Servo-control and an aircraft having such a servo-control

Abstract

A servo-control having at least one movable cylinder that includes a hydraulic directional control valve. The hydraulic valve includes a control shaft that is rotatable about a longitudinal axis, the control shaft being connected to a distributor slide. The servo-control including a stationary abutment member secured to a cylinder and an input lever situated outside the cylinder. The input lever is connected to the control shaft and includes a stop portion arranged in the abutment member. The servo-control includes movement means for moving the input lever longitudinally, a first abutment surface of the abutment member limiting a travel amplitude of the stop portion when the input lever is in a first position.

Claims

1. A servo-control having at least one movable cylinder and a stationary power rod, the power rod having one piston per cylinder, each piston defining a chamber referred to as a “retraction” chamber and a chamber referred to as an “extension” chamber in a casing of the cylinder, each cylinder including a hydraulic directional control valve provided with at least one hydraulic inlet suitable for being connected to a fluid delivery system and at least one hydraulic outlet suitable for being connected to a fluid discharge system, each hydraulic valve of a cylinder comprising at least one hydraulic distributor slide movable within the hydraulic valve in order to put each chamber of the cylinder on request into fluid flow communication with the hydraulic inlet or the hydraulic outlet, the hydraulic valve having a control shaft that is rotatable about a longitudinal axis, the servo-control including an input lever situated outside each cylinder, the input lever being suitable for being connected to a linkage for generating a movement order for the servo-control, wherein the control shaft is connected to the distributor slide so that a rotary turn of the control shaft causes the distributor slide to move, the input lever being connected to the control shaft and being movable with a first movement to cause the control shaft to turn, the servo-control including a stationary abutment member secured to at least one of the cylinders, the abutment member having at least a first abutment surface, the input lever including a stop portion co-operating with the abutment member, the servo-control including movement means for moving the input lever in a second movement in longitudinal translation from a first position to a second position and vice versa as a function of a predetermined condition, the first abutment surface limiting press-free travel of the stop portion during a first movement to a first amplitude solely when the input lever is in the first position.

2. A servo-control according to claim 1, wherein the abutment member includes a second abutment surface distinct from the first abutment surface, the second abutment surface limiting the travel amplitude of the stop portion during the first movement to a second amplitude when the input lever is in the second position, the second amplitude being different from the first amplitude.

3. A servo-control according to claim 1, wherein the abutment member includes an abutment surface that varies longitudinally from the first abutment surface.

4. A servo-control according to claim 1, wherein the stop portion is centered within the first abutment surface when the servo-control is supplied with hydraulic fluid at a pressure greater than a “minimum” pressure threshold, the distributor slide hydraulically isolating the chambers from the hydraulic inlet and the hydraulic outlet.

5. A servo-control according to claim 1, wherein the movement means include an actuator connected to the input lever and a control device suitable for giving an order to the actuator to move the input lever in longitudinal translation.

6. A servo-control according to claim 1, wherein the movement means include a cavity, the movement means moving the input lever in longitudinal translation from a first position to a second position, and vice versa, as a function of a threshold referred to as “maximum” threshold for a pressure in the cavity.

7. A servo-control according to claim 6, wherein the servo-control includes a hydraulic circuit delivering hydraulic fluid to a hydraulic inlet of a cylinder, the cavity being arranged in the hydraulic circuit.

8. A servo-control according to claim 6, wherein the cavity is arranged in the control shaft within the cylinder, the control shaft being constrained to move in longitudinal translation with the input lever, the movement means including a fluid-flow connection connecting the cavity with the hydraulic inlet.

9. A servo-control according to claim 8, wherein the hydraulic valve includes a resilient member that keeps the control shaft in the first position below the maximum pressure threshold.

10. A servo-control according to claim 1, wherein the control shaft includes a longitudinally extending elongate structure and an elongate arm secured to the elongate structure, the elongate arm extending longitudinally in parallel with the elongate structure, the elongate arm sliding in an orifice in the distributor slide.

11. A servo-control according to claim 1, wherein the control shaft projects in part from the cylinder, having a non-projecting portion arranged in the cylinder and a projecting portion arranged outside the cylinder, the non-projecting portion being mechanically connected to the distributor slide, the projecting portion being mechanically connected to the input lever.

12. A servo-control according to claim 1, wherein the abutment member includes a clevis having a first cheek and a second cheek, at least one cheek having at least one first arcuate abutment surface, a space between the cheeks being suitable for having a control link of the linkage passing therethrough.

13. A servo-control according to claim 12, wherein at least one cheek includes at least one second arcuate abutment surface.

14. A servo-control according to claim 1, wherein the input lever is secured to the control shaft.

15. A servo-control according to claim 1, wherein the input lever is hinged to the control shaft.

16. A servo-control according to claim 1, wherein the stop portion includes a hinge suitable for being connected to the linkage.

17. An aircraft, including at least one servo-control according to claim 1.

Description

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS

(1) The invention and its advantages appear in greater detail from the context of the following description of embodiments given by way of illustration and with reference to the accompanying figures, in which:

(2) FIG. 1 is a view of an aircraft of the invention;

(3) FIG. 2 is a view of a servo-control of the invention;

(4) FIG. 3 is a diagram showing a single-cylinder servo-control in a hydraulic embodiment;

(5) FIGS. 4 and 6 are section views showing a servo-control cylinder in a hydraulic embodiment and in a first position;

(6) FIGS. 5 and 7 are sections showing a servo-control cylinder in a hydraulic embodiment and in a second position;

(7) FIGS. 8 and 9 are diagrams showing a two-cylinder servo-control; and

(8) FIG. 10 is a diagram showing a servo-control provided with an actuator.

(9) Elements present in more than one of the figures are given the same references in each of them.

DETAILED DESCRIPTION OF THE INVENTION

(10) FIG. 1 shows an aircraft 1, and more particularly a rotorcraft having an airframe 3 carrying a main rotor 2 and a tail rotor 5 (not shown).

(11) The aircraft 1 then has a set of swashplates 4 for adjusting the pitch of the blades of the main rotor 2. This set of swashplates is controlled by three servo-controls 10 that are connected to control means 8 by means of linkages 6.

(12) Likewise, the linkage for controlling the pitch of the blades of the tail rotor 5 may include a servo-control that is not shown in FIG. 1.

(13) With reference to FIG. 2, each servo-control 10 of the invention comprises a cylinder 20 and a power rod 15.

(14) The power rod has anchor means for anchoring to a structure. One such anchor means may be in the form of a hinge fastened to an anchor point of a structure.

(15) Under such circumstances, each cylinder 20 is a movable cylinder, i.e. a cylinder that can slide along the power rod in a direction AX0 along which the power rod extends.

(16) Conventionally, the cylinder 20 presents an outer casing 21. Such an outer casing 21 may comprise a single shell, or a plurality of shells that are connected to one another by conventional means.

(17) The cylinder defines in particular an internal volume in which a piston of the power rod moves. This piston subdivides the internal volume into two chambers, namely an extension chamber and a retraction chamber.

(18) In order to deliver fluid to the retraction chamber and the extension chamber, the cylinder 20 includes a hydraulic directional control valve 30. This hydraulic valve 30 receives a distributor slide. The distributor slide is movable relative to the outer casing in order to control the pressures that exist in the retraction chamber and the extension chamber.

(19) In order to control the position of the distributor slide relative to the outer casing, the hydraulic valve has a control shaft 50 that is rotatable about a longitudinal axis AX1. A direction parallel to the longitudinal axis AX1 is substantially perpendicular to the direction AX0 in which the power rod extends. Likewise, a direction parallel to the longitudinal axis AX1 is substantially perpendicular to an axis of symmetry of the distributor slide.

(20) The control shaft 50 is also mechanically connected to the distributor slide so that turning the control shaft about the longitudinal axis AX1 causes the distributor slide to move, e.g. causes the distributor slide to move in translation.

(21) Furthermore, the servo-control includes an input lever 60 that is hinged to a control link 7 of a linkage 6. This linkage 6 leads to at least one pilot-operable control means.

(22) The input lever 60 is also situated outside the associated cylinder 20.

(23) Furthermore, the input lever 60 is mechanically connected to the control shaft. Thus, a movement of the input lever 60 performing a “first” movement leads to the control shaft 50 turning. As shown in FIG. 2, this first movement may be in the form of a turnabout the longitudinal axis AX1, or in another variant it may be in the form of a transverse movement in translation along a transverse direction. A direction parallel to the transverse direction is substantially perpendicular to the longitudinal axis AX1, for example.

(24) The control shaft 50 projects in part from the cylinder 20. Under such circumstances, the control shaft has a non-projecting portion (not shown in FIG. 2) that is arranged inside the cylinder 20. Furthermore, the control shaft has a projecting portion 55 that is arranged outside the cylinder 20. The non-projecting portion is then mechanically connected to the distributor slide, while the projecting portion is mechanically connected to the input lever 60.

(25) For example, the input lever 60 of FIG. 2 is secured to the control shaft 50. Thus, a first turning movement of the input lever about the longitudinal axis AX1 causes the control shaft 50 to turn.

(26) In another example, the input lever is connected to the control shaft via a conventional mechanical connection so that a movement in transverse translation of the input lever causes the control shaft 50 to turn.

(27) Furthermore, the input lever has a “stop” portion 63. For example, the linkage 6 is hinged to the stop portion 63.

(28) The stop portion 63 optionally includes an arcuate stop surface, or indeed, in particular, a surface that is at least partially circular.

(29) Under such circumstances, the servo-control has an abutment member 70 in which the stop portion 63 moves at least in part. The abutment member serves to adjust the constraint-free travel of the input lever when the input lever performs a said first movement.

(30) This abutment member 70 is secured to the cylinder 20 by conventional means such as screws, rivets, adhesive, or welding, for example.

(31) Furthermore, the abutment member 70 presents at least one “first” abutment surface. For example, at least one abutment surface is an arcuate surface, or indeed a surface that is in particular at least partially circular. The first abutment surface 72 serves to limit the constraint-free travel amplitude of the stop portion 63 to a first amplitude 201 under certain conditions.

(32) The abutment member may also include a varying abutment surface and/or a second abutment surface limiting the first constraint-free movement of the input lever to a second amplitude that is different from the first amplitude.

(33) In the variant of FIG. 5, the abutment member 70 may include a clevis 75. The clevis 75 has a first cheek 76 and a second cheek 77.

(34) There is a space 78 between the cheeks 76 and 77. Consequently, a control link 7 of the linkage 6 can pass through this space in order to be hinged to the stop portion by a hinge 64.

(35) Furthermore, at least one of the cheeks 76, 77 includes at least one first abutment surface 72. At least one of the cheeks 76, 77 may also include at least one second abutment surface 73.

(36) In the example of FIG. 5, each cheek presents a first abutment surface 72 and a second abutment surface 73. In other variants there may optionally be a varying abutment surface, e.g. varying between the first abutment surface and the second abutment surface.

(37) Furthermore, the servo-control 10 has movement means that are not shown in FIG. 5. The function of the movement means is to move the input lever 60 longitudinally to perform a “second” movement that is different from the first movement that serves to turn the control shaft.

(38) Thus, the movement means can move in longitudinal translation along the longitudinal axis AX1 of the input lever 60 between a first position POS1, included, and a second position (not shown in FIG. 5), included.

(39) The movement means serve in particular to move the input lever as a function of at least one predetermined condition. Such a predetermined condition may correspond to a pressure condition, a condition of a pilot-operable member being activated, or an execution condition issued by equipment of the aircraft.

(40) Under such circumstances, when the input lever 60 is in the first position POS1, the first abutment surface 72 limits the constraint-free travel amplitude of the stop portion 63 to a first amplitude 201. In contrast, when the input lever 60 is in the second position POS2 (shown in FIG. 7), the second abutment surface 72 limits the constraint-free travel amplitude of the stop portion 63 to a second amplitude 202.

(41) FIG. 3 shows a single-cylinder servo-control in a hydraulic embodiment.

(42) Independently of the embodiment, the servo-control has a power rod 15 provided with one piston 16 per cylinder 20. Each piston 16 defines within the casing 21 of the associated cylinder a chamber 22 referred to as a “retraction” chamber 23 and a chamber 22 referred to as an “extension” chamber 24.

(43) Under such circumstances, the cylinder 20 has a hydraulic directional control valve 30 connected to a hydraulic circuit 100. Thus, the hydraulic valve has at least one hydraulic inlet 31 connected to a fluid delivery system 101 and at least one hydraulic outlet 32 connected to a fluid discharge system 102 of the hydraulic circuit 100.

(44) Each hydraulic valve 30 also has a “retraction” channel 33 that leads to the retraction chamber 23, and an “extension” channel 34 that leads to the extension chamber 24. Under such circumstances, the hydraulic valve 30 includes a distributor slide 40 interposed between firstly the retraction channel 33 and the extension channel 34, and secondly the hydraulic inlet 31 and the hydraulic outlet 32.

(45) The distributor slide may for example comprise a spool having a first groove 42 and a second groove 43.

(46) Furthermore, the hydraulic valve includes a control shaft 50 connected to the distributor slide. A rotary turning movement ROT1, ROT2 of the control shaft causes the distributor slide to move.

(47) By way of example, in a neutral position of the input lever, none of the grooves is in communication with the hydraulic inlet 31 or the hydraulic outlet 32. The piston is in a middle position within the volume that the piston subdivides into two chambers 22.

(48) In contrast, an order O1 from a pilot may request the input lever to move into a retraction position. Under such circumstances, the control shaft performs a first rotary turn ROT1 in the counterclockwise direction as shown in FIG. 3.

(49) This first rotary turn ROT1 causes the distributor slide to move, and more particularly causes it to perform a first upward movement in translation T1 in FIG. 3. The second groove 43 then connects the hydraulic inlet 31 to the retraction channel 33 via ducts 311 and 313. The first groove 42 then connects the hydraulic outlet 32 to the extension channel 34 via a duct 321.

(50) Under such circumstances, the cylinder 20 is moved in translation along arrow S1.

(51) In contrast, the control link 7 remains stationary. Under such circumstances, the movement in translation of the cylinder 20 causes the control shaft to move relative to the input lever. This movement ends up by causing the input lever, the control shaft, and the distributor slide to be repositioned in the neutral position of FIG. 1.

(52) Likewise, a second order O2 from the pilot can request the input lever to move in an extension direction. Under such circumstances, the control shaft performs a secondary rotary turn ROT2 in the clockwise direction in the example of FIG. 3.

(53) This second rotary turn ROT2 causes the distributor slide to move, and more particularly causes it to perform a second movement in translation T2 towards the bottom of FIG. 3. The first groove 42 then connects the hydraulic inlet 31 to the extension channel 34 via ducts 311 and 312. The second groove 43 connects the hydraulic outlet 32 to the retraction channel 33 via a duct 321.

(54) Under such circumstances, the cylinder 20 is moved in translation along arrow S2.

(55) Furthermore, the control shaft 50 has an elongate structure 51 extending longitudinally along a longitudinal axis AX1. In addition, the control shaft 50 includes an elongate arm 52 secured to the elongate structure 51. The elongate arm 52 extends longitudinally parallel to the elongate structure 51. Additionally, the elongate arm 52 can slide in an orifice 41 in the distributor slide 40. Under such circumstances, turning the control shaft causes the distributor slide to move in translation.

(56) Furthermore, the control shaft is mechanically connected to the input lever 60. In particular, the elongate structure 51 is mechanically connected to the input lever 60.

(57) This input lever 60 is also provided with a hinge 64 connected to the control link 7 of the linkage 6. This hinge 64 may be carried by the stop portion 63 of the input lever 60.

(58) This stop portion 63 is arranged within the abutment member 70.

(59) Under such circumstances, the abutment member has at least one first abutment surface 72 limiting the first movement of the input lever to a first amplitude 201 when the input lever is positioned in the first position POS1 by the movement means.

(60) In the embodiment of FIG. 3, the movement means comprise a hydraulic device applied to a single-cylinder servo-control.

(61) The hydraulic device includes a cavity 83.

(62) The movement means 80 then move the input lever 60 in longitudinal translation from a first position POS1 to a second position, and vice versa, as a function of a threshold in a pressure that exists in the cavity 83 and referred to as the “maximum” threshold. If the pressure in the cavity is below the maximum threshold, then the input lever is in the first position. In contrast, if the pressure in the cavity is above the maximum threshold, then the input lever is moved into the second position.

(63) The cavity may be arranged in the hydraulic circuit 100.

(64) In contrast, in the embodiment shown in FIG. 3, the cavity is arranged in the cylinder of the servo-control. The cavity 83 is connected to the hydraulic inlet 31 via a fluid flow link 314 of the movement means 80.

(65) With reference to FIG. 4, this cavity 83 is defined in part by the control shaft 50 and an end wall 25 of the casing of the cylinder. The end wall 25 may be removable.

(66) Under such circumstances, the control shaft 50 is constrained to move in longitudinal translation together with the input lever 60.

(67) For this purpose, the control shaft 50 includes a non-projecting portion 56 arranged inside the cylinder 20 and a projecting portion 55 arranged outside the cylinder 20.

(68) The non-projecting portion 56 is mechanically linked to the distributor slide 40 by the elongate arm 52. In contrast, the projecting portion 55 is mechanically linked to the input lever 60. More particularly, in the embodiment of FIG. 4, the projecting portion 55 is secured to the input lever 60 by conventional means 57. Consequently, the input lever has a rod 61 extending from the stop portion 63 to an end 62 that is connected to the control shaft.

(69) Furthermore, a gasket 26 is arranged between the control shaft and the casing of the servo-control cylinder.

(70) In order to prevent the input lever moving below the maximum threshold, the hydraulic valve 30 includes a resilient member 90. This resilient member 90 may comprise a block of elastic material or indeed a spring, as shown in FIG. 4.

(71) The resilient member 90 exerts a force on the control shaft 50 in order to hold the control shaft 50 in the first position POS1 below the maximum pressure threshold.

(72) FIG. 10 shows an alternative embodiment for movement means.

(73) In this embodiment, the input lever 60 can slide along the control shaft 50. For example, the input lever is constrained to move in rotation with the control shaft 50 by fluting 54.

(74) Under such circumstances, the movement means 80 comprise an actuator 81 connected to the input lever 60. The actuator 81 may be a hydraulic, pneumatic, or electric jack that is suitable for causing the input lever to slide in longitudinal translation along the control shaft.

(75) Furthermore, the movement means possess a control device 82 suitable for giving an order to the actuator 81 to move the input lever in longitudinal translation as a function of said order.

(76) By way of example, the control device 82 may comprise a pressure sensor arranged in a hydraulic circuit, a button operated by a pilot, equipment for determining the position that the input lever is to reach, a sensor measuring the value of a monitoring parameter of the aircraft, . . . .

(77) FIGS. 4 to 7 explain the operation of the invention on a single-cylinder servo-control. This method is explained on the basis of the hydraulic embodiment shown in FIG. 3, however it could be performed using the embodiment of FIG. 10.

(78) With reference to FIGS. 4 and 5, when the hydraulic circuit is not delivering fluid to the servo-control, the input lever 60 is in the first position POS1 facing the abutment member 70. The stop portion 63 of the input lever is then facing the first abutment surface 72 of the abutment member.

(79) The input lever 60 can perform a first constraint-free movement through a first amplitude within the abutment member 70 in order to move the control shaft 55.

(80) The servo-control then provides no hydraulic assistance.

(81) In contrast, when the stop portion comes into contact with the abutment member, the stop portion can move the abutment member without stress and can consequently move the servo-control cylinder.

(82) The cylinder 20 of the servo-control can than behave like a link.

(83) When the hydraulic circuit is delivering fluid to the servo-control, the input lever 70 remains in the first position so long as a first condition is not satisfied.

(84) For example, the input lever 60 is maintained in the first position POS1 so long as the pressure in the servo-control is less than a maximum pressure threshold. For example, this maximum thresholds is about 40 bars.

(85) In the embodiment of FIG. 4, the resilient member 90 is dimensioned so as to keep the control shaft and the input lever in the first position POS1 so long as the first condition is not satisfied.

(86) Nevertheless, the servo-control can provide hydraulic assistance if a second condition is satisfied.

(87) Thus, and by way of example, the servo-control may provide hydraulic assistance as soon as the pressure in the servo-control reaches a minimum pressure threshold. This minimum pressure threshold is less than the maximum threshold, being of the order of 10 bars, for example.

(88) Once the second condition is satisfied, and with reference to FIG. 5, the intrinsic operation of the servo-control causes the stop portion 63 to be centered within the first abutment surface 72. The input lever is in a neutral position. In this neutral position, the distributor slide 40 isolates the chambers 22 hydraulically from the hydraulic inlet 31 and from the hydraulic outlet 32.

(89) If the input lever is not centered when the minimum threshold is reached, then the input lever shifts the distributor slide relative to its neutral position. Under such circumstances, hydraulic fluid is conveyed to a chamber of the servo-control. Because of the pressure of the fluid, this fluid causes the cylinder of the servo-control to move towards its neutral position.

(90) Consequently, the input lever is then in a centered position within the abutment member.

(91) The input lever may be moved without stress by flight controls to perform a first movement of a first amplitude 201 in order to request hydraulic assistance from the servo-control.

(92) This first amplitude is small for a single-cylinder servo-control. For example, the first amplitude is of the order of plus or minus one millimeter relative to the neutral position.

(93) This small amount of slack allows the servo-control to assist the pilot, while nevertheless giving a relatively small travel speed to the servo-control.

(94) With reference to FIG. 6, when the first condition is satisfied, the input lever 60 is moved by the movement means 80 towards a second position POS2.

(95) In the embodiment of FIG. 6, the pressure in the cavity 83 generates a force on the control shaft that is greater than the return force exerted by the spring 90. The control shaft 50 and the input lever then move jointly in longitudinal translation along the longitudinal axis AX1. This longitudinal translation movement may be interrupted by an abutment 200 of the cylinder of the servo-control, a shoulder of the control shaft coming into contact with said abutment 200. The input lever and the control shaft are then in a second position POS2.

(96) It should be observed that the abutment member does not impede the transition from the first position POS1 to the second position POS2, since the input lever is previously centered in the abutment member.

(97) With reference to FIG. 7, the stop portion 63 of the input lever 60 then no longer faces the first abutment surface.

(98) In contrast, the stop portion may be facing a second abutment surface 73.

(99) Consequently, the input lever can then be moved without stress by the flight controls with a first movement over a second amplitude 202 in order to request hydraulic assistance from the servo-control.

(100) This second amplitude is greater than the first amplitude in a single-cylinder servo-control. For example the second amplitude is of the order of plus or minus three millimeters relative to the neutral position.

(101) This large amount of slack enables the servo-control to assist the pilot, while nevertheless imparting a relatively fast travel speed to the servo-control.

(102) In the event of a hydraulic failure, the movement means position the input lever in the first position POS1. As a result of the hydraulic failure, constraint-free movement of the input lever within the limits of the first amplitude has no influence. In contrast, as soon as the input lever comes into abutment against the abutment member, the input lever then moves the cylinder of the servo-control against opposing stress. The cylinder then behaves like a link.

(103) FIGS. 8 and 9 show a servo-control of the invention having at least two cylinders.

(104) Each cylinder includes a hydraulic directional control valve with a distributor slide co-operating with a control shaft 50.

(105) Furthermore, the control shafts 50 of the cylinders are mechanically connected to an input lever 60.

(106) In FIG. 9, the input lever 60 is hinged to each of the control shafts. A movement in transverse translation of the input lever as shown by double-headed arrow 300 thus causes each of the control shafts to turn.

(107) Furthermore, and with reference to FIG. 8, the input lever 60 has a stop portion 63 arranged in an abutment member 70. This abutment member is secured to a cylinder of the servo-control.

(108) When the first condition is satisfied for each of the cylinders, each input lever is in the second position POS2 that is drawn with continuous lines.

(109) The travel of the input lever is limited by the abutment member to a second amplitude that is small in order to avoid the servo-control being too reactive.

(110) In contrast, if the hydraulic circuit delivering fluid to a cylinder fails, then the control lever returns to its first position POS1. In the example shown, the control shaft of the top cylinder of the servo-control is moved longitudinally.

(111) Under such circumstances, the constraint-free travel of the input lever is limited by the abutment member to a first amplitude that is large in order to be able to increase the performance of the cylinder that remains in operation.

(112) Likewise, when stopped or when only the second condition is satisfied for each of the cylinders, the input lever is in a first position POS1 in which the travel of the input lever is limited by the abutment member to a first amplitude.

(113) In the context of a servo-control having a plurality of cylinders, the input lever is in the first position POS1 when the first condition is not satisfied for at least one of the cylinders.

(114) Naturally, the present invention may be subjected to numerous variations as to its implementation. Although several embodiments are described, it will readily be understood that it is not conceivable to identify exhaustively all possible embodiments. It is naturally possible to envisage replacing any of the means described by equivalent means without going beyond the ambit of the present invention.