• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:FR3017669A1
    申请号:FR1551447
    申请日:2015-02-20
    公开日:2015-08-21
    发明作者:David G Bannon
    申请人:Hamilton Sundstrand Corp；
    IPC主号:
    专利说明:

    [0001] This disclosure relates to a system for deploying and storing a dynamic air turbine, and more particularly, disclosure relates to an actuator for the system. BACKGROUND OF THE INVENTION [0002] A dynamic air turbine (RAT) is a device for producing an additional electric power in case of emergency on many aircraft to provide a hydraulic and electrical power supply. The RAT is stored in the aircraft structure and is deployed in the airflow by an actuator. The actuator is attached to the structure of the aircraft and on one arm on the amount of the RAT. During deployment, the deployment actuator forces the RAT to deploy from its stowed position, or retracted into the aircraft to position itself in the airflow. The airflow acts on the blades of the RAT to rotate the turbine and regulator assembly, which in turn operates an electric generator and a hydraulic pump to power the plane When not needed, the In one aspect, an actuator for a RAT system includes a piston rod which is cylindrical in shape and which is centered around a central line and is provided with an actuator for a RAT system. a plurality of locking wedges supported by the piston rod and which can move radically. The actuator also includes a locking pin which extends along the center line radially inside the piston rod and the locking pin being axially displaceable within the piston rod between a stored position and an extended position and a plurality of rollers extending radially outwardly of the centerline and guided by the locking pin. The actuator comprises radially a slideway between at least a portion of the locking pin which is adjacent to the rollers and the piston rod comprising the slideway being axially displaceable between a stop position and an extended position and the stop position being axially between the deployed position and the stored position.
    [0002] The actuator also includes a cylinder that extends radially outwardly from the piston rod and the cylinder is axially movable between a stowed position and an extended position. The actuator is locked in the stowed position when the locking pin, slider and cylinder move axially to position the rollers radially inwardly from the locking wedges so that the rollers push the locking wedges radially to the in an opening adjacent one end of the cylinder and prevent the locking pin, the slide and the cylinder from moving axially. In another aspect, a component that is to be used in an actuator in a RAT comprises a piston, a cylinder, a locking pin extending along the center line, and the locking pin being axially displaceable along the central line between a stowed position and an extended position, and a plurality of rollers which extend radially outwardly from the center line and which is guided by the locking pin. The component also comprises a slideway radially between at least a portion of the locking bolt and a piston rod having the slideway which is axially movable between a stop position and an extended position and the stop position being axially between the deployed position. and the stowed position and locking wedges supported by the piston rod. The locking pin and the slide are axially movable within the piston rod and the actuator is locked in the stored position when the locking pin and the slide axially move within the piston rod and a cylinder for positioning the rollers to push the locking wedges radially outwardly into an opening adjacent to one end of the cylinder and to prevent axial movement of the locking pin, slider and cylinder. BRIEF DESCRIPTION OF THE FIGURES [0005] FIG. 1 is a perspective view of the RAT system in an extended position. [0006] FIG. 2A is a perspective view of the actuator of FIG. 1 in a row position. [0007] FIG. 2B is a sectional view of the actuator of FIG. 1 in a row position. [0008] FIG. 2C is an enlarged view of the actuator of FIG. 1 in a row position. [0009] FIG. 3A is a sectional view of the actuator in the deployed position. [0010] FIG. 3B is an enlarged view of the actuator in the deployed position. [0011] FIG. 4A is a sectional view of the actuator in an almost row position. [0012] FIG. 4B is an enlarged view of the actuator in an almost row position. [0013] FIG. 5 is an enlarged view of the actuator in a stored and locked position. DETAILED DESCRIPTION 100141 FIG. 1 is a perspective view of the RAT system 10 in an extended position. The RAT system 10 is attached to the structure of the aircraft 12 by a housing 14. The housing 14 pivotally supports an upright 16 having the turbine 18 at one end. The turbine 18 comprises the blades 20, which communicate a rotation drive to the electric generator 22 and the hydraulic pump 30. The actuator 24 is fixed to the upright 16 at the first end 26 and the housing 14 at the second end 28. L actuator 24, as illustrated in FIGS. 2A and 2B, is illustrated in an extended position in FIG. 1. [0015] FIG. 2A is a perspective view of the actuator 24 of FIG. 1 in a stowed position, FIG. 2B is a sectional view of the actuator 24 of FIG. 1 in a stowed position, and FIG. 2C is an enlarged view of the actuator 24 of FIG. 1 in a row position.
    [0003] The actuator 24 comprises a housing 32 having a first cylinder 34 and a second cylinder 36, which are not fixed to the housing 32 and which are in a telescopic arrangement relative to each other. A deployment spring 38 is radially outwardly from and between the ends of the first cylinder 34 and the second cylinder 36 and is in a compressed state when the actuator 24 is in a stowed position. Latches 40 are located near the second end 28 and serve to activate and initiate the deployment of the RAT system 10 through the extension of the actuator 24. [0016] The second cylinder 36 is received in the first cylinder 34 when the actuator 24 is in the stowed position. The piston rod 42 is fixed to the housing 32 so that the piston rod 42 is rigidly attached to the first cylinder 34 so that the second cylinder 36 slides between and with respect to the piston rod 42 and the first cylinder 34 when it extends into an extended position or retracts into a stowed position. The piston rod 42 is not removable relative to the first cylinder 34, and the second cylinder 36 slides axially along the radial outer side of the piston rod 42 when the actuator 24 is deployed or stored. The piston rod 42 comprises a first opening 44 and a second opening 46, which respectively receive the locking wedges 48 and the unlocking wedges 50. The locking wedges 48 and the unlocking wedges 50 may have an annular shape or may be a plurality of wedges / pawls circumferentially disposed around the piston rod 42. The locking pin 52 and the slideway 53 (which is radially outwardly from a portion of the locking pin 52) are disposed of slidingly inside the piston rod 42 and are configured to activate the locking wedges 48 to lock the actuator 24 in a stowed position and to activate the unlocking wedges 50 to lock the actuator 24 in an extended position . The piston rod 42 comprises a flange 58, which is spaced from the collar 60. The spring of the locking pin 54 is located between the flange 58 and the collar 60, and in contact therewith, to keep the rod 42 and the locking pin 52 along the center line A. [0018] The set of rollers 56 comprises a plurality of rollers 76, which are guided by the locking pin 52 and arranged radically between the locking pin 52 and the locking pins 52. locking blocks 48 when the actuator 24 is in the stowed position. When not in the stowed position, the set of rollers 56 is located radically between the locking pin 52 and the piston rod 42. The rollers 76 are circumferentially spaced around the portion of the locking pin 52 which guides the rollers 76 and which may have a cylindrical shape. During operation, to initiate the deployment of the RAT system 10, the locking pin 52 and the slide 53 can move axially (to the right in FIGS.
    [0004] 2B and 2C) in response to the pushing force from the spring of the locking pin 54, which is free to act on the locking pin 52 and the slide 53 due to the unlocking of the latches 40. The movement of the assembly of rollers 56 (to the right in FIG.
    [0005] 2B and 2C) allows the locking blocks 48 to move radially inwardly and disengage from the second cylinder 36, thereby allowing the second cylinder 36 to move axially away from the first cylinder 34 and the stem. piston 42 due to the force exerted on the second cylinder 36 by the deployment of the spring 38. The deployed actuator 24 is illustrated in FIG.
    [0006] 3A. [0020] FIG.
    [0007] 3A is a sectional view of the actuator 24 in the extended position, while FIG 3B is an enlarged view of the actuator 24 in an extended position. The actuator 24 includes (among the features described in FIGS.
    [0008] 2A, 2B, and 2C), a first end 26 adjacent to a second cylinder 36 and a second end 28 adjacent a first cylinder 34. The actuator 24 also includes a piston rod 42, which is stationary relative to the second end 28 and a first cylinder 34. Radially outwardly from the piston rod 42 is a second cylinder 34, which moves axially along the piston rod 42. The piston rod 42 comprises a first opening 44 and a second opening 46, which respectively receive the locking wedges 48 and the unlocking wedges 50. The locking wedges 48 comprise, on the radial inner side, a tapered internal surface 49. [00211 Radially inside the piston rod 42 is a slide 53, which is removable inside the piston rod 42 and activates the unlocking wedges 50 to lock the actuator 24 in an extended position by pushing the unlocking wedges 50 drastically outward. Between the piston rod 42 and the slideway 53 is at least one slide seal / a first seal 78 (shown in FIG.
    [0009] 3B). The first seal 78 has an annular shape and prevents the liquid from moving between a first end 26 and a second end 28 through a hole between the piston rod 42 and the slide 53. Between the piston rod 42 and the slide 53 there is also a stop 82, which prevents the slide 53 from coming into contact with the locking wedges 50 (discussed in more detail with respect to FIGS.
    [0010] 4A, 4B and 5). Radially inside the slideway 53 is a portion of the locking pin 52, which is removable within the slideway 53 and the piston rod 42. The locking pin 52 extends from a second end 28 to a set of rollers 56 and guide the rollers 76. Between the locking pin 52 and the slideway 53 is at least one lock pin joint / a second seal 80. The second seal 80 has an annular shape and prevents the liquid to move between a first end 26 and a second end 28 through a hole between the locking pin 52 and the slide 53. [0020] As mentioned with respect to FIG.
    [0011] 2A and 2B, the deployment spring 38 drives the second cylinder 36 in an axial movement away from the first cylinder 34. The deployment spring 38 extends the actuator 24 until the second cylinder 36 is located such that so that the unlocking pins 50 are radially inside the groove 51 in the second cylinder 36. The groove 51 is close to the end of the second cylinder 36 which is adjacent to the first cylinder 34. When the deployment spring 38 has caused the movement of the first cylinder 34 and the second cylinder 36 until the unlocking wedges 50 reach the groove 51 in the second cylinder 36, the actuator 24 is in an extended position. After deployment of the actuator 24 in an extended position, the actuator 24 is locked in place by the unlocking wedges 50, which are pushed radially outward in the groove 51 by the tapered portion 84 of the slide 53 when the locking pin 52 and the slide 53 move axially away from the first end 26 (to the right in FIGS.
    [0012] 3A and 3B). When locked in an extended position, the unlocking wedges 50 are on the radial outer side of the second opening 46 in the groove 51 in the second cylinder 36. Since the unlocking wedges 50 are within the groove 51, the axial movement of the second cylinder 36 is prevented and the actuator 24 is locked in an extended position.
    [0013] The slide 53 is axially displaced away from the first end 26 upon deployment by contact with a stair shaped portion 86 of the locking pin 52, which is configured to move the slide 53 into an extended position but which does not move the slide 53 to a stowed position. Instead, the slide 53 is configured to slide the locking pin 52 into a locked position due to the contact between the slide 53 and the locking pin 52 (as will be presented with respect to FIGS.
    [0014] 4A, 4B and 5). [0025] FIG.
    [0015] 4A is a sectional view of the actuator 24 in an almost tilted position, while FIG 4B is an enlarged view of the actuator 24 in an almost tilted position. To move the actuator to a stowed position from an extended position, pressure is introduced into the actuator 24. This pressure may be caused by a gas or other fluid being pumped into the actuator 24. The pressure moves the second cylinder 36 toward the first cylinder 34 by creating a volume between the piston rod 42 and the second cylinder 36 to extend axially and push the second cylinder 36 toward the first cylinder 34 (to the right in FIGS.
    [0016] 4A and 4B). The pressure also moves the locking pin 52 and the slide 53 in a direction opposite to the movement of the second cylinder 36 by creating a volume within the piston rod 42 to axially extend and push the slide 53 (which in turn pushing the locking pin 52 due to the stair shaped portion 86 in the locking pin 52) towards the first end 26. The pressure in the actuator 24 pushes the first seal 78, causing the slide 53 to move to the locking wedges 48 until the slide 53 engages the abutment 82 (located on the piston rod 42), which prevents the slideway 53 from contacting the locking wedges 48. [0026 The pressure also pushes the second seal 80, causing the locking stud 52 to move toward the locking wedges 48 and continuing to move toward the locking wedges 48 even after the slide 53 is self-locking. It is possible for the rollers 76, which are supported by the locking pin 52, to push the locking wedges 48 radially outwardly through the contact with a tapered inner surface, see FIG. 49 (see FIG. 5). In the disclosed application, the contact between the slide 53 and the stop 82 (which prevents the slide 53 from moving towards the locking wedges 48) absorbs the excess force generated by the pressure on the first seal 78 and reduces the force that moves the locking pin 52 and the rollers 76 to the locking wedges 48. Thus, the force that moves the locking pin 52 to the locking wedges 48 (after the slide 53 has come into contact with the the stop 82) can only be applied to a second seal 80. The second seal 80 may have a smaller area than the area of the previous seals on the lock pin 52, so that less force is applied to the locking pin 52 (because the force is equal to the pressure multiplied by the area, so if the area decreases then the force decreases). The decrease in the area of the seal results in a decrease in the contact force between the rollers 76 and the locking shims 48 and reduces the damage to the lock blocks 48 and / or the rollers 76 caused by the excess force. The force acting on the second seal 76 must be sufficiently small not to damage the locking wedges 48 and the rollers 76 while being large enough to allow the locking pin 52 and the rollers 76 to force the radially tapered locking blocks 48. outward and place the actuator 24 in a stowed position (as shown in FIG 5). [0028] FIG. 5 is an enlarged view of the actuator 24 in a stored and locked position. The actuator 24 of FIG. 5 is fully retracted and is locked in place by the locking wedges 48. When locked in a stowed position, the locking wedges 48 are on the radial outer side of the first opening 44 adjacent the second cylinder 36 close to the first end 26. Since the locking wedges 48 are adjacent to a second cylinder 36 (the locking wedges 48 are adjacent the end of the second cylinder 36 which is closest to the first end 26), a movement axial axis away from the first cylinder 34 of the second cylinder 36 is prevented and the actuator 24 is locked in a stowed position. Locking wedges 48 are pushed outwardly in a stowed and locked position by the rollers 76 (in contact with the tapered inner surface 49) which are guided by the locking pin 52 at the set of rollers 56. The locking pin 52 positions the rollers 76 to be in a stowed position by moving independently of the slideway 53 after the slide 53 has come into contact with the stopper 82 (and its continuous movement towards the locking wedges 48 is prevented). As mentioned above, the configuration of the locking pin 52 and the slide 53 reduces damage to the locking wedges 48 and the rollers 76 due to the force used to store the actuator 24 caused by the pressure introduced into the actuator 24. The damage reduction extends the life of the actuator 24 and reduces the need for maintenance. This configuration can be implemented in newly manufactured actuators or can be installed in actuators manufactured according to the previous models. Discussion of Possible Embodiments [0031] The following are non-exclusive descriptions of possible embodiments of the present invention. An actuator of a dynamic air turbine system may comprise a piston rod which has a cylindrical shape and which is centered around a central line; a plurality of locking wedges supported by the piston rod and movable radially; a locking pin which extends along a central line radially inside the piston rod, the locking pin being axially displaceable within the piston rod between a stowed position and an extended position; a plurality of rollers which extend radially outwardly from the center line and which are guided by the locking pin; a slideway radially between at least a portion of the locking pin which is adjacent to the rollers and the piston rod, the slideway being axially displaceable between a stop position and an extended position, the stop position being axially between the position deployed and stowed position; a cylinder extending radially outwardly from the piston rod, the cylinder being axially displaceable between the stowed position and the extended position, wherein the actuator is locked in the stored position when the locking stud, the slide and the cylinder move axially to position the rollers radially inwardly from the locking wedges so that the rollers push the locking wedges radially outwardly into an opening adjacent one end of the cylinder and prevent the locking stud, slide and cylinder to have axial movement. The actuator of the preceding paragraph may optionally comprise, in addition and / or alternatively, one or more of the following additional elements, features and / or configurations: [0034] A first annular seal between the slideway and the piston rod and a second annular seal placed between the locking pin and the slide. The pressure applied to the first annular seal causes axial movement of the slide and the locking pin until the slide is in the off position. The pressure applied to the second annular seal causes movement of the locking pin until the actuator is locked in a stowed position. A stop on the piston rod at the stop position close to the locking wedges, the stop preventing the slide to move towards the locking wedges but allowing the locking pin to continue its movement towards locking wedges. The pressure applied to the first annular seal and the second annular seal causes movement of the slide and the locking pin until the slide 20 contacts the stop and then allows only the locking pin of move until the rollers are inside the locking wedges. An inner surface of the locking wedges is tapered. The actuator is not locked in a locked position when the rollers are not radially inward relative to the locking wedges. [0041] A component that is to be used in an actuator in a dynamic air turbine may comprise a piston; a cylinder; a locking pin extending along a center line, the locking pin being axially displaceable along the center line between a stowed position and an extended position; a plurality of rollers which extend radially outwardly from the center line and guided by the locking pin; a slideway radially between at least a portion of the locking pin and the piston rod, the slide being axially displaceable between a stop position and an extended position, the stop position being axially between the deployed position and the stored position; and locking wedges supported by the piston rod, wherein the locking pin and the slide are axially displaceable within the piston rod and the actuator is locked in a stowed position when the locking pin and the slide axially move within the piston rod and the cylinder to position the rollers to urge the locking wedges radially outwardly into an opening adjacent one end of the cylinder and to prevent the locking pin, the slide, and the cylinder to have an axial movement. The component of the preceding paragraph may optionally comprise, in addition and / or alternatively, one or more of the following additional elements, features and / or configurations: [0043] A first annular seal located radially outward from the slide is a second annular seal placed between the locking pin and the slide. The pressure applied on the first annular seal causes axial movement of the slide and the locking pin until the slide is in the off position. The pressure applied to the second annular seal causes movement of the locking pin until the actuator is locked in a stowed position. [0046] A stop located at the stop position close to the locking wedges, the stop preventing the slide from having a movement towards the locking wedges but allowing the locking pin to continue its movement towards the locking wedges. . The pressure applied to the first annular seal and the second annular seal causes movement of the slide and the locking pin until the slide contacts the stopper and then allows only the locking pin to engage. move until the rollers are inside the locking wedges. [0048] An inner surface of the locking wedges is tapered. Although the invention has been described with reference to one or more exemplary embodiments, those skilled in the art will understand that various modifications may be made to the elements described herein, and equivalents may be used in their place without deviate from the scope of the invention. In addition, several modifications may be made to adapt a given situation or material to the teachings of this invention without departing from the essential scope thereof. Thus, it is contemplated that this invention is not limited to the particular disclosed embodiment (s), but that this invention will include all embodiments that are within the scope of the invention described above.
    权利要求:
    Claims (15)
    [0001]
    Claims: 1. An actuator for a dynamic air turbine system comprising: a piston rod which is cylindrical in shape and centered around a centerline; a plurality of locking wedges supported by the piston rod and movable radially; a locking pin which extends along the center line radially inside the piston rod, the locking pin being axially displaceable within the piston rod between a stowed position and an extended position; a plurality of rollers extending radially outwardly from the center line and guided by the locking pin; a slideway radially between at least a portion of the locking pin which is adjacent to the rollers and the piston rod, the slideway being axially displaceable between a stop position and an extended position and the stop position being axially between the deployed position and the stowed position; a cylinder which extends radially outwardly from the piston rod, the cylinder being axially movable between the stowed position and an extended position. wherein the actuator is locked in a stowed position when the locking pin, slider and cylinder move axially to position the rollers radially inwardly from the locking wedges so that the rollers push the locking wedges radially outwardly into an opening adjacent one end of the cylinder and prevent the locking pin, the slide and the cylinder from moving axially.
    [0002]
    An actuator according to claim 1, further comprising: a first annular seal located between the slideway and the piston rod; and a second annular seal located between the locking pin and the slide. 5
    [0003]
    3. The actuator of claim 2, wherein pressure applied to the first annular seal causes axial movement of the slide and the locking pin until the slide is in the off position.
    [0004]
    4. The actuator according to claim 2 or 3, wherein the pressure applied to the second annular seal causes movement of the locking pin until the actuator is locked in a stowed position.
    [0005]
    An actuator according to any one of claims 2 to 4, further comprising:
    [0006]
    The actuator according to claim 5, wherein the pressure applied to the first annular seal and the second annular seal causes movement of the slide and the locking pin until the slide contacts the stop and Then only allows the locking pin to move until the rollers are inside the locking wedges.
    [0007]
    7. The actuator according to any one of claims 1 to 6, wherein the inner surface of the locking wedges is tapered. 25
    [0008]
    8. The actuator according to any one of claims 1 to 7, wherein the actuator is not locked in a stowed position when the rollers are not radially inward with respect to the locking wedges.
    [0009]
    9. A component to be used in an actuator of a dynamic air turbine comprising: a piston rod; a stop on the piston rod at the stop position close to the locking wedges, the stop preventing the slide from moving towards the locking wedges but allowing the locking pin to continue its movement towards the wedges of the lock. locking. A cylinder; a locking pin extending along a center line, the locking pin being axially displaceable along a center line between a stowed position and an extended position; a plurality of rollers extending radially outwardly from the center line and guided by the locking pin; a slideway between at least a portion of the locking pin and the piston rod, the slide being axially displaceable between a stop position and an extended position, the stop position being axially between the deployed position and the stored position; locking wedges supported by the piston rod, wherein the locking pin and the slide are axially displaceable within the piston rod and the actuator is locked in the stored position when the locking pin and the slide move axially within the piston rod and the cylinder to position the rollers to push the locking wedges radially outwardly into an opening adjacent one end of the cylinder and to prevent axial movement of the locking pin, the slide and cylinder.
    [0010]
    The component of claim 9, further comprising: a first annular seal located radially outwardly from the slideway and a second annular seal located between the locking pin and the slideway.
    [0011]
    The component of claim 10, wherein the pressure applied to the first annular seal causes axial movement of the slide and the locking pin until the slide is in the off position.
    [0012]
    The component of claim 10 or 11, wherein the pressure applied to the second annular seal causes movement of the locking pin until the actuator is locked in a stowed position.
    [0013]
    13. Also: Component according to any one of claims 10 to 12, comprising a stop located at the stop position close to the locking wedges, the stop preventing the slide from having a movement towards the locking wedges but allowing to the locking pin to continue its movement towards the locking wedges.
    [0014]
    The component of claim 13, wherein the pressure applied to the first annular seal and the second annular seal causes movement of the slide and the locking pin until the slide contacts the stop and then allows only to the locking pin to move until the rollers are inside the locking wedges.
    [0015]
    The component of any one of claims 9 to 14, wherein the inner surface of the locking wedges is tapered.
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    同族专利:
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    EP3112270B1|2015-06-29|2019-09-04|Hamilton Sundstrand Corporation|Unlocking mechanism for ram air turbine actuator|
    FR3042237B1|2015-10-09|2017-11-03|Labinal Power Systems|ACTUATING DEVICE FOR AN AIRCRAFT EMERGENCY WIND SYSTEM|
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    法律状态:
    2016-01-22| PLFP| Fee payment|Year of fee payment: 2 |
    2017-01-24| PLFP| Fee payment|Year of fee payment: 3 |
    2017-09-01| PLSC| Publication of the preliminary search report|Effective date: 20170901 |
    2018-01-23| PLFP| Fee payment|Year of fee payment: 4 |
    2020-01-22| PLFP| Fee payment|Year of fee payment: 6 |
    2021-01-20| PLFP| Fee payment|Year of fee payment: 7 |
    2022-01-19| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    US14185405|2014-02-20|
    US14/185,405|US9399522B2|2014-02-20|2014-02-20|Ram air turbine actuator|
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