8 9 BACKGROUND ART 10 11 Thrust reversers that integrate variable exhaust nozzles are known in the art. A typical example of a 12 target reverser with throat adjustment capability is described in US Patent 5181676. It is composed of a fixed 13 structure 34 (reference numbers are those in the patent) commonly called jet pipe, on which are hinged a pair 14 of thrust reverser doors 30 and a pair of shells 44. When the reverser doors 30 are stowed, the pair of shells 15 44 cooperate with the pair of thrust reverser doors to ensure that the exhaust nozzle is planar.

16 The pivots 40 of the reverser doors, which are linked to the corresponding pivots 58 of the shells via 17 arms 56, have the capability of undergoing radial and longitudinal displacements that confer area adjustment 18 capability to the throat of the exhaust nozzle. The nozzle exhaust area variation capability allows, in forward 19 thrust mode, the adjustment of the exhaust area to the particular value required for achievement of optimum 20 performance for the particular flight conditions.

21 In this prior art patent the adjustment of the throat area of the nozzle is performed by actuation 22 means 50, while the deployment of the thrust reverser is performed by different actuation means 52. The use 23 of a dedicated actuation system 50 for the variable nozzle function of the apparatus described has also the 24 advantage of allowing the locking of the thrust reverser door pivots in their most rearward position while the 25 reverser doors, by actuation means 52, are deployed and during their travel from their deployed position to 26 their stowed position.

27 The locking of the reverser door pivots during the stowing mode of the reverser is necessary so that 28 the latch receptacle 66 can re-engage the latch arm 54. If previous mentioned locking of the pivots of the 29 thrust reverser doors is not performed prior to moving the reverser from its deployed position to its stow 30 position, then the dedicated actuation system 52 of the reverser doors would rotate'and forwardly translate the 31 pivots of the reverser and consequently prevent its complete stowing as its latch receptacles 66 would miss 32 their respective target 54.

33 While the use of a dedicated actuation means for varying the area of the exhaust nozzle and the use 34 of a second actuator means for deploying the reverser is mechanically attractive by its simplicity, experience 35 shows that the space required for installation of these dedicated actuation means is often not compatible with 36 the available space.

37 A first desired object is to overcome the drawbacks of prior art jet engine variable nozzles 1 integrated to thrust reversers, and to use the same actuation means for performing the adjustment of the value 2 of the exhaust area of the nozzle and for performing the deployment/stowing of the thrust reverser.

3 A second object is to provide, for forward thrust mode, fixed retainers for keeping the reverser in its 4 stowed position.

5 A third object is to give, for forward thrust mode, the capability to previous fixed retainers to 6 accommodate the longitudinal and radial motions of the reverser nozzle assembly, for adjustment of the value 7 of the exhaust area of the nozzle.

8 A fourth object is to configure previous fixed door retainers such that the reverser doors, for 9 deployment purpose, can only disengage the fixed retainers once the doors have moved downstream of the 10 position corresponding to the value of maximum area of the exhaust nozzle.

11 A fifth object is to provide, in forward thrust mode, a locking means of the position of the reverser 12 nozzle assembly, when the value of the exhaust area of the nozzle is minimum.

13 A sixth object is to provide, in forward thrust mode, a locking means of the position of the reverser 14 nozzle assembly, when the value of the exhaust area of the nozzle has reached its maximum.

15 A seventh object is to allow, for forward thrust mode, the manual setting of the maximum value of 16 the area of the exhaust nozzle.

17 An eighth object is to allow, for reverse mode, a locking means of the position of the reverser door 18 pivots when the reverser door pivots have reached their deployed position, for deployment of the thrust 19 reverser and for a portion of the transit of the reverser from its deployed to its stowed position.

20 A ninth object is to provide an automatic unlocking means of the position of the reverser door 21 pivots, during transit to stow, for completion of the reverser stowing transit sequence, once the reverser door 22 receptacles have re-engaged their respective fixed retainers.

23 A tenth object is to use the thrust reverser doors as the muscle for previous unlocking means.

24 Yet another object is to provide the same, or possibly improved protection against an inadvertent 25 deployment of the reverser compared to the prior art.

26 27 DISCLOSURE OF INVENTION 28 29 A turbofan exhaust nozzle includes a jet pipe having a pair of thrust reverser doors disposed on 30 opposite sides thereof. Each door has a hinge arm joined to a swing arm, which in turn is joined to the pipe.

31 Each door also includes a latching clip at a forward end, and a deployment clevis between the clip and hinge 32 arm. A common actuator is connected to both doors by corresponding links joined to the clevises for driving 33 the links aft to pivot aft the doors and swing arms. A first lock selectively locks the latching clip and a 34 second lock selectively locks the swing arms in coordination with the first lock for permitting variable area 35 axial movement of the doors, thrust reverser deployment thereof, and retraction to stowed positions of the 36 doors.

37

BRIEF DESCRIPTION OF DRAWINGS The invention, in accordance with preferred and exemplary embodiments, together with further objects and advantages thereof, is more particularly described in the following detailed description taken in conjunction with the accompanying drawings in which: Figure 1 is a schematic side view of an integrated variable area-thrust reverser nozzle disposed at the aft end of a turbofan engine, with the upper reverser door shown stowed with minimum nozzle discharge exhaust area, and the lower reverser door shown fully deployed for relative comparison.

Figure 2 is a schematic view of the integrated nozzle shown in Figure 1 illustrating kinematic elements thereof and cooperating forward and aft locking mechanisms.

Figure 3 is an enlarged axial side view of a portion of the nozzle illustrated in Figure 1 with the doors being in the stowed position with minimum nozzle discharge exhaust area.

Figure 4 is a side view of the nozzle, like Figure 3, with the doors being translated aft with a maximum nozzle discharge exhaust area.

Figure 5 is a side view, like Figure 4, with the doors being translated further aft for commencing pivotal deployment thereof for thrust reverse operation.

Figure 6 is a side view, like Figure 5, of engagement of the aft locking mechanism prior to pivotal deployment of the doors.

Figure 7 is a side view, like the aft portion of Figure 6, in which the doors are pivoted aft to the thrust reverser deployed position.

Figure 8 is a side isometric view of the forward locking mechanism of Figures 1-6 shown in isolation in accordance with an exemplary embodiment for locking the reverser doors in their stowed position.

Figure 9 is another isometric view of the forward locking mechanism illustrated in Figure 8 with the doors being locked at maximum nozzle discharge exhaust area.

Figure 10 is a top, plan view of the forward locking mechanism illustrated in Figure 9 and taken along line 10-10.

Figure 11 is a another isometric view of the forward locking mechanism illustrating liberation of a latching clip from the lock.

Figure 12 is an isometric view of an exemplary form of the latching clip illustrated in Figure 11 in isolation.

Figure 13 is an elevational forward-facing-aft view of the forward locking mechanism illustrated in Figure 11 and taken along line 13-13.

Figure 14 is an elevational view of the forward locking mechanism, like Figure 13, as the reverser doors are being stowed.

Figure 15 is a side elevational view of the forward locking mechanism in accordance with an alternate embodiment in which the reverser doors are locked in their stowed position.

Figure 16 is. a side elevational view, like Figure 15, in which the forward locking mechanism permits limited axial movement of the reverser doors for a variable-to-maximum area operation thereof.

Figure 17 is a side elevational view, like Figure 16, in which the reverser doors are liberated from the forward locking mechanism and automatically re-engaged therewith during the stowing sequence.

MODE (S) FOR CARRYING OUT THE INVENTION A planar reverser and variable exhaust area nozzle are combined for turbofan engines. Such an integrated nozzle may be used on business aircraft or commercial aircraft for reducing the noise produced by the engine at takeoff, for optimizing the aircraft takeoff, climb and cruise performance, as well as for decelerating the aircraft at landing. The nozzle can be installed on long nacelles of turbofan engines that are fitted on the fuselage or under the wings of an aircraft.

The thrust reverser nozzle comprises the same actuation means for automatically adjusting the value of the area of the exhaust nozzle for forward mode of operation, and for deploying the thrust reverser for reverse mode of operation. Furthermore, the nozzle comprises at least an upstream fixed thrust reverser doors retainer, at least an upstream locking means of the position of the reverser nozzle assembly, when the value of the exhaust area is minimum or has reached its maximum, at least a downstream locking means of the position of the reverser door pivots once the reverser door pivots have reached their deployed position, and an automatic unlocking of the reverser door pivots locking means, for completion of the stowing sequence and using the thrust reverser doors as a muscle.

The fixed reverser doors retainer is installed on the fixed structure on which is pivotally mounted the reverser nozzle assembly. Its function is to retain and guide, via a guiding track, the rollers of the receptacles of the reverser nozzle assembly in the forward thrust mode to allow the adjustment of the value of the area of the exhaust nozzle, for forward mode of operation.

Furthermore, the guiding track of the reverser doors retainer is configured to allow the disengagement of the receptacle rollers of the reverser doors, so that the reverser doors can be pivotally positioned to their deployed position, only after the reverser doors receptacle rollers has moved away and downstream of the position corresponding to the maximum value of the area of the exhaust nozzle. The guiding track of the thrust reverser doors retainer is also configured to ensure the proper re-engagement of the receptacle rollers during the stowing sequence once the longitudinal position of the reverser door pivots has been unlocked.

The function of the upstream locking means is to provide a mechanical stop to the thrust reverser nozzle assembly for operation in forward thrust mode: 1) provide a mechanical stop to the thrust reverser nozzle assembly when the value of the exhaust nozzle is minimum, and 2) provide a mechanical stop to the thrust reverser nozzle assembly, so that its receptacle rollers cannot pass the position, in their guiding track, that corresponds to the maximum value of the area of the exhaust nozzle.

The upstream locking means can also be manually adjustable, for adjustment of the travel of the 1 reverser door rollers in their guiding tracks, which in turns sets the required maximum value of the area of the 2 exhaust nozzle.

3 The function of the downstream locking means is to provide a mechanical stop to the thrust reverser 4 door pivots, when the reverser door pivots have reached their deployed position for reverser deployment and 5 during stowing transit from the deployed position, until the receptacle rollers have re-engaged their respective 6 track of their corresponding retainer. Once the reverser door rollers have re-engaged their retainers and 7 reached a predetermined position within them, using the reverser doors as muscle, the unlocking means fitted 8 on the reverser doors automatically unlock the downstream locking means of the reverser door pivots, as well 9 as the upstream locking means.

10 This action allows the upstream motion of the reverser nozzle assembly as the receptacle rollers 11 move upstream in their guiding tracks for completion of the reverser nozzle stowing sequence. As the thrust 12 reverser nozzle assembly is driven upstream towards stow, the upstream locking means of the forward thrust 13 position re-lock automatically to prevent the downstream longitudinal motion of the reverser nozzle 14 assembly.

15 The actuation means that control the position of the reverser nozzle assembly can be 16 electro-hydraulic, electro-mechanical, electro-pneumatic or other extendible actuation means. The actuation 17 means of the upstream locking means can also be electro-hydraulic, electro-mechanical, electro-pneumatic or 18 any extendible actuation means. In a preferred embodiment there is a single actuation means on each side of 19 the jet pipe to provide controlled positioning of the reverser nozzle assembly, adjustment of the value of the 20 nozzle exhaust area for forward thrust operation, and deployment of the reverser doors for reverser thrust 21 operation.

22 For forward thrust operation, a method adapts a reverser nozzle assembly mounted on the aft 23 portion of a nacelle installed on a turbofan engine, by varying the value of the nozzle exhaust area for 24 reducing the noise during takeoff and/or for optimizing engine and aircraft performance and by locking the 25 minimum area and maximum area positions of the nozzle for preventing unwanted reverser deployment in 26 flight.

27 For reverse thrust operation, the method includes deploying and stowing the reverser nozzle 28 assembly by locking the longitudinal displacement of the reverser door hinges once they have reached their 29 deployed position, by deploying the thrust reverser doors of the reverser nozzle assembly, by keeping the 30 longitudinal displacement of the thrust reverser door hinges locked during a portion of the thrust reverser 31 transit to stow from its deployed position, and by automatically unlocking the thrust reverser door hinges to 32 allow their longitudinal displacement for completion of the reverser stowing sequence.

33 The exhaust system of US Patent 5181676 disclosed above integrates the thrust reverser with 34 variable area exit nozzle features. The present invention relates to the actuation means and locking means of 35 such a thrust reverser that integrates a variable exhaust area nozzle of the type comprising a fixed structure, 36 two thrust reverser doors, two half exhaust nozzles and a sealing means.

37 The fixed structure, also called jet pipe, is the structure that provides the support for the two thrust

reverser doors, the two half exhaust nozzles, the sealing means, the actuation means, and the locking means.

The fixed structure cooperates radially and longitudinally with the two thrust reverser doors and the two half exhaust nozzles through a sealing means that ensures fluid tightness for forward thrust operation.

However, and as explained above, the apparatus described in US Patent 5181676 uses two specific actuation means. One actuation means is for varying the exhaust area of the nozzle, i. e. , increasing or decreasing the exhaust area in forward thrust operation, while the second one is for deploying the thrust reverser doors.

A single and unique actuation means and method of the present invention allows: 1) the adjustment of the nozzle exhaust area for optimization of engine and aircraft performance, 2) the deployment of the reverser doors for decelerating the aircraft at landing, 3) the automatic locking of the longitudinal displacement of the reverser doors hinges for deployment of the reverser nozzle assembly and for a portion of the transit of the reverser nozzle assembly from its deploy to its stow positions, and 4) the automatic unlocking of the longitudinal displacement of the deployed position of the reverser door hinges by the thrust reverser doors while the doors transit from deploy to stow only after the receptacle rollers of the thrust reverser doors have re-engaged and reached a predetermined position within their respective guiding track.

As shown in Figs. 1 and 2, a turbofan jet engine 1 is equipped with an exhaust system 1A comprising a fixed structure 2 called jet pipe, two thrust reverser doors 3 respectively hinged on pivoting fittings or hinge arms 4 hinged on the jet pipe along pivot axis 5, and two half exhaust shells or nozzles 6 pivotally mounted on trailing arms 7. A pair of common deployment actuators 8 are mechanically attached to opposite sides of the jet pipe, and are also connected via corresponding deployment rods or links 9 to the thrust reverser doors for controlling in forward thrust operation the adjustment of the value of the exhaust area of the nozzle and for deploying in reverse thrust operation the thrust reverser doors.

As commonly used in the art, the following terminology"stow", "deploy"will be used in the description of the integrated nozzle where"stow"depicts a retracted thrust reverser that is in forward thrust configuration (top half of Figs. 1,2), while"deploy"depicts a thrust reverser that is in thrust reverse configuration for decelerating the aircraft at landing (bottom half of Figs. 1,2). Note that Figs. 1,2 have been shown with the top door stowed and the bottom door deployed for clarity of presentation, but in practice both doors travel identically over their full travel paths from stowed to deployed.

A first lock mechanism or locking means 10A includes a fixed retainer 10 attached to the jet pipe 2 configured with two guiding tracks 11, and has the multiple functions of : 1) retaining the thrust reverser nozzle assembly in the stow configuration for whatever value of the area of the exhaust nozzle, 2) requiring additional travel for deployment of the reverser nozzle assembly beyond the position corresponding to the maximum value of the area of the exhaust nozzle and 3) guiding the reverser nozzle assembly while approaching stow during its transit from deploy, so that it can be re-stowed.

Each longitudinal side of the thrust reverser doors is equipped in its upstream end portion with a latching clip or receptacle 12 that houses a latch pin or roller 13. The rollers 13 remain captured by their associated guiding tracks 11 of the retainer 10 for adapting the value of the area of the exhaust nozzle while 1 the reverser nozzle assembly is in stow configuration.

2 With reference to Fig. 3, arms 7 share the same pivoting axis 5 of their corresponding reverser 3 doors hinges 4 and are characterized by having a second lock mechanism or locking means 10B which 4 includes an upstream first locking lever or extension 14. Arms 7 support the half exhaust nozzles 6 while 5 their upstream extensions 14 have the important function of locking any upstream longitudinal motion of the 6 pivots 5 of the reverser doors when the pivots have reached their deployed position and during a portion of 7 the transit of the reverser doors from deploy to stow positions until the rollers 13 have re-engaged and 8 reached a predetermined position within their respective retainers. This particular aspect will become clearer 9 further along the description of this integrated nozzle.

10 With reference to Fig. 3 the reverser nozzle assembly is in forward thrust position, and the value of 11 the nozzle exhaust area is minimum. The reverser nozzle assembly is kept stowed and locked because rollers 12 13 housed by the receptacles 12 are retained by the guiding tracks 11 of retainer 10. The position 13 corresponding to the minimum value of the area of the exhaust nozzle is radially locked by the retainer 10 14 and longitudinally locked by a first stop tab 15 of the upstream locking means or mechanism 10A.

15 With reference to Fig. 3, and although the upstream extensions 14 of arms 7 are free and overlap a 16 downstream second locking lever 16 of the reverser doors hinges 4, the hinges remain locked longitudinally 17 by the first stop 15 of the upstream lock 10A.

18 With reference to Figs. 3,4 a lock actuator 17 of the upstream lock has unlocked the first stop 15 19 corresponding to the minimum value of the exhaust area of the nozzle but not the second stop tab 18 20 corresponding to the maximum value of the exhaust area. The actuator 8 of the thrust reverser nozzle 21 assembly has moved the hinges 4 radially as well as longitudinally via links 9 from their initial first position 22 Pl to the second position P2.

23 The longitudinal displacement of hinges 4 is possible because the pivots are pivotally mounted on 24 pivoting swing arms 20 hinged on the jet pipe along hinge axis 21. Position P1 of the reverser hinges is the 25 position at which the value of the nozzle exhaust area is minimum, and position P2 is the position for 26 maximum value of the nozzle exhaust area.

27 As shown in Fig. 2, during this motion the rollers 13 of the reverser doors have traveled a distance 28"d"in their respective tracks 11 to the second position R2 from their initial first position R1. Position Rl of 29 the rollers 13 corresponds to position PI of the hinges, while position R2 of the rollers corresponds to 30 position P2 of the hinges.

31 With reference to Figs. 2 and 4 the reverser door receptacle rollers 13 are longitudinally prevented 32 from going any further downstream of position R2 in their respective guiding track 11 since the upstream 33 locking means provide the mechanical stop 18 to rollers 22 installed outside receptacles 12 and sharing the 34 same centerline axis with rollers 13. The upstream locking means are pivotally mounted on the jet pipe along 35 an axis 23 that is substantially normal to the axis of their actuator 17 and that is contained in a plane 36 substantially parallel to the plane of symmetry of the reverser doors.

37 In a preferred embodiment, the actuator 17 that controls the rotation of the upstream locking means 1 is a single effect spring loaded actuator. The actuator 17 is only energized when the pivots of the reverser 2 doors are moving from position Pl towards position P2 and from position P2 to third position P3, but not 3 from position P3 to positions P2 and P1. As required for forward thrust operation, for decreasing the noise 4 during takeoff and for optimization of the performance of the engine, hence of the aircraft, the actuator 8 of 5 the reverser nozzle assembly can position the assembly at minimum or maximum value of the exhaust area of 6 the nozzle, without risking unwanted deployment of the reverser doors.

7 The introduction of the upstream first lock 10A and the downstream second lock 10B permits the 8 single actuators 8 on each side of the exhaust nozzle to simultaneously translate the reverser doors 3 for 9 variable area capability thereof, following which the doors may be fully pivoted open for thrust reverse 10 operation, with automatic locking of the swing arms 20. The first locks permit locking of the latching clips 11 12 to prevent pivotal deployment of the reverser doors, while permitting axial movement of the doors 12 between the forward stowed position and the aft intermediate axial position prior to pivotal deployment. The 13 second lock locks the swing arms 20 in their aft pivoted position to prevent forward pivotal movement 14 thereof at the door intermediate position, while permitting pivotal movement of the doors aft for thrust 15 reverser deployment.

16 Figure 3 illustrates the axially forward, stowed position of the reverser doors, with the upstream first 17 lock 10A engaged and the downstream second lock 10B disengaged. The latch pin 13 is locked forward of 18 the first tab 15 in the first axial position Rl, with the swing arm being disposed in its corresponding axially 19 forward position P1.

20 In Figure 4, the lock actuator 17 has been energized to temporarily pivot the two tabs 15,18 away 21 from the guide track 11 for permitting the deployment actuator 8 to drive the reverser doors aft for 22 re-trapping the latch pin 13 between the two stops 15,18 in the intermediate axial position R2.

23 Correspondingly, the swing arm 20 has been pivoted aft to its intermediate position P2, with the two swing 24 arms being colinearly aligned with each other in the radially vertical direction illustrated. This vertical 25 position of the swing arms correspondingly moves outwardly the hinge arms 4 of the reverser doors for 26 achieving the maximum discharge flow area of the exhaust nozzle.

27 Figure 5 illustrates axial translation further aft of the latch pin 13 for clearing the inlet end of the 28 guide track 11 as the second tab 18 is pulled outwardly away therefrom by the actuator 17. The swing arms 29 20 have been correspondingly pivoted to their aft position as the hinge arms 4 reach their aft-most position.

30 Both the first and second locks for the latch pins 13 and swing arms 20 are disengaged.

31 In Figure 6, the deployment actuator 8 further drives the control links 9 aft to begin pivoting 32 deployment of the thrust reverser doors. The latch pins 13 rise from their corresponding guide tracks 11 as 33 the reverser doors are driven radially outwardly to their fully deployed position illustrated in Figure 7.

34 A preferred embodiment of the upstream first lock mechanism 10A is illustrated in Figures 8-13.

35 The first lock configuration illustrated in Figure 8 corresponds with Figure 3 in which the roller head 22 of 36 the latch pin 13 is trapped axially forwardly of the first tab 15.

37 The first lock illustrated in Figure 9 corresponds with Figure 4 in which the roller 22 is trapped 1 axially between the first and second tabs 15,18, with the latch pin 13 being radially trapped in the guide track 2 11.

3 Figure 10 illustrates a top view of the first lock in which the lock actuator 17 is effective for 4 pivoting the two tabs 15,18 outwardly away from the guide track 11 to permit the latch pin and roller 22 to 5 move axially without obstruction by the tabs. Since the actuator 17 is preferably spring-loaded, it may be 6 energized for pulling the tabs away from the guide track 11, and de-energized to permit the internal spring 7 force to return the tabs closely adjacent to the guide track 11.

8 Figure 11 illustrates the radially outer position of the latching clip 12 above the second tab 18 as the 9 reverser door is deployed radially outwardly or radially inwardly.

10 Figure 12 illustrates a preferred form of the latching clip 12 with an integral cam for automatically 11 deflecting the second tab 18 illustrated in Figure 11 as the reverser door is retracted from its pivoted position.

12 This operation is described in more detail hereinbelow, along with Figures 13 and 14 which illustrate 13 automatic displacement of the two stop tabs 15,18 as the reverser door is retracted.

14 With reference to Fig. 4 the upstream locking means are provided with a manual adjustment 15 capability. This is for manually setting the travel of the rollers 13 in their guide tracks 11 in order to 16 determine the value of the maximum area that the exhaust nozzle will be driven to by the actuation means 8.

17 As more clearly shown on Fig. 9 the upstream locking means are substantially composed of two 18 stops tabs, the upstream tab 15 for locking the position that corresponds to the minimum value of the exhaust 19 area, and the downstream tab 18 for stopping the travel of the rollers 22 so that the associated rollers 13 do 20 not pass the position R2 (Fig. 2) that corresponds to the maximum value of the area of the exhaust nozzle.

21 The first mounting plate or fitting 24 that holds the upstream stop 15 is provided with at least two 22 oblong holes 25,26 so that the second fitting plate 27 that holds the downstream stop 18 and that mounts on 23 the first fitting 24 can be longitudinally adjusted manually, via associated bolts 28,29, for setting the value of 24 the maximum area of the exhaust nozzle. The single effect spring-loaded actuator 17 can be 25 electro-hydraulic, electro-mechanic or electro-pneumatic and controls the pivotal motion of the upstream 26 locking plates 24,27. In a preferred embodiment, there are two sets of locking plates 24,27 and their 27 associated tabs 15,18 per reverser nozzle assembly, one inboard and one outboard.

28 With reference to Figs. 2 and 5 for reverser operation, the actuator 17 further rotates the upstream 29 locking means around its axis 23. This unlocks stop 18 of the upstream locking means of the rollers 22 so 30 that the actuator 8 of the reverser nozzle assembly can drive longitudinally the assembly beyond and 31 downstream of the position R2 of the rollers 13 that corresponds to the maximum value of the exhaust area of 32 the exhaust nozzle. The actuators 8 via links 9 have driven the hinges 4 of the reverser doors to their 33 deployed position P3, and the rollers 13 have moved to their third position R3 in their guiding tracks 11. For 34 this position of the reverser nozzle assembly, the rollers 13 are still in contact with the longer inner sides of 35 their associated guiding tracks 11, but are now no longer radially captured by retainer 10 having cleared the 36 shorter top sides of the tracks 11.

37 Also shown in Fig. 5, when the reverser doors hinges 4 reach their deployed position, the supporting

arms 7 of the exhaust nozzle have also moved downstream, longitudinally and radially, since the supporting arms share the same pivoting axis 5 with their respective reverser doors hinges 4. The upstream extensions 14 of arms 7 now uncover the downstream locking levers 16 that are now free to pivot around their upstream pivot axis 30 when the reverser doors 3 are moving from this position towards their deploy position. Axes 30 are substantially parallel to the pivoting axes 5 of the thrust reverser doors 3.

The downstream locking levers 16 pivot away from the longitudinal centerline axis 32 of the actuator 8 as they are spring loaded by leaf springs 31. For this position of the reverser door pivots, the downstream locking means do not yet lock the upstream extension 14 of arms 7. This aspect of the assembly is fundamental as it allows the relocking of the reverser nozzle assembly in the stow configuration when the assembly is moved from its deploy position to its stow position.

As the reverser. nozzle assembly is moving towards its deploy position by actuator 8, and as shown in Figs. 6 and 13, the rollers 13 are radially moving away from their associated guiding tracks 11. For this position of the rollers 13, the reverser doors 3 have further pivoted around their respective axis 5, and the downstream locking levers 16, under the action of their associated springs 31, move further away from the longitudinal axis 32 of the actuator 8, locking the upstream extension 14 of arms 7 and consequently preventing any upstream longitudinal displacement of the reverser door hinges 4.

This aspect of the assembly is also fundamental as it allows the use of the same actuator 8 for varying the value of the exhaust area of the nozzle and for deploying the thrust reverser nozzle assembly.

The actuator 8 can no longer communicate a longitudinal displacement to the hinges 4 of the reverser doors, but only a pivotal motion. Consequently the actuator 8 pivots the reverser nozzle assembly to its fully deployed position as shown on Figs. 1,2, and 7.

With reference to Figs. 2,6, and 13 the actuator 8 is now moving the reverser nozzle assembly from its deploy position towards its stow position. A remarkable aspect of this assembly is that the reverser doors hinges 4 remain in their deploy position P3 as they are still longitudinally locked by the downstream locking levers 16 that prevent the longitudinal forward motion of the upstream extension 14 of the supporting arms 7.

The unlocking means of the downstream locking levers 16 are substantially rollers 34 mounted on the reverser doors, for example on deployment clevises 35 on which are connected one end of the reverser door driving links 9. Since the rollers 13 are still away from their corresponding tracks 11 of retainer 10, and as shown in Fig. 6 the unlocking rollers 34 are just starting to contact the downstream locking levers 16; and the reverser doors hinges 4 cannot yet be longitudinally unlocked, and consequently they remain in position P3.

With reference to Figs. 6 and 11 the receptacles 12 supporting the rollers 13 are moving radially inward towards their stow position. Rollers 13 have now re-engaged the substantially vertical downstream extremity or face 33 of retainer 10. Also the unlocking cam 36 shown in Figs. 11 and 12 that is part of retainers 12 starts to contact the distal-end ramps 37 of stops 18.

As receptacles 12 continue to move inwards toward each other, the unlocking cams 36, through ramps 37 of stops 18, force the upstream locking plates 24,27 which support stops 18,15, to pivot around the 1 axis 23 as shown in Figs. 13 and 14. This allows the automatic or self-unlocking of the upstream locking 2 means without energizing its controlling actuator 17, and consequently the rollers 22 can further move 3 inwards towards each other.

4 With reference to Figs. 6 and 13 it is only when the rollers 13 have reached a predetermined 5 position within the substantially vertical branch of the retainer 10 that the rollers 34 contact the locking levers 6 16 and consequently will be able to push inward to unlock them as the rollers 13 move further inwards 7 toward each other.

8 Once rollers 13 are contacting their associated tracks 11 (Figs. 5 and 14) the downstream locking 9 levers 16 are fully unlocked by the associated unlocking means 34 allowing the actuator 8 to continue the 10 stowing sequence of the reverser nozzle assembly. The rollers 13 continue their upstream travel in their 11 associated guiding tracks 11 to reach position R2 from position R3 while the hinges of the reverser doors 12 move longitudinally from position P3 to position P2 (Fig. 2). The rollers 22 are automatically relocked by 13 stop 18 (Fig. 9).

14 With reference to Figs. 9 and 10 the unlocking cam 36 contacts the back of stop 15 forcing the 15 upstream locking plates 24,27 to rotate around the pivoting axis 23. This allows the automatic unlocking of 16 the upstream locking means without energizing its controlling actuator 17, and consequently, the rollers 13 17 can move from position R2 to position Rl while the reverser door hinges move longitudinally from position 18 P2 to position P1 (Fig. 2). The rollers 22 are then automatically relocked by stop 15 as the spring-loaded 19 actuator 17 returns the displaced plate 24 to trap the roller 22. This completes the stowing sequence.

20 As illustrated schematically in Figure 2, the first lock includes the axial track 11 with an inlet facing 21 aft for receiving the latch pin 13 for radial or lateral retention thereof over the predetermined axial travel 22 provided by the length of the track. The thrust reverser doors may therefore be axially translated for varying 23 nozzle exhaust area as the swing links 20 raise or lower the aft ends of the doors.

24 In Figure 6, when the doors are translated aft to clear the latch pins 13 from the guide tracks 11, the 25 swing arms 20 are axially locked in position by the abutting first and second levers 14,16. The reverser doors 26 may then be pivoted open around the distal ends of the swing arms, without those swing arms themselves 27 moving axially.

28 As shown in Figures 1 and 2, the pair of semi-arcuate nozzle shells 6 are pivotally mounted at the 29 aft ends of the two reverser doors 3 on the corresponding trailing arms 7. The trailing arms in turn are 30 pivotally mounted to the distal ends of the swing arms 20 on the common pivot axes 5.

31 Each of the nozzle shells is additionally joined to the corresponding reverser door by a pair of 32 circumferentially spaced apart follower links 38 pivotally joined at opposite ends thereof for permitting 33 simultaneous deployment of the doors and shells to different positions.

34 As shown in Figure 1, the nozzle shells 6 provide a planar outlet for the engine which reduces drag 35 losses otherwise found in scarfed outlets without such shells. Note that the trailing edges of the reverser 36 doors themselves are scarfed or inclined rearwardly to permit the opposing doors to pivot fully open until the 37 trailing edges thereof come in close contact or abutment with each other.

1 Each of the nozzle shells 6 is linked to a corresponding reverser door by the two trailing arms 7 at 2 the corresponding swing arms, and at the two follower links 38 at the tops of the doors. In this way, the 3 reverser doors may fully deploy while the nozzle shells separately rotate relative thereto. And, when the 4 reverser doors are stowed, the nozzle shells return to their cooperating planar position for defining the 5 discharge outlet or throat for the integrated reverser nozzle.

6 Note that the common swing arms 20 mount both the reverser doors 3 at their hinge arms 4 and the 7 nozzle shells 6 at their trailing arms 7, as shown in Figure 5 for example. The common swing arms 20 8 provide the multiple functions of permitting variable area operation of the nozzle as the swing arms are 9 pivoted forward and aft by axial translation of the reverser doors, followed by reverser door deployment as 10 the hinge arms 4 pivot around the swing arms.

11 The downstream lock provided by the abutting levers 14,16 prevents pivotal movement of the swing 12 arms during reverser door pivotal deployment. Locking of the levers 14,16 is conveniently effected by the 13 leaf springs 31 which bias the second levers 16 radially outwardly toward the corresponding first levers 14 14 extending from the trailing arms 7.

15 By introducing the unlocking roller 34 radially inwardly of the corresponding clevises 35, the rollers 16 34 may simply contact the second levers 34 during retraction of the pivoted doors which uses the doors 17 themselves as the driving force to unlock the two levers 14,16 from each other. The swing arms 20 may then 18 be pivoted axially forwardly as the latch pin 13 at the front end of the doors is guided forwardly in the guide 19 tracks 11.

20 Figures 8-14 illustrate one embodiment of the upstream locking mechanism wherein the mounting 21 plate 24 is joined to the pipe for pivoting outwardly away from the track 11 to permit axial movement of the 22 latch pin along the track.

23 As shown in Figure 8, the first tab 15 is integral with the distal end of the first fitting plate 24, and 24 the second tab 18 is integral with the distal end of the second fitting plate 27. The bolts 28,29 extend through 25 the oblong apertures in the mounting plate 24 for permitting axial adjustment of the location of the second tab 26 18. In this way, the axial spacing between the two tabs 15,18 is adjustable and correspondingly permits 27 adjustment of the axial position of the reverser doors for adjusting the desired maximum discharge flow area 28 of the exhaust nozzle as dependent on the pivoted position of the corresponding swing arms 20.

29 As shown in Figures 10-12, the second tab 18 is disposed aft of the guide track 11, and includes the 30 tip ramp 37 facing outwardly toward the latch pin 13. Correspondingly, the latch clip 12 includes the 31 unlocking cam extension 36 disposed below the latch pin. The cam extends both outwardly and forwardly 32 from the latch clip, and is sized to engage the tip ramp 37 to displace the second tab 18 and mounting plate 33 27 outwardly away from the guide track 11 for receiving the latch pin therein. Figure 13 illustrates the cam 34 36 being driven radially inwardly or downwardly for driving the ramp 37 in the left direction in Figure 13 35 against the closing force of the internal spring of the lock actuator 17.

36 In Figure 14, the cam 36 displaces the second stop 18 suitably away from the roller 22 at the distal 37 end of the latch pin 13 to permit entry of the latch pin into the guide track 11.

1 As the reverser door is driven forwardly by the deployment actuator 8, the latch pin and the roller 22 2 as illustrated in Figure 10 will move forwardly of the aft tab 18, with the cam 36 then engaging the inner 3 surface of the forward tab 15 for maintaining outwardly the first tab 15 away from the guide track 11 to 4 permit further axially forward movement of the latch pin and roller. As soon as the cam 36 clears the forward 5 end of the forward tab 15, the internal spring of the lock actuator 17 returns the first and second tabs 15,18 to 6 their original position adjacent the guide track 11, which locks the first tab 15 axially behind the latch roller 7 22.

8 Figures 15-17 illustrate an alternate embodiment of the forward locking mechanism or means in 9 which a mounting plate 24a is joined to the jet pipe for lateral pivoting movement in the radial or vertical 10 direction below the corresponding guide track 11 for permitting axial movement of the latch pin 13 along the 11 track. In this embodiment, the first and second stop tabs 15a, 18a are integral with the mounting plate 24a in a 12 unitary construction therewith, and are formed by corresponding ramps 37a, b and notches therein. Each 13 mounting plate 24a therefore has a generally sawtooth-type configuration.

14 In this embodiment, the guide track 11 is arcuate as best illustrated in Figure 17, and the 15 corresponding ramps 37a, b adjacent the notch tabs 15a, 18a are similarly arcuate for permitting axial travel of 16 the latch pin along the ramps and track.

17 In Figure 15, the lock actuator 17 includes an internal spring for biasing the output rod thereof in its 18 extended, axially aft position. The actuator rod includes a pulley wheel at its distal end which engages 19 corresponding tongues of the mounting plate 24a. The latch pins 13 are initially trapped by the first notch 20 tabs 15a in the fully stowed position of the reverser doors, having minimum discharge exhaust area.

21 Upon energizing the actuator 17 as shown in Figure 16, its output rod is driven forward to pivot 22 inwardly the two fitting plates 24a for permitting the latch pins 13 to clear the first notch tabs 15a to enter the 23 corresponding ramps 37b. The second notch tabs 18a prevent further axial travel of the latch pins 13, and 24 maintain the axial position of the reverser doors at the desired maximum discharge area.

25 By again energizing the actuator 17 as illustrated in Figure 17, the fitting plates 24a are further 26 pivoted radially inwardly to free the latch pins 13 from the second notch tabs 18a to reach the downstream 27 ramps 37a. In this position, the latch pins 13 are free to leave the axial extent of the guide tracks 11 for 28 permitting pivotal deployment of the reverser doors to their thrust reversal positions.

29 After thrust reverse operation, the doors are pivoted radially inwardly, with the corresponding latch 30 pins 13 first engaging the ramps 37a illustrated in Figure 17 for automatically displacing radially inwardly the 31 fitting plates 24a without the need for energizing the actuator 17. In this way, the reverser door driven by the 32 deployment actuator 8 automatically opens the upstream lock for permitting the latch pin 13 to enter the 33 guide track 11 as it travels axially forwardly.

34 The pin then reaches the second ramp 37b illustrated in Figure 16 and continues to be driven axially 35 forwardly along the guide track 11. Once the pin 13 reaches the first notch tab 15a as shown in Figure 15, 36 the internal spring of the actuator 17 drives the fitting plate 24a radially outwardly to trap and lock the latch 37 pin 13 in its forwardmost axial position associated with stowed position of the reverser doors.

1 In the corresponding embodiments of the forward locking mechanism illustrated in Figures 6-17, the 2 first and second stop tabs thereof are spring loaded by actuator 17 to lock the latch pin 13 in the stowed, 3 minimum area position of the reverser doors, and in the radially locked, maximum discharge area position of 4 the doors. Correspondingly, the two levers 14,16 of the aft locking mechanism illustrated in Figure 6 are also 5 spring loaded to lock the swing arms 20 in their aft pivotal positions for reverser door pivotal deployment.

6 In both embodiments of the forward locking mechanism, those mechanisms are configured for 7 automatically unlocking the first and second tabs 15,18 during the stowing sequence of the doors using the 8 latch clips to displace the tabs against the spring loads thereon. Complete retraction of the reverser doors 9 from their deployed position may therefore be achieved without energizing the lock actuator 17.

10 In contrast, the lock actuator 17 must be energized for deploying the thrust reverser doors by 11 selectively displacing the first and second tabs away from the latch pins for permitting axially aft travel of the 12 door.

13 The cooperating levers 14,16 of the aft locking mechanism are also configured as described above 14 for automatic engagement with each other to lock the swing arms 20 during pivotal deployment of the doors.

15 Correspondingly, the two levers 14,16 cooperate with the rollers 34 for automatically disengaging the levers 16 to unlock the swing arms 20 during pivotal stowing of the doors.

17 In this way, positive actuation of the lock actuator 17 is required for deploying the thrust reverser 18 doors during landing operation of the aircraft being powered by the engine. However, locking of the swing 19 arms during door deployment is automatic; unlocking of the swing arms during door retraction is also 20 automatic; and, relocking of the latch pin 13 behind the two stop tabs 15,18 is also automatic during 21 retraction of the doors to their stowed position.

22 As illustrated schematically in Figure 2, the guide tracks 11 in the upstream lock mechanism have 23 an axial length corresponding with the axial travel of the latch pins 13 and swing arms 20 between the aft 24 position thereof R3, P3 and the forward position thereof R1, P1 for permitting disengagement of the latch pin 25 from the guide track only after the swing arm is suitably deployed aft. In this way, the upstream and 26 downstream locking mechanisms are configured for coordinated locking of the latch pins 13 and the swing 27 arms 20 to permit selected axial deployment or travel of the doors while the upstream lock mechanism 28 engages the latch pins 13, and permitting pivotal deployment of the doors while the downstream lock 29 mechanism engages the swing arms 20.

30 In the preferred embodiment illustrated in Figure 2, the swing arms 20 extend outwardly opposite 31 from each other toward the opposite doors 3, and include a forward inclined position P1 corresponding with 32 the stowed position of the doors and latch pin (Rl), with the nozzle having the minimum discharge flow area.

33 The swing arms also have an intermediate, colinear radially aligned position P2 corresponding with the aft 34 travel of the doors and latch pin (R2) having a maximum discharge flow area of the nozzle. The aft inclined 35 position P3 of the swing arms corresponds with pivotal deployment of the doors during thrust reversal.

36 The guide track 11 illustrated in Figure 2 has an axial length configured for laterally or radially 37 retaining the latch pin 13 as the doors are axially translated between the stowed and intermediate positions

(R1, R2), with the upper side of the track terminating to radially liberate the latch pin as the doors translate further aft to the aft position (R3).

The coordinated positions of the latch pin and swing arm in the door stowed position (R1, P1), maximum discharge area position (R2, P2), and pivotal deployment position of the doors (R3, P3) is readily coordinated by the configuration of the guide track 11 and the pivotal range of the swing arms 20. The latch pin 13 is correspondingly locked in the guide track 11, and the swing arms are correspondingly locked in their aft positions as required for coordinating the deployment and retraction sequences of the thrust reverser doors.

Accordingly, a single deployment actuator 8 is used on each side of the integrated nozzle for simultaneously deploying both reverser doors 3 with controlled movement, notwithstanding the additional rotary movement provided by the swing arms 20. The swing arms are locked when required during pivotal deployment of the doors, and unlocked when required during axial deployment and retraction of the doors.

Correspondingly, the forward ends of the doors are locked at the latch pins by the forward lock mechanisms, with controlled axial movement within the corresponding guide tracks 11.

While there have been described herein what are considered to be preferred and exemplary embodiments of the present invention, other modifications of the invention shall be apparent to those skilled in the art from the teachings herein, and it is, therefore, desired to be secured in the appended claims all such modifications as fall within the true spirit and scope of the invention.