US2441356A - Driving system for centrifugals or the like - Google Patents

Driving system for centrifugals or the like Download PDF

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Publication number
US2441356A
US2441356A US435023A US43502342A US2441356A US 2441356 A US2441356 A US 2441356A US 435023 A US435023 A US 435023A US 43502342 A US43502342 A US 43502342A US 2441356 A US2441356 A US 2441356A
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Prior art keywords
oil
coupling
motor
torque
pressure
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US435023A
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English (en)
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Hertrich Joseph
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Western States Machine Co
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Western States Machine Co
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Priority to US435023A priority patent/US2441356A/en
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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
    • B04B9/08—Arrangement or disposition of transmission gearing ; Couplings; Brakes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S60/00—Power plants
    • Y10S60/912—Cooling means

Definitions

  • I also propose to provide such a system which will enable the accelerating torque of the machine to be selected and set at any of a wide range of values, thereby enabling the same machines to be used withdii'ierent acceleration rates for the most eillcient treatment of different types of material.
  • Another object of my invention is to provide a new driving system for centrifugal machines or the like which automatically limits the torque transmission to a* predetermined value during operating periods of excessive torque demand, by allowing the necessary slip between the driving and driven members of the machine, yet which automatically minimizes the slip and so gives the most efficient power transmission within the capacity of the system whenever the torque demand is below the limiting value, as when-the machine has been accelerated to its full running speed.
  • a further objectof my invention is to provide a driving system for sugar centrifugals or the like which places two or more independently operable machines under a common torque control and makes it possible to keep the several machines operating with identical accelerating characteristics.
  • a hydraulic clutch or coupling is employed for transmitting a limited but variable torque between a driving motor and the driven machine; and a variable control means is provided which responds automatically to the torque being delivered at any moment by the motor and which controls the torque transmitted to the machine through the coupling, hence the torque of the motor, by varying the quantity of liquid in the coupling.
  • oil is circulated through the coupling during its operation, and the torque varied by varying the rate of oil circulation.
  • the oil supply system for the coupling may be provided with a variable control valve for regulating the rate of oil inflow, and the coupling itself may have an oil discharge means, such as one or more bleeder holes, through which oil may escape at a more or less constant rate.
  • the control valve will change the oil inflow rate and in that way in crease or reduce the quantity of oil in the coupling, which of course will increase or reduce the torque of the coupling for any given arrangement and degree of slip between the coupling members.
  • With a suitable rate of discharge the oil will prevent the coupling becoming overheated, and the oil that is discharged may be cooled and recirculated through the corn trol valve and back into the coupling.
  • Such a control valve is made operative to control the torque of the coupling, according to my invention, by utilizing the fact that the stator of the driving motor is aimays subject to a torque reaction that is equal to the torque of the motor, though oppositely directed.
  • the motor frame holding the stator and likewise the base plate and other structure which support the motor are subject to the same torque reaction.
  • a control means quickly reactive to the torque of the driving motor may be completed pursuant hereto by providing for a limited shifting or turning movement of the stator or the motor frame, or even of structure to which the motor is fastened, if desired; by associating the shiftable motor frame with the variable control valve in the oil supply system of the hydraulic coupling, so that movement of the motor in reaction to its own torque may cause a reduction in the torque of the coupling; and by opposing such movement of the motor and control valve by spring means or fluid under pressure.
  • the spring means or fluid pressure then urges the control valve and the motor frame toward a position to increase the quantity of oil in the coupling, and the torque reaction of the motor acts in the opposite direction and urges the motor frame and control valve toward a position to reduce the quantity of oil in the coupling.
  • the torque that can be applied by the driving system therefore becomes a direct function of the spring or fluid pressure, and the value of that torque may be changed by changing the spring or its compression, or by changing the fluid pressure.
  • the spring or fluid pressure is selected so as to provide that desired accelerating torque for the machine, within the capacity of the driving motor and the hydraulic coupling, which results in a uniform selected acceleration and at the same time protects the motor against overloads or overheating during acceleration and other periods of excessive torque demand.
  • the hydraulic coupling will receive more oil and deliver its maximum power with a minimum loss of energy through slippage and heat.
  • a torque control system for a group of machines is obtained according to this invention by providing each machine with a system of the type described, in which fluid pressure determines the limiting torque, and by supplying the fluid pressure for every machine of the group from a common source, so that the accelerating characteristics of each machine are fixed by a force which is the same for every other machine.
  • hydraulic pressure is used for this purpose and is supplied from an oil circulation system that also is used to supply 011 for the hydraulic couplings of the several machines.
  • Figure l is a front elevation, partly in section and partly diagrammatic, of a suspended gyratory centrifugal machine embodying this invention
  • Figure 2 is a horizontal section, substantially along line 2-2 of Figure 1;
  • 'Eigure 3 is an enlarged vertical section showing parts of the hydraulic coupling oi the machine in Figure 1;
  • Figure 4 is a horizontal section, substantially along line fl4 of Figure 1;
  • Figure 5 is a fragmentary vertical section, substantially along line 5-li of Figure 4.
  • Figure 6 is a vertical section, substantially along line 8-45 of Figure 4.
  • FIG. 7 is a diagrammatic illustration of another embodiment of the invention.
  • Figure 8 is a diagrammatic illustration of a third embodiment of the invention, wherein it is applied for the control of a group of centrifugal machines.
  • FIG. 9 is a vertical section through a liquid control valve such as may be used in the embodiment of Figure 8.
  • FIG. 1 01 the drawings I have illustrated a preferred motor-driven centrifugal arrangement intended for use in the manufacture of sugar.
  • the machine includes the usual perforate basket l0 located inside a surrounding casing i2 and suspended by a spindle H from a syratory centrifugal head it.
  • a brake drum I1 is secured for rotation with the spindle and adapted to be engaged by friction brake bands Ila in any suitable manner.
  • the head it contains bearings and a, suitable ball and socket or universal Joint (not shown) which provides for the requisite gyratory or swinging movement of the basket and spindle under unbalanced loads during operation of the machine.
  • the weight of the basket and spindle assembly is sustained by a stationary motor shaft to a positive driving connection witha part 22 oi a flexible coupling (not iully shown) which in turn positively connects the shait 28 through the head II for rotation with the centriiugal spindle l4.
  • a stationary motor shaft to a positive driving connection witha part 22 oi a flexible coupling (not iully shown) which in turn positively connects the shait 28 through the head II for rotation with the centriiugal spindle l4.
  • This particular arrangement is not claimed as a ieature oi the present invention, but is claimed in my copending application, Serial No. 874,668, filed January 18, 1941; now United States Patent 2,380,595. It obviously may be varied in many respects within the purview oi the invention hereinclaimed, such as by using a solid shait motor and disposing the hydraulic coupling between the motor and the centriiugal' head, or otherwise.
  • the coupling has an oil supply system connected with an inlet pipe 36 that leads oil axially 6 I valve itselicontains a cylindrical plunger Cl which has two seats 82 and 44 controlling the admission oi oil to pipes 44 and II, respectively.
  • a compression spring ll bears at one end against an end piece 04 oi the valve body and at its other end against the end oi plunger ll, so tending to hold the plunger against seat 04 and to keep seat 22 open ior iull flow oi oil through a duct I0 and line '4 to the inlet 2
  • the plunger I has a stem I2 that extends through and is sealed to a flexible into the rotary coupling housing 28.
  • An oiitake pipe 4 il-takes oil iromthe bottom of a stationary oil collector 42 that surrounds'the coupling and is mounted on the upper end shield of the motor irame 22.
  • the peripheral '-'wall of housing 28 is provided with several small bleeder holes 44 which allow a continuous discharge oi oil during opera-' tion oi the coupling.
  • the bleeder holes 44 are made at least large enough to keep oil flowing from the coupling under centriiugal iorce at a rate suflicient to prevent overheating oi the oil.
  • the coupling By cooling this heated oil and recirculating it to the coupling the excess heat generated durin acceleration oi the centrliugal or other periods of high torque is readily disposed oi, and the coupling is kept operating at a. temperature conducive to eiiicient power transmission.
  • the oil from collector 42 may pass through pipe 40 to an oil tank 46, from which it may be withdrawn by a pump 48 and passed through an oil cooler 42 en route back to pipe 26 and the coupling.
  • the torque of the hydraulic coupling and the load on the motor, at any certain basket speed corresponding'to a certain degree oi slip between the impeller 32 and the runner 24, will vary with the quantity of oil inside the coupling, and also that the quantity oi oil inside the coupling may be controlled by varying the rate of oil supply through pipe 38.
  • the quantity of the liquid in the coupling at any given speed or degree of slip determines the accelerating power or torque transmitted to the basket of the machine and is controlled pursuant hereto so as to hold the acceleration characteristics constant in each cycle oi operation, yet permit variation oi the acceleration rate, at will, to suit theneeds oi the material being treated.
  • a three-way control valve 50 is provided at some convenient location adjacent the motor irame 22, such as by mounting it on the base plate 20. (See Figures 1, 2, 4 and 6.) Oil irom cooler in enters this valve through a pipe 52.
  • a second pipe 54 leads from the valve body II to a connection with the coupling inlet pipe 26.
  • a third pipe 56. leads irom the valve body back to the oil tank 48.
  • a passage II in the plunger equalizes the hydraulic pressure on the plunger and allows oil to pass irom the plunger into a duct 18 and thence into pipe it whenever the plunger is moved away irom seat 44.
  • an arm 22 is secured to the lower end shield of the motor irame 22 to extend radially to a position opposite the end oi stem I2, and a set screw s2 is threaded in arm so as to abut against the end oi stem 12.
  • the motor irame itseli is mounted ior limited angular movement in a manner hereaiter to be described. It will be apparent that when the motor irame moves to any appreciable extent'in a counterclockwise direction, as seen in Figure 4, such movement will be transplunger ill and will shift the plunger against the force oi spring 86 in a direction tending to close valve seat 62 and open valve seat 84.
  • the motor irame is mounted for limited angular movement in reaction to the torque oi the motor as iollows:
  • the adaptor plate 22b is made iast to the motor base plate 20 by means oibolts 84.
  • the motor is held down on the adaptor plate 22b by means of bolts 8' and compression springs 80.
  • These bolts extend through bolt holes 82 in the flanges 22a, as seen in Figure 4.
  • the holes ll are enlarged slightly say, about one-eighth oi an inch, to allow limited angular movement of the frame.
  • the adaptor plate 22 preierably is iormed withan open circular groove 82, and a circular row of ball bearings 94 is disposed in this groove to sustain the thrust oi the motor while reducing the frictional resistance to its angular motion.
  • a second radial arm 80a may be provided on the motor irame 22 diametrically opposite to arm 80 and arranged for co-action with a second valve body "it having a plunger 80a and a compression spring 66a therein.
  • This structure balances the a force opposing angular movement oi the motor centrifugal. the torque of the motor being in a clockwise direction as viewed in Figure 4.
  • the centrifugal has a heavy inertia to be overcome by the driving system, so that the motor torque immediately attains a value such that the correspending torque reaction on the stator 24 and the motor frame 22 becomes suflicient to shift the frame counterclockwise against the force of springs 88 and 86a.
  • the general arrangement and combination of parts is similar to the first embodiment, but fluid pressure is used inplace of spring pressure to control the accelerating torque of the'machine.
  • the oil-take pipe 40 from the oil collector 42 leads to an oil tank I46, and a pump I48 draws oil from the tank and passes it through a cooler I48 to a control valve I58.
  • the body of this valve houses a plunger I60 having two enlarged portions I'8I and I62 for closing or opening respective ducts I68 and I64.
  • An 011 line I65 leads from the cooler into a space IE6 at one end of the valve body, where the oil presses against an end of the plunger I80.
  • Duct I64 of the valve body connects with an oil line I88 leading to the coupling inlet 38.
  • Duct I63 connects with an oil line I10 leading back to the tank I48.
  • a pipe I12 is connected with the pressure line I85 to carry oil from the cooler I49 into space I5I of the valve body, but this pipe has a pressure relief valve I14 in it to ensure a definite predetermined pressure on the oil in line I48.
  • the relief valve I14 for example. may be set to be released at a pressure of thirty pounds per square inch.
  • a pipelli extends from pipe I12 back to the oil tank I48 and has a pressure relief valve I18 in it to ensure a substantially constant pressure on the oil entering the valve body.
  • the pressure maintained by valve I18 may be aboutten to twenty pounds per square inch.
  • the oil pump I48 feeds oil to the pressure line I88 and through the relief valve I14 in line I12 under pressure of, e. g., thirty pounds per square inch.
  • This pressure forces the plunger I80 in a direc tion giving a full oil supply through duct I84, line I88 and inlet 28 to the hydraulic coupling.
  • the torque reaction on the motor frame 221 suflicient to overcome the pressure of thirty pounds per square inch exerted on the end of plunger I80, the plunger is moved in a right-hand direction as seen in Figure 7, with the result'of reducing the flow of oil to the coupling and by-passing the excess oil through duct I82 and line I18 back to the tank I48.
  • the torque of the driving system during acceleration therefore will be maintained substantially constant at a value established by the setting of relief valve I14, and the torque may be varied by changing this value or its setting.
  • FIG. 8 of the drawings illustrates diagrammatically a third embodiment in which the invention is applied to maintain a uniform control over the torque characteristics of a group of centrifugal machines.
  • the oil inlet 28 for the hydraulic coupling of each machine receives oil through a control valve 288, which has a line 288 leading to the coupling inlet, an oil supply line.212, and a pressure line 285.
  • the off-take pipe 48 from the oil collector 42 of each machine is connected with a common header 248 which carries the oil discharged from the several couplings back to a common oil tank 248.
  • each control valve 250 houses a plunger 280 one end of which is subject to oIl pressure admitted through line 285, and the other end of which is associated with an arm 80 on the motor frame 22 in substantially the same manner as already described with respect to previous embodiments.
  • a duct 264 in each valve body communicates with the oil supply line 212 and is adapted to be closed-01f or opened. to regulate the flow through line 288'to the coupling, by the action of an enlargement 282 on plunger 260.
  • the several oil supply lines 212 stem from a common header 288.
  • the several pressure lines 265 stem from a common header 282.
  • a pump 248 forces oil from tank 246 through a cooler 249 and a pipe 28I into the pressure header 282.
  • a pipe 284 connects at one end with the oil supply header 288 and has two branches 288 and 288.
  • Branch 288 is connected with the pressure pipe 28I through a pressure relief valve 214.
  • Branch 288 extends back to the tank 248 through a pressure relief valve 218.
  • the setting of valve 214 therefore determines the torque-controlling pressure for thefour machines and the setting of valve 218 determines the pressure of the oil supply for the hydraulic couplings of the four machines. It will be-apparent that each machine of the group remains subject to operation independently of every other machine in the customary manner for sugar centrifugals, but also that the torque or accelerating characteristics of all four machines may be set at any desired value and maintained uniform in each and every operating cycle.
  • hydraulic coupling for transmitting that is reactive to its torque for limited angular 1 movement, and means connecting said part with comprising a driven shaft and rotary driving means including a motor and a hydraulic coupling, means connected with said motor and shiftable in one direction by the torque reaction of said motor, yieldable means to exert continuously a predetermined force tending to move said shiftable means in another direction in opposition to such torque reaction, and means operated by said shiftable means for varying and controlling the volume of fluid in said coupling.
  • a rotary machine having a driven shaft, a 'motor having a rotary driving shaft, a hydraulic coupling for transmittin power between the driving and driven shafts, and means continually subject to the torque reaction of the motor and shiftable in direct response thereto for limiting to a predetermined value the torque transmission of the coupling.
  • a heavy-duty machine comprising a rotary driven shaft, a rotary driving motor and a hydraulic coupling to transmit power from the motor shaft to the driven shaft, means for supplying liquid-into said coupling, means for discharging liquid from said coupling,-a control valve for varying the rate of liquid supply, means to apply continuously to said valve a predetermined force urging said valve toward open position, and means connected to said valve and to the motor and directly reactive to the torque of said motor to urge said valve toward closed position with a force always proportionate to said torque.
  • driving means having a rotary driving shaft and a hydraulic coupling to transmit torque between said shafts, means for circulating liquid into and out of said coupling including movable valve means outside the coupling for controlling the flow of liquid into the coupling, means urging said valve means yieldably toward a position to increase the quantity of liquid in the coupling, and means operated by a force equal at all times to the torque of said driving means for counteracting said last-recited means and moving said valve means toward a position to reduce the quantity of liquid in the coupling.
  • a plurality of machines each having a rotary driving motor, a rotary driven shaft, a hydraulic coupling to tralmmit power to the driven shaft from the motor, a motor frame mounted for limited turning movement in reaction to the motor torque, an oil supply line leading into the hydraulic coupling, a control valve in said line to vary the oil inflow to the coupling, means in the coupling for continuously discharging oil therefrom, means operated by such turning movement of said frame for moving said control valve to restrict said oil inflow and iiuid-pressure-responsive means for opposing turning movement of said frame and urging said control valve toward a position for full 011 inflow, an oil supply header common to said supply lines, an oil pressure header having branch lines leading to the respective fluid-pressure-responsive means, means connecting said supply header.
  • an ofl supply header common to said supply lines, an oil pressure header having branch lines leading to the respective fiuid-pressure-responsive means, means connecting said supply header with said pressure header, an oil tank and pump for forcing oil into said pressure header and said connecting means, a pressure relief valve in said connecting means to maintain a predetermined substantially uniform pressure in said pressure header and branch lines, an oil return line connecting said supply header with said oil tank, and a pressure relief valve in said return line to maintain a predetermined pressure on the oil in said supply header and said supply lines.
  • a heavy-duty machine a vertical rotary driven shaft, a motor support thereabove, an electrlc driving motor, a hydraulic coupling to transmit power from the motor shaft to said driven shaft, means mounting the stator-carrying frame of said motor in vertical position for limited turning movement on said support, said means including a circular series of bearings between the motor frame and the support, an oil supply line I said motor in opposition to said force-exerting said pressure header, an oil tank and pump for i forcing oil into said pressure header and said connecting means, and a pressure relief valve in said connecting means to maintain a predetermined substantially uniform pressure in said pressure header and branch lines.
  • a plurality of machines each having a rotary driving motor, a rotary driven shaft, a hydraulic coupling to transmit power to the driven shaft from the motor, a motor frame mounted for limited turning move ment in reaction to the motor torque, an oil supply line leading into the hydraulic coupling, a control valve in said line to vary the oil inflow to the coupling, means in the coupling for-continuously discharging oil therefrom, means operated by such turning movement of said frame for moving said control valve to restrict said oil inflow and fluid-pressure-responsive means for o posing turning movement of said frame and urgmeans.

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2596927A (en) * 1947-06-20 1952-05-13 Western States Machine Co Centrifugal machine control organization
US2636594A (en) * 1945-06-27 1953-04-28 Wallace E Kerr Procedure and apparatus for metal drawing
US2673450A (en) * 1950-01-24 1954-03-30 Twin Dise Clutch Company Rotary turbine-type hydraulic coupling
US3096620A (en) * 1960-05-31 1963-07-09 American Radiator & Standard Fluid drive improvement
US3255590A (en) * 1964-04-16 1966-06-14 Gen Motors Corp Control system with multiple pressure source for pressure operated devices
US3873244A (en) * 1972-08-21 1975-03-25 Haeny & Cie Electrical variable-speed drive
US3941956A (en) * 1972-11-28 1976-03-02 H. Maihak Ag Apparatus for indicating the filling level of silos and the like
US4345884A (en) * 1980-01-28 1982-08-24 Peerless Pump Division, Indian Head Inc. Pump drive

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US552521A (en) * 1896-01-07 Stephen d
US1282344A (en) * 1918-05-15 1918-10-22 Isaac F Willey Quill and housing for moisture-extractors for drying clothes.
US1387149A (en) * 1918-06-26 1921-08-09 Wagner Electric Mfg Co Voltage-regulating apparatus
US1536915A (en) * 1921-06-03 1925-05-05 S S Hepworth Company Centrifugal machine
US1663513A (en) * 1922-03-02 1928-03-20 Riley Stoker Corp Ram drive for underfeed stokers
US1768938A (en) * 1925-10-08 1930-07-01 Sinclair Harold Hydraulic power-transmitting apparatus
DE541961C (de) * 1930-03-19 1932-01-16 Gustav Bauer Dr Fluessigkeitsgetriebe nach Art der Foettinger-Getriebe
US1855032A (en) * 1927-07-06 1932-04-19 Sinclair Harold Load equalizing machinery
US2227814A (en) * 1938-10-10 1941-01-07 Oilgear Co Control for hydraulic transmissions
US2287709A (en) * 1940-01-30 1942-06-23 Nat Supply Co Hydraulic well pumping mechanism
US2300338A (en) * 1940-10-03 1942-10-27 Florence Pipe Foundry & Machin Hydraulic press and the like
US2301719A (en) * 1939-12-06 1942-11-10 Turchan Manuel Attachment for high speed heads

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US552521A (en) * 1896-01-07 Stephen d
US1282344A (en) * 1918-05-15 1918-10-22 Isaac F Willey Quill and housing for moisture-extractors for drying clothes.
US1387149A (en) * 1918-06-26 1921-08-09 Wagner Electric Mfg Co Voltage-regulating apparatus
US1536915A (en) * 1921-06-03 1925-05-05 S S Hepworth Company Centrifugal machine
US1663513A (en) * 1922-03-02 1928-03-20 Riley Stoker Corp Ram drive for underfeed stokers
US1768938A (en) * 1925-10-08 1930-07-01 Sinclair Harold Hydraulic power-transmitting apparatus
US1855032A (en) * 1927-07-06 1932-04-19 Sinclair Harold Load equalizing machinery
DE541961C (de) * 1930-03-19 1932-01-16 Gustav Bauer Dr Fluessigkeitsgetriebe nach Art der Foettinger-Getriebe
US2227814A (en) * 1938-10-10 1941-01-07 Oilgear Co Control for hydraulic transmissions
US2301719A (en) * 1939-12-06 1942-11-10 Turchan Manuel Attachment for high speed heads
US2287709A (en) * 1940-01-30 1942-06-23 Nat Supply Co Hydraulic well pumping mechanism
US2300338A (en) * 1940-10-03 1942-10-27 Florence Pipe Foundry & Machin Hydraulic press and the like

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636594A (en) * 1945-06-27 1953-04-28 Wallace E Kerr Procedure and apparatus for metal drawing
US2596927A (en) * 1947-06-20 1952-05-13 Western States Machine Co Centrifugal machine control organization
US2673450A (en) * 1950-01-24 1954-03-30 Twin Dise Clutch Company Rotary turbine-type hydraulic coupling
US3096620A (en) * 1960-05-31 1963-07-09 American Radiator & Standard Fluid drive improvement
US3255590A (en) * 1964-04-16 1966-06-14 Gen Motors Corp Control system with multiple pressure source for pressure operated devices
US3873244A (en) * 1972-08-21 1975-03-25 Haeny & Cie Electrical variable-speed drive
US3941956A (en) * 1972-11-28 1976-03-02 H. Maihak Ag Apparatus for indicating the filling level of silos and the like
US4345884A (en) * 1980-01-28 1982-08-24 Peerless Pump Division, Indian Head Inc. Pump drive

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