US3403514A - Scoop-trimmed hydraulic turbocouplings - Google Patents

Scoop-trimmed hydraulic turbocouplings Download PDF

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Publication number
US3403514A
US3403514A US609526A US60952667A US3403514A US 3403514 A US3403514 A US 3403514A US 609526 A US609526 A US 609526A US 60952667 A US60952667 A US 60952667A US 3403514 A US3403514 A US 3403514A
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United States
Prior art keywords
scoop
coupling
emptying
quick
trimming
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Expired - Lifetime
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US609526A
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English (en)
Inventor
Walter H K James
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FLUIDRIVE ENGR CO Ltd
Fluidrive Engineering Co Ltd
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Fluidrive Engineering Co Ltd
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Publication date
Application filed by Fluidrive Engineering Co Ltd filed Critical Fluidrive Engineering Co Ltd
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Publication of US3403514A publication Critical patent/US3403514A/en
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    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
    • F16D33/08—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control
    • F16D33/14—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control consisting of shiftable or adjustable scoops
    • 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

  • a scoop-trimmed hydraulic turbocoupling has a second, quick-emptying scoop which is forced into the ring of liquid in the scoop chamber to effect abnormally rapid emptying of the coupling when a detector detects abnormal operation conditions, for example pulling-out of a synchronous electric motor driving the coupling or seizure of the driven load, requiring disconnection of the coupling drive more quickly than can be effected by the normal trimming scoop.
  • This invention relates to scoop trimmed hydraulic turbocouplings and to power transmission systems in which drive is transmitted through scoop-trimmed hydraulic turbocouplings.
  • Scoop-trimmed hydraulic turbocouplings comprise vaned impeller and runner elements which together define ⁇ a toroidal working circuit for the working uid and a casing which rotates with the impeller and extends around the runner to form a scoop chamber into which extends a movable trimming scoop.
  • the scoop chamber is in communication with the working circuit and the scoop trims off the liquid from the scoop chamber and thereby from the working circuit.
  • Liquid is conveyed from the scoop to a reservoir, and is returned from the reservoir to the working circuit at a steady rate by a pump. In many cases a cooler for the liquid is suitably located in the flow path.
  • the radial position of the scoop in the scoop chamber determines the radial depth of liquid in the scoop chamber and thereby the quantity of liquid in the working circuit. This in turn determines the torque transmitted by the coupling.
  • the transmitted torque, and hence the transmitted power can be adjusted by adjusting the position of the scoop in the scoop chamber.
  • Scoop-trimmed hydraulic turbocouplings can thus be conveniently incorporated in power transmission systems for use where the transmitted torque is to be controllable. This enables the speed of a driven machine to be controlled and also enables the driving machine, for example an electric motor, to be quickly run up to its operating speed before applying the full load torque.
  • Adjustment of the scoop position, and hence the transmitted torque is often effected automatically by a servomechanism in response to changes in operating conditions.
  • the speed of movement of the scoop is deliberately kept low.
  • the trimming scoop may take ten or even twenty seconds to move through its full range of movement.
  • a scoop-trimmed turbocoupling includes a second movable scoop constructed as a quick-emptying scoop and actuating means for moving the quick-emptying scoop to empty the scoop chamber and thereby the working circuit in response to a signal from a detector for detecting an abnormal operating condition necessitating rapid reduction in the torque transmitted by the coupling.
  • the size of the outer diameter of the trimming scoop is restricted by the other parts of the coupling. Accordingly, the wall thickness and thereby the mechanical strength of the tube can only be increased at the expense of reducing the bore of the trimming scoop. This in turn would increase the flow velocities in the trimming scoop, leading to the possibility of turbulence and surging which may be reflected back into the working circuit to upset the steady transmission of torque. It is thus in general not considered feasible to construct a satisfactory trimming scoop which can also be used for rapid emptying of the coupling by being forced deeply into the rotating ring of liquid in the scoop chamber.
  • the quick-emptying scoop acts independently of the trimming scoop and can therefore be designed for optimum performance in removing liquid from the scoop chamber and working circuit.
  • the trimming scoop may take 10 or 20 seconds to complete its travel
  • the quick-emptying scoop may complete of its travel from the working-circuit full to the Working-circuit empty positions in four seconds so that in this time interval the torque transmitted by the coupling may drop to no more than a quarter of the full load value.
  • the quick-emptying scoop may remain stationary during normal operation of the coupling and of the trimming scoop with its scooping orifice just clear of the circuit full position.
  • the quick-emptying scoop and its actuating means may -move With the trimming scoop during normal operation, with the scooping orifice of the quickempty-ing scoop retracted relative to the trimming scoop so as to lie a short distance outside the radial level of liquid determined vby the scooping orifice of the trimming scoop. The quick-emptying scoop then has less far to move if its operation becomes necessary in the partially filled condition of the working circuit.
  • Both the trimming scoop and the quick-emptying scoop may be of different designs best suited for the purposes they have to fulll.
  • the trimming scoop tube mouth and section may be sized specifically to give good regulation with minimum aeration of the liquid, whilst the quick-emptying scoop tube would be constructed specifically for very rapid emptying.
  • -a diverter valve may be included in the supply conduit from the pump to the working circuit.
  • the diverter valve is operated simultaneously with movement of the quick-emptying scoop and may for example, be mechanically linked to it.
  • the diverter valve diverts the pump output away from the working circuit, conveniently back into the reservoir.
  • the speed of operation of the quick-emptying scoop can thereby be increased since the normally continuous supply of working liquid to the working circuit is cut off.
  • FIG. l is a perspective view with parts cut away of a scoop-trimmed coupling in accordance with the invention.
  • FIG. 2 is a side elevational view of the coupling shown in FIG. 1, the upper part of the figure being shown in vertical axial section;
  • FIG. 3 is a diagrammatic cross sectional view on the line III-III of FIG. 2 showing a modified form of scoop operating gear in the normal operating condition;
  • FIG. 4 is a view corresponding to FIG. 3 showing the quick-emptying scoop in its operational position for rapidly emptying the coupling under emergency conditions.
  • the scoop-trimmed hydraulic turbocoupling shown in FIGS. l and 2 follows conventional practice in that it comprises a base 1, the interior of which forms a sump for the working liquid and on which is mounted a housing 2 supporting in a spherical bearing 3 co-axial input and output shafts 4 and S, the input and output shafts being located relative to each other by a bearing 6.
  • a bearing 6 Secured to the input shaft 4 is an impeller casing 7 carrying the impeller element 8 and a scoop chamber 9.
  • a runner element 10 is secured to the output shaft 5.
  • the impeller 8 is also mounted on an impeller sleeve 11 which is rotatably supported by the spherical bearing 3.
  • the impeller and runner elements 8 and 10 are vaned and together define a toroidal working circuit W for the working liquid of the coupling.
  • the working circuit W is in free communication with the interior of the scoop chamber 9 through the gap between the impeller and runner elements 8 and 10 at their radial outer peripheries.
  • Oil for filling the working circuit W is delivered by a motor driven pump 12 from which the oil passes through a cooler 13 and a diverter valve 14 to an inlet pipe 15 which delivers oil to the working circuit through internal passages 16 within the housing 2.
  • a trimming scoop tube 17 is slidably mounted in the housing 2 and extends into the scoop chamber 9.
  • the free end of the scoop tube 17 is formed with a scooping orifice 18 which dips into the annulus of oil in the scoop chamber 9 and trims off oil into the scoop tube 17.
  • the scoop tube 17 is formed with an ecological 19 through which the oil passes through an elbow 20 to a cylindrical de-aerator chamber 21 which it enters tangentially to form a rotating oil film on the wall thereof. From the lower end of the chamber 21 the oil drops into the sump in the base 1.
  • the scoop tube 17 can be moved between its various operating positions by a hydraulic or pneumatic actuator 22, the range of movement of which is sufficient to move the scoop between one end position in which the scoop chamber 9 and working circuit W are empty and substantially no torque is transmitted and the other end position in which the working circuit W and scoop chamber 9 are full.
  • the actuator 22 enables the scoop tube 17 to be heldin any desired intermediate position corresponding to the desired partial filling of the working circuit W.
  • the actuator 22 is controlled by appropriate control gear which is conventional in the art and the precise nature of which is determined by the installation in which the coupling is used. In general the speed of movement of the scoop tube 17 will be kept low in order to avoid hunting and overshooting of the control systems and thus of the transmitted torque.
  • the coupling shown in FIGS. 1 and 2 differs from conventional practice in that it includes a second, quickemptying scoop tube 23 which is parallel to the ⁇ scoop tube 17 but mounted on the opposite side of the coupling axis.
  • the external diameter of the quick-emptying scoop tube 23 may be the same as that of the scoop tube 17 but as clearly shown in FIG. 2 its wall thickness is greater, thereby imparting greater rigidity.
  • the quick-emptying scoop tube 23 terminates in a scooping orifice 24 which is larger than the orifice 18.
  • the scoop tube 23 is normally located so that its scooping orifice 24 lies radially inwards of the annulus of oil in the scoop chamber 9 so that under normal operating conditions there is no flow through the quick-emptying scoop tube 23 in any position of the control scoop tube 17.
  • the quick-emptying scoop tube 23 can be forced further into the scoop chamber 9 under emergency conditions by an actuator 2S which is arranged to operate much more rapidly than the actuator 22.
  • the greater rigidity of the scoop tube 23 enables it to withstand the forces imposed on it by this operation while its large scooping orifice 24 empties the working circuit W and scoop chamber 9 very rapidly.
  • the pressure supply to the actuator 25 is also applied to a conduit 26 to actuate the diverter valve 14 to divert the ow from the cooler 13 directly back into the sump through a conduit 27, thereby diverting the flow from the coupling inlet 15.
  • control and quick-emptying scoop tubes 17 and 23 are shown by way of comparison in phantom outline in FIG. 2.
  • FIGS. 3 and 4 illustrate an alternative arrangement for operating the scoop tubes 17 and 23.
  • the quick-emptying scoop tube 23 moves with the control scoop tube 17 but is positioned so that its orifice 24 is slightly nearer to the coupling axis than the control scoop orifice 18 so that no liquid enters the orifice 24.
  • the scoop tube 23 only has to move a small distance for its orifice to enter the annulus of liquid in the chamber 9.
  • the scoop tube 17 carries an arm 27' which in turn carries a lost motion device 28 which cooperates with a flange 29 on the quick-emptying scoop 23.
  • the lost motion device 28 provides two abutments 30 and 31.
  • a spring 32 of sufficient stiffness to move the quickemptying scoop 23 under normal conditions is positioned between the abutment 31 and the flange 29.
  • the actuator 25' for the quick-emptying scoop is normally empty of fluid but is provided with pressurised uid through the pipe 26' under emergency conditions.
  • the rst of these applications relates to synchronous electric motor drives.
  • the fluid coupling scoop is controlled by a servo motor receiving its signals from the automatic boiler control system in the case of a boiler feed pump.
  • the scoop tube would normally be moved at a rate determined by this servo gear and to match the overall dynamics of the plant it may take anything from l to 20 seconds for the scoop tube to be moved through its full travel from circuit full to circuit empty.
  • the quick-emptying scoop is held normally at the circuit full position until signalled to move, whereafter it would empty the uid coupling to a suicient degree within, say four seconds, that is to say the auxiliary scoop tube would go through about 90% of the full travel in four seconds, whereafter the iiuid coupling could not transmit more than, say, one-quarter full load torque.
  • a suitable detector would again actuate the scoop 23 to move very quickly to the circuit full position and the fluid coupling working circuit would be refilled by the oil pump to the level called for by the control scoop tube 17 very quickly. Therefore, throughout the cycle the control scoop tubeconnected to the usual automatic control equipment need not move, and on resumption of normal operation would continue to regulate the Huid coupling in the usual way.
  • the second application of the invention to be described in more detail relates to the direct driving of main boiler feed pumps by turbo-alternator sets.
  • a 275 mw. turbo-alternator running at 3,000 r.p.m. drives an 8,000 H.P. boiler feed pump through a scoop trimming coupling having a double working circuit, that is having two impellers, two runners and two scoop chambers with a trimming scoop in each chamber, the two runners being connected together back-to-back.
  • the uid coupling is particularly chosen to have a low minimum slip so that the torque transmitted by the working circuit when the output is stalled is many times the nominal full load torque value.
  • the trimming scoops are usually arranged to move at a rate not faster than full travel in, say, 10 to 20 seconds. Therefore, if a quick-emptying scoop were provided for each circuit, they could have their servo lactuating means responsive to the output of a temperature senser such as a thermocouple in the oil leaving the working circuit. In the event of the uid coupling stalling and a dangerous rise in temperature ensuing, the quick-emptying scoops would be moved very rapidly and thus empty the fluid coupling circuits and keep them empty.
  • a scoop-trimmed hydraulic turbocoupling comprising vaned impeller and runner elements which together dene a toroidal working circuit for the working uid, a casing which rotates with the impeller and extends around the runner to form a scoop chamber into which extends a movable trimming scoop, the scoop chamber -being in communication with the working circuit, and wherein the coupling includes a second movable scoop constructed as a quick-emptying scoop and actuating means ⁇ for moving the quick-emptying scoop to empty the scoop chamber and thereby the working circuit in response to a signal from a detector for detecting an abnormal operating condition necessitating abnormally rapid reduction in the torque transmitted by the coupling.
  • a coupling according to claim 1, wherein the quickemptying scoop and its actuating means may move with the trimming scoop during normal operation, with the scooping perennial of the quick-emptying scoop retracted relative to the trimming scoop so as to lie a short distance outside the radial level of liquid determined by the scooping orifice of the trimming scoop.
  • a coupling according to claim 1, wherein the said detector is a power factor pull-out relay associated with a synchronous electric motor connected to drive the coupling.
  • a coupling according to claim 1, wherein the said detector is a thermally sensitive device responsive to temperature increases in the liquid leaving the working circuit.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Positive-Displacement Air Blowers (AREA)
US609526A 1966-01-18 1967-01-16 Scoop-trimmed hydraulic turbocouplings Expired - Lifetime US3403514A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB2379/66A GB1172861A (en) 1966-01-18 1966-01-18 Scoop Trimmed Hydraulic Turbo Couplings

Publications (1)

Publication Number Publication Date
US3403514A true US3403514A (en) 1968-10-01

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ID=9738517

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Application Number Title Priority Date Filing Date
US609526A Expired - Lifetime US3403514A (en) 1966-01-18 1967-01-16 Scoop-trimmed hydraulic turbocouplings

Country Status (5)

Country Link
US (1) US3403514A (zh)
BE (1) BE692822A (zh)
FR (1) FR1515196A (zh)
GB (1) GB1172861A (zh)
SE (1) SE326607B (zh)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3478516A (en) * 1967-03-22 1969-11-18 Voith Getriebe Kg Emptying device for fluid flow circuits
US3646756A (en) * 1970-02-12 1972-03-07 American Standard Inc Trapezoidial scoop tube
US3703078A (en) * 1971-04-19 1972-11-21 American Standard Inc Rapid response fluid drive
WO2016028156A1 (en) * 2014-08-18 2016-02-25 Aker Subsea As Topsides variabel speed drive for large pumps or compressors

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2264341A (en) * 1939-06-20 1941-12-02 Sinelair Harold Rotary power transmitter employing a working liquid
US2428005A (en) * 1941-02-19 1947-09-30 Bennett Feragen Inc Dynamometer
US2492456A (en) * 1948-09-23 1949-12-27 Becker John Edward Fluid circulation control for reversible fluid couplings
GB762371A (en) * 1953-09-03 1956-11-28 Harold Sinclair Improvements relating to hydraulic turbo couplings
US3320748A (en) * 1965-10-01 1967-05-23 American Radiator & Standard Fluid coupling control means

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2264341A (en) * 1939-06-20 1941-12-02 Sinelair Harold Rotary power transmitter employing a working liquid
US2428005A (en) * 1941-02-19 1947-09-30 Bennett Feragen Inc Dynamometer
US2492456A (en) * 1948-09-23 1949-12-27 Becker John Edward Fluid circulation control for reversible fluid couplings
GB762371A (en) * 1953-09-03 1956-11-28 Harold Sinclair Improvements relating to hydraulic turbo couplings
US3320748A (en) * 1965-10-01 1967-05-23 American Radiator & Standard Fluid coupling control means

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3478516A (en) * 1967-03-22 1969-11-18 Voith Getriebe Kg Emptying device for fluid flow circuits
US3646756A (en) * 1970-02-12 1972-03-07 American Standard Inc Trapezoidial scoop tube
US3703078A (en) * 1971-04-19 1972-11-21 American Standard Inc Rapid response fluid drive
WO2016028156A1 (en) * 2014-08-18 2016-02-25 Aker Subsea As Topsides variabel speed drive for large pumps or compressors
GB2544242A (en) * 2014-08-18 2017-05-10 Aker Solutions As Topsides variabel speed drive for large pumps or compressors
US20170244312A1 (en) * 2014-08-18 2017-08-24 Aker Solutions As Topsides variable speed drive for large pumps or compressors
NO344104B1 (en) * 2014-08-18 2019-09-02 Aker Solutions As Topsides variable speed drive for large pumps or compressors

Also Published As

Publication number Publication date
BE692822A (zh) 1967-07-03
GB1172861A (en) 1969-12-03
SE326607B (zh) 1970-07-27
FR1515196A (fr) 1968-03-01

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