DE2354332A1 - SYNCHRONOUS SELF-SHIFTING GEAR CLUTCH - Google Patents

Description

PATB NTASWALT

Dipl. Ing. B. HOLZEE

AUGSBURG

· Ριτττ.ττ » τ» ΐυΒ -WBISBB- SJBA88H IA

R. 866

Augsburg, October 29, 1973

S.S.S. Patents Limited, 51-55 Stirling Road, Acton Town, London W.3, England,

Synchronous, self-shifting tooth clutch

The invention relates to a synchronous self-switching Tooth coupling, with an effective when the rotating coupling parts pass through the synchronism in a relative direction of rotation, one for the purpose of at least partial engagement of the two clutch sprockets inevitably relative to one of the rotating ones Coupling parts having displaceable coupling part

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Operating mechanism and with a device to prevent the disengagement of the interengaged Clutch sprockets.

Couplings of the general type just outlined are usually with or to a ratchet mechanism Equipped with equivalent means that cause the relative rotation of the coupling parts in one sense of rotation Clutch "overtakes" while passing through the clutch parts through the synchronism in the opposite relative direction of rotation of the same, the ratchet mechanism or the means equivalent to it a displacement of the displaceable coupling part in the sense of a precise beginning mutual engagement of the Effect clutch sprockets.

Very often it is required that the clutch also has a device due to the actuation of a Disengagement of the interlocking clutch sprockets is prevented, so that the clutch can then transmit torque in both directions of rotation.

The devices previously provided for this purpose have certain disadvantages. For example, by well-known Facilities of this type the total length of the coupling

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have been enlarged and also need the known facilities by means of a servo mechanism with interposition a shift fork, which complicates the clutch construction.

The invention is intended to solve the problem at Clutches of the general type set out at the beginning provide the device for preventing clutch disengagement Simultaneous simplification of the overall construction so that the overall axial length of the coupling is not is unnecessarily enlarged.

This object is achieved according to the invention by that this device either from the sliding coupling part or by one of the revolving coupling parts held by locking means and either by this one revolving Coupling part or held by the displaceable coupling part inhibiting means, which at least partially engaged clutch sprockets a relative rotational movement around. the coupling axis around between an inhibited condition, in which, because of the axial inhibitory relationship between the inhibiting means and the locking means, disengages the clutch sprockets prevented from performing and a non-inhibiting condition are able to, in which the latter because of the circumstance that

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the blocking means out of axial hemi relation to the locking means disengagement of the clutch sprockets is possible.

The relative rotational movement of the locking means and inhibiting means in terms of producing the inhibiting state can take place automatically under the action of spring force when the clutch sprockets at least partially interlock are indented.

The relative rotational movement of the locking means and the locking means in terms of producing the non-locking State can come about under the effect of pressure medium pressure.

In an exemplary embodiment described below with reference to the accompanying drawings a tooth coupling according to the invention, the spring force is automatically overcome by the said pressure medium pressure, as soon as the clutch reaches a certain speed.

The attached drawings show:

Fig. 1 is a schematic central longitudinal

cut through a synchronous one

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Self-shifting tooth clutch according to the invention, in which the upper half of the piguren shows the clutch in the disengaged state and the lower half of the piguren shows the clutch in the engaged state, _{see FIG}

Figo 2 shows a schematic part-middle

longitudinal section of the coupling shown in Figo 1 _s partially engaged into each other is which the clutch gear rings _s

FIg ₀ 3 a partial section along the

Level IH-III- in Pig -.- I,

Pig. 4 a partial section * Isings the

Ebsne IV = IV in FIG _o 1, and

Figo 5 ". © A partial section along the

Level VV "in Fig _o 2 _O "

When the coupling shown in the drawings has

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a circumferential coupling part on a cylindrical approach, which by means of a flange 1 ^! is attached to a splash 2 of a shaft 3. The cylindrical extension 1 has an inner clutch ring gear 4 and an inner ratchet ring gear 5. Another circumferential coupling part has a sleeve 6 with a flange 6 ', on the outer circumference of which a cylindrical extension 7 is arranged. The sleeve 6 has a right-hand partial external thread 8. The flange 6 'of the sleeve 6 is attached to a flange 10 of a shaft 11, which is designed as an oil catch ring 12, into the annular space of which oil can be injected by means of an injection nozzle 13 from an external oil source. A displaceable coupling part has a sleeve 14 which, by means of an internal partial thread 15, engages in the external partial thread 8 of the sleeve. The sleeve Ik has a coupling outer ring gear and pivot pin 17, on which latter pawls 18 are mounted, which are loaded by loading springs, not shown. The lugs of these pawls 18 point, viewed from the left in FIG. 1, _s in the counterclockwise direction. The sleeve 14 also has a radially outwardly projecting flange 19, on the outer circumference of which a holder 20 for a locking ring is arranged

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cooperates. The holder 20 for the locking ring has radially inwardly projecting projections 22 which are shown in FIG Arcuate recesses 23 protrude into the outer surface of a locking ring 26 and are shown in FIGS. 3 to 5 are visible. The locking ring 26 can rotate relative to the holder 20, this rotational movement through Stops 27 is limited, which are arranged on the holder 20 for the locking ring. The stops -27 protrude radially into recesses 28 of the locking ring 26 and form a sliding fit with them. On the locking ring 26 a locking inner ring gear 29 is arranged.

The cylindrical extension 7 of the rotating coupling part 6 has an outer sprag 30. aside from that radial oil supply bores 31 are arranged in this approach, which via channels 32, 33 and 3 ^ in the coupling part 6 have connection with channels 36 of flange 10, which latter in the annular oil chamber of the oil catch ring 12 open. The annular control slide 21 has channels 37, each at its radially outer ends Connection with one of the recesses 28 in the locking ring 26, while its radially inner ends connection with an annular chamber 38, the latter being formed in the annular control slide 21.

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The arcuate recesses 23 of the locking ring 26 each accommodate compression springs 39, each of which one ends bear against the respective associated projections 22, while their respective other ends each against an end wall of the recesses 23 are in contact. The projections 27 serve as pistons, while the recesses 28 as piston chambers works.

When the clutch is disengaged according to the upper half of FIG. The locking gear rim 29 is engaged in the sprag gear rim 30, as can be seen from FIG. 3. The channels 31 are covered by the inner cylindrical surface 21 ^{f of} the annular control slide.

For the following description of the operation of the clutch it is now assumed that it is in the Wave 3 is a generator shaft, that shaft 11 is the shaft of a gas turbine and that for the purpose of starting the gas turbine from standstill a starter can be coupled to the shaft 3.

First, the generator shaft 3 rotates in the position shown in FIG.

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_{Direction of rotation s} indicated by an arrow so that the pawls 18 engage in the ratchet ring gear 5 and, under the action of the interlocking coarse threads 8 and 15, the sliding sleeve "14 is axially-very robbing relative to the __ 'coupling part 6 (in the upper half of Pig» 1 after is shifted to the right), and thereby the clutch outer ring gear 16 of the socket in a precise preliminary engagement with the internal gear 4 brings _s which on the coupling part 1 is arranged "During this axial-screw riden displacement of the displaceable coupling part Ik also shifts the holder 20 for den'Verriegelungsring axiäl <= to the cylindrical Ansats J in Figure "3 clockwise" Since the locking sprocket 29 and the Hemmzahnkranz 30 is reciprocally engaged Video- _B, the holder 20 for the locking ring to the locking ring 26 in Figo 3 clockwise _s rotated relative 3chraubend relatively whereby the The pressure effect of the compression springs 39 is increased «The teeth of the locking mechanism limgszahnkranzes 29 then slide axially out of engagement with the teeth of the Hemmsahnkranzes _30a whereupon the springs 39 cause the locking ring 26 to the Ηθεϊιε-tooth crane in Figo 3 ii Utesoigersina rotates relative _a so that the teeth of the V @ rri © g @ lungssahnkransei 29 each axially in Durohdeekung with the jamming teeth 30 are _s as shown ie Fig = k "

The gas turbine can now be started by means of the starter, which serves to rotate the shaft 3 in a direction of rotation opposite to the arrow indicated in Pig, I. If the teeth of the locking gear rim and those of the hemia gear rim were not axially overlapped with one another and consequently there was no inhibited state, then the partially interlocked clutch gear rims 4 and 16 would disengage from each other «But because the teeth of the locking gear rim 29 in the axial direction through those of the HeimasaimiD? anzes 50 inhibited ifsrdsn "sine soloh® Ausrttekung apr Kupp lungs is avoided sprockets and the coupling can nunmeta" in one state. in which-they normally "überholsn ^81" twisting moment would be transmitted.

In the Augenfolielc _s in which the gas turbine begins to deliver power ^ causes characterized Iierirorgerufene rotation of the shaft 11 relative sur shaft 5 and the interaction of the partially intermeshing engagement Kupplungsaahnkränze 4 and 16 aufgrüne! üev Eusamaenffektmig der Steilgewiiide 8 ux \ a 15 ®ia® shift of the movable coupling part 14 relatix ⁵⁷ to the coupling part β to the right ^ so that now the clutch gear rim IS fully into the clutch gear rim 4 eißrCiekt® This shift of the

Slidable coupling part Ik has the effect that the teeth of the locking gear rim 30 are relieved of the load of the teeth of the locking gear rim 29 at the end, as the lower half of FIG. 1 shows. During this displacement of the sliding coupling part Ik , the annular chamber 38 of the annular control slide 21 comes into connection with the radial channels 31 and the oil in the oil chamber of the oil collecting ring 12 comes into the channels 31 due to the centrifugal force due to the centrifugal force now increasing the speed of the arrangement the annular chamber 38 and the channels 37 into the piston chambers 28. If the speed of the arrangement increases further, the oil pressure in the piston chambers 28 also increases as a result of the increasing centrifugal force, until at a certain speed the oil pressure in the piston chambers is high enough to generate the force 39 to overcome the springs and k to rotate the locking ring 26 in Fig. counterclockwise to a position in which the projections abut 27 to the end walls of the cutouts 28. If the speed of the gas turbine is now reduced again to below that of the generator, the clutch can disengage because the teeth of the locking gear rim 29 can now engage in the tooth gaps between the teeth of the inhibiting gear rim 30, as shown in FIG. During the clutch disengagement, the

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Channels 31 covered by the cylindrical inner surface 21 of the annular control slide · 21 ₃ so that now the oil supply is cut off to the piston chambers 28th The oil in the piston chambers can flow off through throttled outlet openings 38, this oil drainage being supported by the action of the springs 39, by the displacement of the sliding coupling part 14 in the disengaging direction and by the centrifugal force acting on the oil in the piston chambers 28.

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Claims (5)

Claims I ₀ ) Synchronous self-shifting toothed clutch, with an actuating mechanism that is effective in a relative sense of rotation when the rotating clutch parts pass through the synchronism, an actuating mechanism that is automatically displaceable relative to one of the rotating clutch parts for the purpose of at least partial engagement of the two clutch gears, and with a device for preventing disengagement of the mutually engaged Kupplungssahnkränse ₉ characterized _s that said means ENTX-ieder of the displaceable coupling part (14) or of one (11) of the rotating coupling parts (3 _a 11) held locking means (29) and either by this one revolving coupling part (11) or by the displaceable coupling part (14) held inhibiting means (30), which, when _{the clutch racks (4 S} 16) are at least partially engaged, have a relative rotational movement around the coupling axis, between an inhibited state _s in which is prevented because the axial Hemmbesiehung the blocking means to the Verriegalungsniitteln disengagement of Kupplungszahnkränse _s and a non- 13 - 8819/0389 Able to carry out an inhibiting state in which the latter because of the fact that the inhibiting means are outwardly axial Inhibiting relationship to the locking means are located, disengagement of the clutch rims is possible. 2. Tooth coupling according to claim 1, characterized in that that the locking means comprise a ring with a locking ring gear (29), that furthermore the inhibiting means have a ring with a sprocket wheel (30) and that in the Heiransustand the teeth of the locking ring gear and those of the sprocket in the axial direction overlap at least incompletely, while in the non-locking State these two sprockets can mesh with each other = _S that the relative rotational movement of the locking means (29) and blocking means (30) takes place 3. A toothed coupling of claim 1 or 2, characterized in that for the purposes of producing the Hemmzustandes under the action of spring force (39) automatically _s when the clutch gear rims (4, I6 ) are at least partially indented, 4. Tooth coupling according to one of claims 1 to 3, 409819/0369 characterized in that the relative rotation limitation of the locking means (29) and the inhibiting means (30) in the sense of producing the non-inhibiting state under the effect of a pressure medium pressure (12 _S 36, - 33 »32, 31, 38, 37) comes about. 5. Tooth coupling according to claim 4 _S, characterized in that the relative rotational movement of the locking means (29) and the inhibiting means (30) in the sense of producing the non-inhibiting state takes place automatically when the coupling with at least partially engaged coupling sprockets (4, 16) a reached a certain speed. - 15 - 409 a 19/0369 e e rs e i fa