US3486336A - Hydraulic turbo-couplings - Google Patents

Hydraulic turbo-couplings Download PDF

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Publication number
US3486336A
US3486336A US721327A US3486336DA US3486336A US 3486336 A US3486336 A US 3486336A US 721327 A US721327 A US 721327A US 3486336D A US3486336D A US 3486336DA US 3486336 A US3486336 A US 3486336A
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United States
Prior art keywords
coupling
impeller
liquid
working circuit
working
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Expired - Lifetime
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US721327A
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English (en)
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John Bilton
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Fluidrive Engineering Co Ltd
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Fluidrive Engineering Co Ltd
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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

Definitions

  • HYDRAULIC TURBO-COUPLINGS Filed April l5, 1958 3 Sheets-Sheet 2 Dec. 30, 1969 J. alLToN HYDRAULIC TURBO-COUPLINGS 3 Sheets-Sheet 5 Filed April l5, 1968 United States Patent O 3,486,336 HYDRAULIC TURBO-COUPLINGS John Bilton, Hampton, England, assignor to Fluidrive Engineering Company Limited, Isleworth, Midllesex, lEngland Filed Apr. 15, 1968, Ser. No. 721,327 Clalms priority, application Great Britain, Apr. 21, 1967, 18,57 1/ 67 Int. Cl. Fld 3]/06; Ft4d 29/02 U.S. Cl.
  • a hydraulic turbo-coupling comprising vaned impeller and runner elements which together dene a toroidal working circuit, working liquid being supplied to the working circuit through ports in the impeller or runner.
  • the liquid emerging from these ports is protected by shields against the strong flow along the boundary wall of the working circuit which is particularly strong when the coupling is in the stalled condition with the runner substantially stationary.
  • the resistance offered to the incoming liquid is reduced, for example to one quarter of the normal resistance. This greatly assists the maintenance of a cooling flow through the coupling in the stalled condition particularly where the liquid cannot be directly pressure-fed to the ports.
  • the present invention relates to improvements in hydraulic turbo-couplings of the kind in which working liquid is fed into the working circuit through one or more ports in the impeller or runner element.
  • An object of the present invention is to increase the rate of filling of such a hydraulic coupling or to reduce the back pressure presented to the filling tlow particularly during the time that the coupling is stalled, that is to say when the runner of the coupling is stationary while the impeller is being rotated at a normal working speed.
  • a hydraulic turbo-coupling comprising vaned impeller and runner elements together dening a toroidal working circuit for liquid, at least one of the elements being formed with one or more inlet ports for supplying liquid to till the coupling during operation, wherein a shield for the inlet port or each inlet port projects from the wall of the working circuit into the path of the working liquid to protect liquid emerging into the working circuit from the port from the high speed flow of liquid around the periphery of the working circuit in the direction from the radially inner portion of the runner to the radially inner portion of the impeller when the coupling is operating in the stalled condition.
  • each such shield is formed by a short length of tube the discharge end of which may be angled to face in the direction ot fluid flow in the working circuit.
  • the velocity of vortex flow is highest in a layer which lies close to the boundary of the Working circuit.
  • the inlet tubes may be dimensioned to project through this layer into the inside of the vortex where the flow velocity under the stalled condition is lower than in the said layer.
  • the inlet port or ports are formed in the impeller element of the coupling. This ensures that the inowing working liquid is subjected to less variation in the centrifugal head since the variation in the angular speed of the impeller is usually much less than that of the runner. Furthermore the flow of Working liquid around the working circuit is consequently more uniform and theretore the resulting cooling tiow through the coupling is more steady thereby helping to ensure the reliable removal Patented Dec. 30, 1969 of the considerable amount of heat generated in the coupling in the stalled condition.
  • Hydraulic turbo-couplings normally include a bale at the radially inner region of the runner.
  • An additional am may be mounted on the impeller also in its radially inner region.
  • the additional batender is preferably not of greater outside diameter than the normal anti-surge baflie fitted to the runner.
  • the additional batiie serves to assist the inlet port shields by deecting the boundary vortex ow in the stalled condition away from the shielded inlet ports. It is desirable to retain the runner batiie in order to prevent liquid being deflected through the clearance between the impeller and runner at the inner profile diameter of the Working circuit.
  • FIG. 1 shows part of a hydraulic turbo-coupling in axial section
  • FIG. 2 shows an inlet port shield in longitudinal section
  • FIG. 3 is a transverse section on the line III- III of FIG. 2,
  • FIG. 4 is an end View in the direction of the arrow IV of FIG. 3, and
  • FIG. 5 is a view corresponding to FIG. 1 of a scooptrimmed turbo coupling.
  • the hydraulic turbo-coupling shown in FIG. 1 is basically of conventional design in that it comprises vaned impeller and runner elements 1 and 2 which together detine a toroidal circuit W for liquid such as oil.
  • the impeller 1 carries an inner radial ange 3 which is secured by bolts 4 to a driving sleeve 5 connected to a prime mover (not shown).
  • the runner 2 has a radially inner flange 6 which is bolted at 7 to an output sleeve 8.
  • An anti-surge bat-lie 9 is also bolted to the flange 6 by bolts 7.
  • an additional batiie 10 ⁇ is bolted to the impeller flange 3 by the bolts 4.
  • the additional baffle 10 may be of the same outer diameter as the bale 9.
  • Oil is fed into the coupling through sixteen inlet ports 11 in the impeller.
  • the ports 11 are fed from an annular collector channel 12 in the impeller 1 into which open one or more inlet passages 13 in the stationary part 14 of the coupling structure. Oil leaves the radially outer part of the working circuit at a controlled rate. This may be effected by conventional means (not shown).
  • each inlet 11 Secured in each inlet 11 is a shield 16 formed by a short length of tube (FIGS. 2 to 4) the discharge end 17 of each tube 16 is angled at 45 degrees so as to face in the direction of the boundary ow of the working liquid along the walls of the working circuit. This direction extends, at the radially inner part of the working circuit, from the runner to the impeller and is indicated generally by the arrow 18.
  • each shield 16 is formed with a slot 20 to accommodate the edge portions 21 of the vanes 22 of the impeller 1.
  • the arrangement described above may reduce the head to be overcome when lling the coupling in the stalled (and high slip) condition by a factor of four.
  • the arrangement may be applied to any form of coupling requiring a tilling ow. It has a further advantage in the case of a scoop control type of uid coupling as shown for example in British patent specication No. 798,524.
  • FIG. shows a scoop-trimmed coupling intended for transmitting relatively high powers at high rotational speeds. Parts correspondingly to parts in FIG. 1 are indicated by the same reference numerals primed.
  • the inner probook diameter of the coupling is not much greater than the diameter of the hollow shafts 5' and 8 required for transmitting the input and output torque to the coupling. Accordingly the impeller and runner elements 1' and 2 are splined directly to their respective shafts 5 and 8 at 23 and 24, concentricity fbeing ensured by tapered surfaces 25 and 26 and annular wedge rings 27 and 28 which are tightened by means of annular nuts forming the batlles 9' and 10.
  • An impeller casing 29 surrounds the runner 2 and is secured to a flange 30 on the impeller 1. Also secured to the flange 30 is a scoop chamber casing 31 dening an annular scoop chamber 32 in which is mounted a scoop tube 33 having a scooping orifice 34.
  • the scoop tube 33 is movable axially of itself to determine the position of the radially inner surface of the ring of working liquid which collects in the scoop chamber 32 when the impeller is rotating.
  • the scoop chamber 32 communicates with the radially outermost part of the Working circuit W through passages 35 in the impeller 1.
  • the scoop chamber casing 31 carries a n-umber of restricted leak-olf nozzles 36.
  • the tubes 16 protect the incoming ow into the working circuit from the direct action of the Vortex ilow around the boundary wall of the working circuit W' which can occur when the runner 2 is stalled. They also serve to remove from the coupling any working liquid which may accidentally enter the working circuit W when the coupling is shut down and the runner 2' is rotated for any reason.
  • the baflies 9' and 10 reduce the leakage ow through the clearancesv between the shafts 5 and 8' under all opearting conditions including cases where the runner 2 is rotated while the impeller 1 is stationary and the vortex ow is in the reverse direction to normal.
  • liquid cannot be fed directly under pressure to the working circuit along the axis of the coupling for design reasons, usually because the necessarily large bores required to transmit the maximum filling flow cannot be accommodated within the restricted shaft diameters without weakening the shafts.
  • the working liquid is supplied to the annular channel 12 or 12 in the back of the impeller so that for a given impeller speed there is a xed and relatively small centrifugal head available for feeding the fresh liquid into the working circuit W.
  • the shielded inlets 16, 16 serve to reduce this resistance to an acceptable value under the most adverse condition, that is to say when the runner is stalled. lt is precisely under this condition that the cooling flow is most desired in view of the high rate of disipation of heat in the coupling.
  • a hydraulic turbo-coupling comprising vaned impeller and runner elements together defining a toroidal yworking circuit for liquid, at least one of the said elements being formed with one or more inlet ports for supplying liquid to ll the coupling during operation, wherein a shield for the inlet port or each inlet port projects from the wall of the Working circuit into the path of the working liquid to protect liquid emerging into the working circuit from the port from the high speed flow of liquid around the periphery of the working circuit in the direction from the radially inner portion of the runner to the radially inner portion of the impeller when the coupling is operating in the stalled condition.
  • each such shield is formed by a tubular extension surrounding the respective inlet port and projecting into the working circuit.
  • each tubular extension is angled to face in the direction of normal uid flow in the working circuit as seen in axial section.
  • baes form nuts for securing their respective elements to respective hollow driving and driven shafts.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Turbines (AREA)
  • Joints Allowing Movement (AREA)
US721327A 1967-04-21 1968-04-15 Hydraulic turbo-couplings Expired - Lifetime US3486336A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1857167 1967-04-21

Publications (1)

Publication Number Publication Date
US3486336A true US3486336A (en) 1969-12-30

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ID=10114744

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Application Number Title Priority Date Filing Date
US721327A Expired - Lifetime US3486336A (en) 1967-04-21 1968-04-15 Hydraulic turbo-couplings

Country Status (5)

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US (1) US3486336A (enExample)
DE (1) DE1750311A1 (enExample)
FR (1) FR1561695A (enExample)
GB (1) GB1227944A (enExample)
NL (1) NL152339B (enExample)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3747348A (en) * 1972-02-16 1973-07-24 Fluidrive Eng Co Ltd Hydrodynamic power drives
US6065286A (en) * 1997-03-12 2000-05-23 Hellinger; Walter Modular hydrodynamic coupling unit for integration into a power transmission unit

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1387831A (en) * 1971-02-17 1975-03-19 Fluidrive Ng Co Ltd Hydrodynamic power drives
DE3341819A1 (de) * 1983-11-19 1985-04-04 Hans-Jürgen 4370 Marl Chilinski Luftpumpe mit integriertem ringschloss
AU2002212175A1 (en) 2000-08-30 2002-03-13 Voith Turbo Gmbh And Co. Kg Method for controlling the power consumption of a hydrodynamic clutch by controlling the volumetric efficiency and a hydrodynamic clutch
DE10046833A1 (de) * 2000-08-30 2002-03-28 Voith Turbo Kg Hydrodynamische Baueinheit

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2466356A (en) * 1946-02-14 1949-04-05 Becker John Edward Torque limiting device for fluid clutches
US2864240A (en) * 1953-09-21 1958-12-16 Youngstown Sheet And Tube Co Hydraulic couplings with means providing for misalignment of input and output shafts
US3045432A (en) * 1958-12-15 1962-07-24 American Radiator & Standard Fluid coupling
US3165894A (en) * 1962-08-13 1965-01-19 American Radiator & Standard Torque limiting ports-fluid drives
US3245220A (en) * 1963-10-16 1966-04-12 Fluidrive Eng Co Ltd Hydraulic turbo couplings

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2466356A (en) * 1946-02-14 1949-04-05 Becker John Edward Torque limiting device for fluid clutches
US2864240A (en) * 1953-09-21 1958-12-16 Youngstown Sheet And Tube Co Hydraulic couplings with means providing for misalignment of input and output shafts
US3045432A (en) * 1958-12-15 1962-07-24 American Radiator & Standard Fluid coupling
US3165894A (en) * 1962-08-13 1965-01-19 American Radiator & Standard Torque limiting ports-fluid drives
US3245220A (en) * 1963-10-16 1966-04-12 Fluidrive Eng Co Ltd Hydraulic turbo couplings

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3747348A (en) * 1972-02-16 1973-07-24 Fluidrive Eng Co Ltd Hydrodynamic power drives
US6065286A (en) * 1997-03-12 2000-05-23 Hellinger; Walter Modular hydrodynamic coupling unit for integration into a power transmission unit

Also Published As

Publication number Publication date
NL152339B (nl) 1977-02-15
DE1750311A1 (de) 1971-01-21
GB1227944A (enExample) 1971-04-15
NL6805614A (enExample) 1968-10-22
FR1561695A (enExample) 1969-03-28

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