  • the output shaft 7 is rotated at high speed from the high speed driven timing, wheel 65 directly, and the basket 2 for the separator is also rotated at high speed in the direction as designated by an arrow A.
  • the drive electric Motor M is reversely driven by the command from the control device (not shown), and at the same time, the braking element l5, 15 is restricted by the torque control mechanism 10 with a predetermined force by the command from the control device.
  • the high speed driven timing wheel 65 is oppositely driven to the direction as described above, that is opposite to the direction designated by the arrow A, and thereby the clutch 62 is disengaged so that the driven timing wheel 65 is idled about the output shaft 7.
  • the input shaft 66 is also rotated in the same direction with the result that the input shaft 66 and the planetary gear mechanism 9 are coupled by the one-way clutch 64.
  • the rotation transmitted through the one-way clutch 64 to the planetary gear mechanism 9 operates the one-way clutch 63 with the result that the planetary gear mechanism 9 and the output shaft 7 are coupled with each other by the one-way clutch 63.
  • the planetary gear mechanism 9 tends to rotate the rotary casing 14 since the rotary casing 14 is restricted by the torque control mechanism 10 through the braking element 15, the rotary casing 14 is not rotated or is rotated very little depending upon the amount of restriction by the braking elements 27, 27 but the planetary gear mechanism 9 is rotated around the output shaft 7 within the rotary casing l4.similar to the case of the device shown in FIG. 6. As-a result, since the one-way clutch 63 is rotated around the output shaft 7 opposite to the direction as designated by the arrow A, the one-way clutch 63 is operated so that the planetary gear mechanism 9 and the output shaft 7 are coupled together. Thus, the low speed rotation transmitted to the input shaft 66 is further reduced through the planetary gear mechanism 9 and. is transmitted to the output shaft 7 so as to rotate the output shaft 7 at low speed in high torque/In this case, as
  • the present invention provides a driving device for rotary chemical machine such as centrifugal separator, which improves the conventional machine which could not heretofore be operated at optimum for the operating conditions so as to enable the machine to operate at optimum levels according to the operating conditions of the machine.
  • variable torque operation is applied only in low speed operation of the device of the embodiment of the present invention, but this variable torque operation may also be applied to high speed operation within the spirit of the present invention.
  • a driving device for a rotary chemical machine having a normally and reversely rotatable rotary basket and a rotary shaft affixed to the rotary basket comprising a reversible prime motor having a cylindrical hollow input shaft driven thereby, an output shaft secured to said rotary shaft, a rotary casing rotatably mounted around said output shaft, a first unidirectional clutch interposed between the input shaft of said prime motor and said rotary casing for coupling the input shaft of said prime motor to said rotary casing when the input shaft rotates in one direction, a second unidirectional clutch interposed between the input shaft of said prime motor and said output shaft secured through the rotary shaft to said rotary basket for coupling the input shaft to said output shaft when the input shaft rotates in the other direction, a reduction gear mechanism contained in said rotary casing and having a first sun gear integrally formed on said output shaft, a sleeve shaft rotatably mounted on said output shaft coaxially adjacent to the sun gear and having a second sun gear integrally formed there
  • a driving device further comprising means for alternating slidably the operating position of said braking elements of said torque control mechanism and having a control electric motor, a screw shaft directly coupled to said control electric motor and a slider having a nut portion threaded on the screw shaft and so placed as to slide on a stationary base radially of said braking elements.
  • said braking mechanism is an eddy current braking mechanism which comprises a pair of electromagnetic poles disposed on opposite surfaces of the brake element, and a control calculator connected to said poles for controlling the electromagnetic poles.
  • a driving device for the rotary chemical machine having a rotary basket normally and reversely rotatable and a rotary shaft affixed to the rotary basket, comprising a reversible prime motor having an input shaft driven thereby, an output shaft secured to said rotary shaft and having a first arm radially projected therefrom, a rotary casing rotatably mounted around said output shaft, a driving timing wheel driven by the reversible prime motor through a belt with a driven timing wheel mounted on the output shaft, a reduction gear mechanism contained in said rotary casing and having a first sun gear integrally formed on said driven timing wheel, a sleeve shaft rotatably mounted on said output shaft coaxially adjacent to the sun gear and having a second arm radially projected therefrom and a second sun gear integrally formed thereon, a first stub shaft so mounted around said output shaft so as to be rotatable about its own axis and also around said output shaft within said rotary casing in such a manner that the second arm of sle
  • a torque control mechanism having a non-restricting element on the rotary casing, at least one pair of braking elements movable relative to each other toward or away from both side surfaces of said non-restricting element.
  • the driving device further comprising means for alternating slidably the operating position of said braking elements of said torque control mechanism and having a control electric motor, a screw shaft directly coupled to said control electric motor and aslider having a nut portion threaded on the screw shaft and so placed as to slide on a stationary base radially of said braking elements.
  • said braking mechanism is an eddy current braking mechanism which comprises a pair of electromagnetic poles disposed on opposite surfaces of the brake element and a control calculator connected to said poles for controlling the electromagnetic poles.
  • a driving device for the rotary chemical machine having a rotary basket normally and reversely rotatable and a rotary shaft affixed to the rotary basket, comprising a reversible prime motor having a first high speed input shaft driven thereby and second low speed input driven thereby, an output shaft secured to said rotary shaft and having a first arm radially projected therefrom, a rotary casing rotatably mounted around said output shaft, a first driving timing wheel driven by the reversible prime motor through a first belt with a first high speed driven timing wheel mounted on the output shaft and a second driving timing wheel driven by the reversible prime motor through a second belt with a second low speed driven timing wheel mounted on the second low speed input shaft, a reduction gear mechanism contained in said rotary casing and having a first sun gear integrally formed on said first driven timing wheel, a sleeve shaft rotatably mounted on said output shaft coaxially adjacent to the sun gear and having a second arm radially projected therefrom and a second sun gear integrally
  • the driving device further comprising means for alternating slidably the operating position of said braking elements of said torque control mechanism and having a control electric motor, a screw shaft directly coupled to said control electric motor and a slider having a nut portion threaded on the screw shaft and so placed as to slide on a stationary base radially of said braking elements.
  • said braking mechanism is an eddy current braking mechanism which comprises a pair of electromagnetic poles disposedon opposite surfaces of the brake element and a control calculator connected to said poles for controlling the electromagnetic poles.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Centrifugal Separators (AREA)
  • Retarders (AREA)
  • Braking Arrangements (AREA)
  • Transmission Devices (AREA)
US00383180A 1972-07-28 1973-07-27 Driving device for rotary chemical machine Expired - Lifetime US3851819A (en)

Applications Claiming Priority (1)

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JP47075596A JPS5013977B2 (de) 1972-07-28 1972-07-28

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US (1) US3851819A (de)
JP (1) JPS5013977B2 (de)
CH (1) CH566816A5 (de)
DE (1) DE2337600A1 (de)
GB (1) GB1435185A (de)
SE (1) SE396298B (de)
SU (1) SU561495A3 (de)

Cited By (13)

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US4141488A (en) * 1977-08-18 1979-02-27 Koninklijke Nederlandse Papierfabrieken N.W. Centrifuge
US4522620A (en) * 1982-11-11 1985-06-11 Deutsche Gesellschaft Method and apparatus for measuring the quantity of solid material in a centrifuge cylinder
US5454777A (en) * 1994-10-05 1995-10-03 Glassline Corporation Centrifugal separator apparatus with load sensing circuit for optimizing clearing cycle frequency
US5456653A (en) * 1994-07-07 1995-10-10 Beckman Instruments, Inc. Torsionally elastic assembly for driving a centrifuge rotor
US5714858A (en) * 1995-03-24 1998-02-03 Nuova M.A.I.P. Macchine Agricole Industriali Pieralisi S.P.A. Device for controlling and regulating the relative speed between rotary components interacting with one another respectively connected to the rotor and stator of an electric motor
US5948271A (en) * 1995-12-01 1999-09-07 Baker Hughes Incorporated Method and apparatus for controlling and monitoring continuous feed centrifuge
US6149573A (en) * 1996-09-05 2000-11-21 Balcon, Inc. Centrifugal separator having a clutch assembly
US6461286B1 (en) * 1998-06-03 2002-10-08 Jeffery N. Beattey Method of determining a centrifuge performance characteristic or characteristics by load measurement
US6478724B1 (en) * 1998-06-03 2002-11-12 Jeffery N. Beattey Centrifuge with clutch mechanism for synchronous blade and bowl rotation
US6997860B2 (en) * 2003-08-18 2006-02-14 Glassline Corporation Single drive centrifugal separator
CN105889468A (zh) * 2015-02-10 2016-08-24 申克罗泰克有限责任公司 用于离心机试验台的驱动装置
US20170314352A1 (en) * 2016-04-29 2017-11-02 Kemtron Technologies LLC d/b/a Elgin Separation Solutions Vertical cuttings dryer
US11098622B2 (en) * 2016-02-01 2021-08-24 3Nine Ab Oil separator

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JPS567049Y2 (de) * 1976-11-26 1981-02-16
JPS5593172A (en) * 1978-12-30 1980-07-15 Ricoh Co Ltd Rotation control unit
JPH0231033U (de) * 1988-08-19 1990-02-27
GB2238090A (en) * 1989-10-16 1991-05-22 John Harries Power transmission system comprising two sets of epicyclic gears
CN105937568A (zh) * 2016-06-30 2016-09-14 重庆浩立塑胶有限公司 分卷制动结构
CN112709790A (zh) * 2020-12-23 2021-04-27 苏州绿控传动科技股份有限公司 一种行星排电驱动合力装置

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US2129992A (en) * 1937-04-09 1938-09-13 Mattia Anthony De Centrifugal separator
US2822127A (en) * 1952-09-30 1958-02-04 Basf Ag Continuous centrifuge
US3480207A (en) * 1966-06-15 1969-11-25 Karl Strohmaier Centrifuge with efficiency measuring device

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US2129992A (en) * 1937-04-09 1938-09-13 Mattia Anthony De Centrifugal separator
US2822127A (en) * 1952-09-30 1958-02-04 Basf Ag Continuous centrifuge
US3480207A (en) * 1966-06-15 1969-11-25 Karl Strohmaier Centrifuge with efficiency measuring device

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4141488A (en) * 1977-08-18 1979-02-27 Koninklijke Nederlandse Papierfabrieken N.W. Centrifuge
US4522620A (en) * 1982-11-11 1985-06-11 Deutsche Gesellschaft Method and apparatus for measuring the quantity of solid material in a centrifuge cylinder
US5456653A (en) * 1994-07-07 1995-10-10 Beckman Instruments, Inc. Torsionally elastic assembly for driving a centrifuge rotor
US5454777A (en) * 1994-10-05 1995-10-03 Glassline Corporation Centrifugal separator apparatus with load sensing circuit for optimizing clearing cycle frequency
US5512031A (en) * 1994-10-05 1996-04-30 Glassline Corporation Method of centrifugal separation with load sensing circuit for optimizing cleaning cycle frequency
US5714858A (en) * 1995-03-24 1998-02-03 Nuova M.A.I.P. Macchine Agricole Industriali Pieralisi S.P.A. Device for controlling and regulating the relative speed between rotary components interacting with one another respectively connected to the rotor and stator of an electric motor
US5948271A (en) * 1995-12-01 1999-09-07 Baker Hughes Incorporated Method and apparatus for controlling and monitoring continuous feed centrifuge
US6143183A (en) * 1995-12-01 2000-11-07 Baker Hughes Incorporated Method and apparatus for controlling and monitoring continuous feed centrifuge
US6149573A (en) * 1996-09-05 2000-11-21 Balcon, Inc. Centrifugal separator having a clutch assembly
US6478724B1 (en) * 1998-06-03 2002-11-12 Jeffery N. Beattey Centrifuge with clutch mechanism for synchronous blade and bowl rotation
US20060264312A1 (en) * 1998-06-03 2006-11-23 Beattey Jeffery N Centrifuge with clutch mechanism for synchronous blade and bowl rotation
US20030017931A1 (en) * 1998-06-03 2003-01-23 Beattey Jeffery N. Centrifuge blade design
US20050003945A1 (en) * 1998-06-03 2005-01-06 Beattey Jeffery N. Centrifuge with a variable frequency drive and a single motor
US6932757B2 (en) 1998-06-03 2005-08-23 Jeffery N. Beattey Centrifuge with a variable frequency drive and a single motor and clutch mechanism
US6461286B1 (en) * 1998-06-03 2002-10-08 Jeffery N. Beattey Method of determining a centrifuge performance characteristic or characteristics by load measurement
US7044904B2 (en) * 1998-06-03 2006-05-16 Beattey Jeffery N Centrifuge with clutch mechanism for synchronous blade and bowl rotation
US6997860B2 (en) * 2003-08-18 2006-02-14 Glassline Corporation Single drive centrifugal separator
CN105889468A (zh) * 2015-02-10 2016-08-24 申克罗泰克有限责任公司 用于离心机试验台的驱动装置
US10088033B2 (en) 2015-02-10 2018-10-02 Schenck Rotec Gmbh Drive mechanism for a spin test rig
CN105889468B (zh) * 2015-02-10 2019-11-19 申克罗泰克有限责任公司 用于离心机试验台的驱动装置
US11098622B2 (en) * 2016-02-01 2021-08-24 3Nine Ab Oil separator
US20170314352A1 (en) * 2016-04-29 2017-11-02 Kemtron Technologies LLC d/b/a Elgin Separation Solutions Vertical cuttings dryer
US10865611B2 (en) * 2016-04-29 2020-12-15 Elgin Separation Solutions Industrials, Llc Vertical cuttings dryer

Also Published As

Publication number Publication date
GB1435185A (en) 1976-05-12
JPS4933263A (de) 1974-03-27
JPS5013977B2 (de) 1975-05-23
SU561495A3 (ru) 1977-06-05
CH566816A5 (de) 1975-09-30
SE396298B (sv) 1977-09-19
DE2337600A1 (de) 1974-02-21

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