GB2043207A - Rotary coupling - Google Patents

Rotary coupling Download PDF

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Publication number
GB2043207A
GB2043207A GB8005052A GB8005052A GB2043207A GB 2043207 A GB2043207 A GB 2043207A GB 8005052 A GB8005052 A GB 8005052A GB 8005052 A GB8005052 A GB 8005052A GB 2043207 A GB2043207 A GB 2043207A
Authority
GB
United Kingdom
Prior art keywords
coupling
hubs
sleeve
flexible bar
teeth
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB8005052A
Other versions
GB2043207B (en
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.)
Maag Gear Wheel and Machine Co Ltd
Maag Zahnrader und Maschinen AG
Original Assignee
Maag Gear Wheel and Machine Co Ltd
Maag Zahnrader und Maschinen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Maag Gear Wheel and Machine Co Ltd, Maag Zahnrader und Maschinen AG filed Critical Maag Gear Wheel and Machine Co Ltd
Publication of GB2043207A publication Critical patent/GB2043207A/en
Application granted granted Critical
Publication of GB2043207B publication Critical patent/GB2043207B/en
Expired legal-status Critical Current

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Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C1/00—Flexible shafts; Mechanical means for transmitting movement in a flexible sheathing
    • F16C1/02—Flexible shafts; Mechanical means for transmitting movement in a flexible sheathing for conveying rotary movements
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
    • F16D3/185—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth radial teeth connecting concentric inner and outer coupling parts
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/56—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts
    • 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
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/78—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic disc or flat ring, arranged perpendicular to the axis of the coupling parts, different sets of spots of the disc or ring being attached to each coupling part, e.g. Hardy couplings

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Health & Medical Sciences (AREA)
  • Oral & Maxillofacial Surgery (AREA)
  • Mechanical Operated Clutches (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Pivots And Pivotal Connections (AREA)

Abstract

An articulated coupling for shafts (10, 12) comprises two coupling hubs (18) connected by a coupling-sleeve (20), which in one embodiment Figure 2, comprises a central portion (44) and two end portions (36), each of which carries flexible drive transmission elements (34). A laterally and torsionally flexible shaft (22) is rotationally rigidly bolted to the coupling hubs (18) through flanges (26, 28) to transmit axial loads. As a safety measure, in order to guarantee stoppage of the machine set in which the coupling is installed in the event of the drive transmission elements breaking, the coupling hubs (18) and end portions (36) have interengageable teeth (30, 32). In another embodiment, Figure 4 the teeth (30, 32) provides the driving connection between the hubs, and comprises internal teeth (30) on the hubs and external teeth (32) on the sleeve (20). Abutment means (40, 42) are provided to act in the event of failure of the flexible bar. <IMAGE>

Description

SPECIFICATION Rotary coupling This invention relates to rotary couplings.
In order to transmit relatively high power levels between shafts rotating at high speed, it is often necessary to connect two shaft ends in flexurally resilient manner by means of a coupling of compact construction and at the same time to ensure that an axial thrust, such as may occur four example when a driving engine of a drive set is switched on or off, cannot result in destruction of the coupling.
DAS No. 19 63755 has already disclosed for this purpose couplings which are constructed as rotationally rigid double-tooth couplings having an internally toothed coupling sleeve connecting two externally toothed coupling hubs. In the case of one construction of such a known coupling, instead of there being individual teeth between the coupling hubs and the coupling sleeve, there are disposed radially resilient engaging elements which are sub jest to an initial tension, centering the coupling sleeve in relation to the coupling hubs. In the case of another construction, centering of the coupling sleeve in respect of the coupling hubs is achieved by making individual teeth on the coupling hubs oversized in relation to the relevant teeth on the coupling sleeve and so constructing the coupling sleeve that it can widen out resiliently.In both cases, the coupling sleeve can indeed be centred by virtue of the radial biasing force relative to the coupling hub, but trouble-free operation can only be maintained over a prolonged period if these couplings are not subjected to significant axial force loadings. Relatively high axial forces and the moments created by them during axial offset of the two shafts which are coupled to each other rapidly lead to destruction of known couplings which are of the form described. In consequence, it is vital to relieve such a known coupling of any significant axial force by arranging axial thrust bearings on both sides of it.
Nevertheless, when high levels of power are being transmitted at high speeds, each bearing results in a loss in efficiency, which is why the number of bearings should be kept as small as possible.
According to the present invention, there is provided a rotary coupling comprising two coupling hubs connected to axially spaced regions of a coupling sleeve by respective torque transmission means, said hubs also being connected by a flexible bar that is located inside the coupling sleeve.
The flexible bar can on the one hand be made so resiliently yieldable to the torque load if it is torsionally restrained that effectively the entire torque is transmitted via the transmission means and the coupling sleeve from one coupling hub to the other; on the other hand, the flexible bar can be sufficiently stiff in bending that axial thrust loads can be resisted. Such axial thrust loads might be produced periodically and/or abruptly by a driving unit or by a driven unit.
The couplings may be constructed according to the invention in particular for transmitting power at levels above 10,000 kW. In machine sets with an output of this magnitude, it is possible for one machine to generate an axial thrust of for example 100000N (~ 10000 kp) in one direction and for another machine to generate an axial thrust of 1 50000N (= 15000 kp) in the opposite direction. The coupling according to the invention is capable of accommodating these axial thrust loads so that it is only necessary to have a single axial thrust bearing which has to accommodate the resultant axial thrust of 50000N (= 5000 kp) in the example quoted.As a result, in comparison with known coupling and bearing arrangements, the overall efficiency of the machine set can be increased substantially under otherwise identical conditions.
According to the axial rigidity required, the flexible bar may be flexurally rigidly and/or rotationally rigidly connected to the coupling hubs.
According to the torsional rigidity desired, so the engagement means which transmit the torque may be constructed as diaphragm flexible bars, plates, sleeves, toothing or the like. Depending on their form the engagement means may be arranged as a series of elements distributed evenly around the periphery of the coupling sleeve.
By a direct fixing of the flexible bar onto the two coupling hubs, it becomes possible for a coupling according to the invention to be fitted between and removed from the position between the shaft ends which are to be coupled to each other as one complete unit, in other words without being dismantled.
Two embodiments of the invention will be described in detail hereinafter by way of example with reference to the accompanying diagrammatic drawings, in which: Figure 1 shows an axial section through a first coupling according to the invention in the normal or undeflected position; Figure la shows an enlarged partial section taken on the line A-A in Figure 1; Figure 2 shows the axial section through the coupling of Figure 1 in a considerably exaggerated state of deflection; Figure 3 shows an axial section through a second coupling according to the invention in the normal or undeflected position, and Figure 4 shows the axial section through the coupling according to Figure 3 in a greatly exaggerated state of deflection.
There will first be described some common features of the two double joint couplings illustrated, i.e. that in Figures 1, la and 2 on the one hand and that in Figures 3 and 4 on the other. In both examples, the coupling interconnects two shaft ends 10 and 12 the axes of which are normally in line with each other although they may be inclined in respect of each other and/or as shown in greatly exaggerated form in Figures 2 and 4, they may have a parallel offset. Both shaft ends 10 and 12 have in each case a flange 14forthe coupling. The shaft end 12 disposed on the right of the coupling is shown mounted in a bearing 16 in the example of Figure 1.
Both of the couplings illustrated have as main component parts two coupling hubs 18, a coupling sleeve 20 and a flexible bar 22.
Arranged on each coupling hub 18 is a radially outer flange 24 which is bolted to the flange 14 on the adjacent shaft end 10 or 12. Futhermore, there is arranged on each coupling hub 18 a radially inner flange 26 which is bolted to a flange 28 on the adjacent end of the flexible bar 22, so forming flexurally stiff connections between the bar and the hub inner flanges. The flexible bar is centered in the flanges 26 of the two coupling hubs 18 and extends for the remainder of its length with radial clearance through the coupling hubs 18 and the coupling sleeve 20.
Each of the two coupling hubs 18 has toothing 30 which according to Figures 1, 1 a and 2 is constituted by external teeth, and according to Figures 3 and 4, by internal teeth. Associated with the toothing 30 on the coupling hubs 18 is in each case toothing 32 on the coupling sleeve 20 which according to Figures 1, la and 2 is constituted by internal teeth, and according to Figures 3 and 4 on the other hand by external teeth.
Since, however, the torque which is to be transmitted by the coupling is taken exclusively by the coupling hubs, the coupling sleeves connecting them and the torque transmission elements disposed between the two, these toothings 30 and 32 fulfil quite different functions in the two examples of embodiment.
In the case of the first-mentioned embodiment, the toothings 30 and 32, as can be seen particularly from Figure 1a have in respect of each other considerable clearance in a radial direction and also a certain clearance in a peripheral direction. This means that in normal operation they are not involved in the transmission of torques, in contrast to the secondmentioned embodiment. In the first embodiment Figures 1 and 2, - the two coupling hubs 18 have, disposed in the manner of diaphragms, flexible drive bars 34 the radially outer ends of which are clamped between an end piece 36 of the coupling sleeve 20 which is associated with the relevant coupling hub 18 and a guard ring 38 bolted thereto. The resilient diaphragm flexible bars are very yieldable so that an axial offset of the two shaft ends 10 and 12 can easily be accommodated by these bars.
In the case of the embodiment according to Figures 3 and 4, such an axial offset is accommodated by the crowning of the toothings 30,32 which intermesh to transmit the torque load on the coupling.
In the event of damage - that is to say in the event of the maximum torque loading being exceeded the diaphragm flexible bars 34 would break in the case of the embodiment shown in Figures 1 and 2.
Thus, the toothings 30 and 32 shown spaced apart in Figure 1 a would come into operation and in such a case would make it possible to stop the machine set.
In the case of the embodiment shown in Figures 3 and 4, only a few of the teeth of the toothings 30 and 32 would be damaged if it was arranged that the drive was discontinued as soon as the accident occurred.
The flexible bar 22 is so slender and correspond ingly weak that it does not contribute significantly to torque transmission; it is however sufficiently resistant to bending to be able to transmit all the axial forces which occur directly from one coupling hub 18 to the other, in fact even when the two shaft ends 10 and 12 are offset parallel to one another as indicated in Figures 2 or 4.To provide for the eventuality of the bar 22 breaking, then in the case of the embodiment according to Figures 1 and 2 an annular abutment 40 is constructed on the inside of each end piece 36 of the coupling sleeve 20, the abutment 40 is constructed on the inside of each end piece 36 of the coupling sleeve 20, the abutment 40 fitting into an intermediate space between the toothing 30 of the associated coupling hub 18 and a likewise annular mating abutment 42 fixed on the coupling hub 18.
If the flexible bar 22 breaks, these abutments 40 and mating abutments 42 together with the annularly formed end of the associated toothings 30 limit the axial relative displacement of the two shaft ends 10 and 12 so that the coupling can continue to run without suffering additional damage until the machine set to which the shaft ends 10 and 12 belong has been switched off and has come to a standstill. In the case of the embodiment shown in Figures 3 and 4, should the flexible bar 22 break, the toothings 30 and 32 take over the function of the abutments 40 and with the mating abutments 42 on the one side or the coupling hubs on the other, limit or prevent axial relative displacement of the two shaft ends 10 and 12.
The annularly formed abutments 40 (Figures 1 and 2) and the corresponding mating abutments 42 or the ends of the toothing 32 which projects beyond the abutments 40, are provided with a convex end face. For reasons of scale, this cannot be seen from the drawings.
In the case of the second embodiment (Figures 3 and 4), exactly the same function is performed by a convex end face provided on that end of each toothing 32 which is opposed to the mating abutments 42.
In the case of the embodiment shown in Figures 1 and 2, the two end portions 36 of the coupling sleeve 20 are connected to each other by a tubular middle portion 44; the coupling sleeve 20 is thus in three parts or, if one includes the protective rings 38, in five parts.
In the case of the embodiment shown in Figures 3 and 4, the coupling sleeve 20 is on the other hand in one piece, but at its two ends there is in each case provided a lubricant space 46 recessed within the toothings 32. From these lubricant spaces 46, the toothings can be directly supplied with lubricant through a kind of jet system comprising tiny bores (not shown) in the roots of the teeth. The toothings 32 are convex and are assembled with radial prestress into the toothing 30 on the coupling hubs 18 so that provision is made for centering the two ends of the coupling sleeve 20 in relation to the coupling hubs 18.
It will be noted that in both the examples described above provide a coupling which, when transmitting substantial torques between high speed shafts, permits substantial parallel relative displacements and other axial displacements of these shafts in respect of each other and which is substantially insensitive to axial forces.
It has already been indicated that the bar 22 may not be flexurally stiffly connected to the two hubs. In that case it may be found that the flexibility of its connections is sufficient and that the bar between the connections may be formed by a flexurally stiff element.

Claims (9)

1. A rotary coupling comprising two coupling hubs connected to axially spaced regions of a coupling sleeve by respective torque transmission means, said hubs also being connected by a flexible bar that is located inside the coupling sleeve.
2. A coupling according to claim 1, wherein the flexible bar is flexurally stiffly connected to the two coupling hubs.
3. A coupling according to claim 1 or claim 2, wherein the flexible bar is rotationally rigidly connected to both coupling hubs.
4. A coupling according to claim 2 or claim 3, wherein the flexible bar is bolted to the coupling hubs through flanges.
5. A coupling according to any one of claims 1 to 4 wherein the transmission means comprise diaphragms or diaphragm flexible bars.
6. A coupling according to any one of claims 1 to 4, in which the transmission means comprise interengaging toothing, the coupling sleeve having externally cut teeth and the coupling hubs having internally cut teeth.
7. A coupling according to any one of claims 1 to 6, in which the coupling hubs and the coupling sleeve have co-operating annular abutments comprising convex end faces.
8. A rotary coupling comprising two coupling hubs at opposite ends of a coupling sleeve and each connected to the sleeve by torque transmission means that are distributed around the periphery of the sleeve and that form articulation joints between the sleeve and the respective hubs, said hubs also being connected by a flexible bar that is located within the sleeve and that is able to transmit an axial thrust load between the hubs.
9. A rotary coupling constructed and arranged for use and operation substantially as described herein with reference to Figures 1, 1 a and 2 or Figures 3 and 4 of the accompanying drawings.
GB8005052A 1979-02-16 1980-02-14 Rotary coupling Expired GB2043207B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH153479A CH634133A5 (en) 1979-02-16 1979-02-16 DOUBLE JOINT CLUTCH.

Publications (2)

Publication Number Publication Date
GB2043207A true GB2043207A (en) 1980-10-01
GB2043207B GB2043207B (en) 1983-04-13

Family

ID=4212673

Family Applications (1)

Application Number Title Priority Date Filing Date
GB8005052A Expired GB2043207B (en) 1979-02-16 1980-02-14 Rotary coupling

Country Status (9)

Country Link
JP (1) JPS55112423A (en)
CA (1) CA1125044A (en)
CH (1) CH634133A5 (en)
DE (1) DE2934346C2 (en)
FR (1) FR2449231A1 (en)
GB (1) GB2043207B (en)
IT (1) IT1130005B (en)
NL (1) NL8000649A (en)
SE (1) SE8001102L (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0565119A1 (en) * 1992-04-09 1993-10-13 The Japan Steel Works, Ltd. Cutter holder device in a pelletizer
GB2446863A (en) * 2007-02-21 2008-08-27 Smiths Aerospace Ltd Diaphragm coupling with stops to limit range of movement
CN102410312A (en) * 2011-11-15 2012-04-11 西安交通大学 Gear and thin-wall disc combined type coupling
EP2657558A1 (en) 2012-04-27 2013-10-30 Eurocopter Flexible coupling means, and mechanical transmission
CN103527649A (en) * 2012-07-04 2014-01-22 北京精密机电控制设备研究所 Super high rotating speed safe flexible coupler
US9063114B2 (en) 2012-08-10 2015-06-23 Dionex Softron Gmbh Switching valve for liquid chromatography
WO2015139999A1 (en) * 2014-03-21 2015-09-24 Avl List Gmbh Shaft with adjustable rigidity
US9400265B2 (en) 2012-08-10 2016-07-26 Dionex Softron Gmbh Switching valve for high-performance liquid chromatography
EP3085982A1 (en) * 2015-04-20 2016-10-26 Rolls-Royce plc A shaft assembly comprising a frangible coupling and a flexible coupling
EP3222868A1 (en) * 2016-03-24 2017-09-27 Goodrich Actuation Systems Limited Splined couplings
EP3321532A3 (en) * 2016-11-03 2018-06-13 Goodrich Corporation Flexible couplings with angular limiters
US10267367B2 (en) 2015-08-07 2019-04-23 Airbus Helicopters Flexible coupling means, a mechanical transmission, and an aircraft
DE102015115948B4 (en) * 2014-10-01 2021-02-04 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Drive shaft with two-stage rigidity
US11408467B2 (en) 2019-05-03 2022-08-09 Goodrich Corporation Flexible coupling assembly

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DE3318922A1 (en) * 1983-05-25 1984-11-29 Robert Bosch Gmbh, 7000 Stuttgart Gear machine
EP0211090B1 (en) * 1985-07-26 1989-08-23 BHS-Bayerische Berg-, Hütten- und Salzwerke Aktiengesellschaft Manufacturing process for a flexible coupling means for the transmission of torque
DE3706135A1 (en) * 1987-02-26 1988-09-08 Kloeckner Humboldt Deutz Ag Torsionally rigid compensating coupling with an axial damper, particularly for driving an injection pump
FR2699619B1 (en) * 1992-12-22 1995-02-24 Creusot Loire Mecanique Rotary coupling device and gypsy and grooved pulley comprising such a coupling device.
DE4326868C1 (en) * 1993-08-11 1995-04-06 Voith Gmbh J M Rapid-release safety coupling
DE29610299U1 (en) * 1996-06-12 1996-09-19 Kwd Kupplungswerk Dresden Gmbh Tooth coupling
DE102006042301B4 (en) * 2006-09-08 2018-02-22 Ellergon Antriebstechnik Gmbh Diaphragm compensation clutch and hole reveal connection
DE102012107378B4 (en) * 2012-08-10 2014-05-15 Dionex Softron Gmbh Switching valve for liquid chromatography, in particular high-pressure switching valve for high performance liquid chromatography
DE102012107379B4 (en) * 2012-08-10 2016-09-29 Dionex Softron Gmbh Switching valve for liquid chromatography, in particular high-pressure switching valve for high performance liquid chromatography

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GB594550A (en) * 1945-01-16 1947-11-13 Power Jets Res & Dev Ltd Improvements in or relating to flexible couplings for shafts and the like
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DE749609C (en) * 1940-10-02 1944-11-27 Shaft coupling
US2550580A (en) * 1945-01-16 1951-04-24 Power Jets Res & Dev Ltd Flexible coupling for shafts and the like
FR1196352A (en) * 1958-05-23 1959-11-24 Tacke Maschinenfabrik Komm Ges Angularly movable toothed coupling
US3005323A (en) * 1959-02-19 1961-10-24 Westinghouse Electric Corp Generator drive shaft assembly
DE1208125B (en) * 1959-11-12 1965-12-30 Gen Electric Shaft coupling
FR1273282A (en) * 1960-11-10 1961-10-06 Thomson Houston Comp Francaise Improvements to flexible couplings between machine shafts
GB929323A (en) * 1961-05-17 1963-06-19 Ass Elect Ind Improved flexible coupling particularly for turbine-generator equipment
FR1545229A (en) * 1966-11-24 1968-11-08 Ass Elect Ind Flexible drive device
FR1556727A (en) * 1967-03-15 1969-02-07
JPS4514969Y1 (en) * 1967-06-09 1970-06-24
SE358716B (en) * 1971-10-18 1973-08-06 Stal Laval Turbin Ab
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US4133188A (en) * 1977-07-13 1979-01-09 General Motors Corporation Back-up torque transmitting structure

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0565119A1 (en) * 1992-04-09 1993-10-13 The Japan Steel Works, Ltd. Cutter holder device in a pelletizer
US5358399A (en) * 1992-04-09 1994-10-25 The Japan Steel Works, Ltd. Cutter holder device in a pelletizer
GB2446863A (en) * 2007-02-21 2008-08-27 Smiths Aerospace Ltd Diaphragm coupling with stops to limit range of movement
CN102410312A (en) * 2011-11-15 2012-04-11 西安交通大学 Gear and thin-wall disc combined type coupling
EP2657558A1 (en) 2012-04-27 2013-10-30 Eurocopter Flexible coupling means, and mechanical transmission
FR2990011A1 (en) * 2012-04-27 2013-11-01 Eurocopter France FLEXIBLE COUPLING MEANS AND MECHANICAL TRANSMISSION
US8986127B2 (en) 2012-04-27 2015-03-24 Airbus Helicopters Flexible coupling means and a mechanical transmission
CN103527649A (en) * 2012-07-04 2014-01-22 北京精密机电控制设备研究所 Super high rotating speed safe flexible coupler
US9297790B2 (en) 2012-08-10 2016-03-29 Dionex Softron Gmbh Switching valve for liquid chromatography
US9063114B2 (en) 2012-08-10 2015-06-23 Dionex Softron Gmbh Switching valve for liquid chromatography
US9329157B2 (en) 2012-08-10 2016-05-03 Dionex Softron Gmbh Switching valve for liquid chromatography
US9400265B2 (en) 2012-08-10 2016-07-26 Dionex Softron Gmbh Switching valve for high-performance liquid chromatography
WO2015139999A1 (en) * 2014-03-21 2015-09-24 Avl List Gmbh Shaft with adjustable rigidity
DE102015115948B4 (en) * 2014-10-01 2021-02-04 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Drive shaft with two-stage rigidity
EP3085982A1 (en) * 2015-04-20 2016-10-26 Rolls-Royce plc A shaft assembly comprising a frangible coupling and a flexible coupling
US10344806B2 (en) 2015-04-20 2019-07-09 Rolls-Royce Plc Shaft assembly comprising a frangible coupling and a flexible coupling
GB2537613B (en) * 2015-04-20 2019-05-22 Rolls Royce Plc A shaft assembly comprising a frangible coupling and a flexible coupling
US10267367B2 (en) 2015-08-07 2019-04-23 Airbus Helicopters Flexible coupling means, a mechanical transmission, and an aircraft
US9989099B2 (en) 2016-03-24 2018-06-05 Goodrich Actuation Systems Limited Splined couplings
EP3222868A1 (en) * 2016-03-24 2017-09-27 Goodrich Actuation Systems Limited Splined couplings
US10253822B2 (en) 2016-11-03 2019-04-09 Goodrich Corporation Flexible couplings with angular limiters
EP3321532A3 (en) * 2016-11-03 2018-06-13 Goodrich Corporation Flexible couplings with angular limiters
US11408467B2 (en) 2019-05-03 2022-08-09 Goodrich Corporation Flexible coupling assembly

Also Published As

Publication number Publication date
SE8001102L (en) 1980-08-17
FR2449231A1 (en) 1980-09-12
JPS55112423A (en) 1980-08-30
GB2043207B (en) 1983-04-13
CA1125044A (en) 1982-06-08
CH634133A5 (en) 1983-01-14
IT1130005B (en) 1986-06-11
IT8019688A0 (en) 1980-02-05
DE2934346C2 (en) 1983-03-24
NL8000649A (en) 1980-08-19
DE2934346A1 (en) 1980-08-21

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