Hull deformation simulation device.

Abstract

Hull deformation simulation device.The invention relates to a simulation device (1) for the deformation of a structure (2) comprising: A rotary drive system (10), A chassis (12) comprising: at least one pusher (120) movable in translation along a direction (A) by means of a sliding link (122) fixed against the chassis (12), configured to be in contact with the structure (2) so as to apply a force on the structure (2) parallel to said direction (A), At least one deformation actuator (14) comprising: a fixing member (142) of said actuator (14) to the chassis (12), a cam (144) driven in rotation and configured to transform said rotation into a translation parallel to the direction (A), a connecting rod (146) connected at one end to the movable pusher (120) and at the other end to the cam (144), the connecting rod (146) being configured to drive the movable pusher (120) in translation parallel to said direction (A).Figure for the abbreviation: figure 2.

Description

Title of the invention: Hull deformation simulation device.

[0001] The invention relates to the field of modeling deformations on a substantially planar or curved surface. More specifically, the invention relates to a device for modeling, by means of a tangible representation, a deformation on a substantially planar or curved surface. The invention finds application in fields where the estimation and quantification of a deformation on a substantially planar or curved surface is necessary. By way of illustrative example, the invention finds particular application in the field of construction, and especially in shipbuilding.

[0002] Many devices or equipment are now mounted against building surfaces. Thus, in order to evaluate maritime physical characteristics, equipment is mounted on ship surfaces such as the hull of a boat, an aquatic drone or the hull of a submarine.

[0003] Any equipment mounted on a ship's surface, such as an underwater drone or a submarine, can be subjected to stress related to hull deformation as a function of immersion. This stress is called "hull contraction." This planar deformation of the hull depends on external conditions affecting the ship's hull, such as pressure or temperature. Thus, a ship's hull does not react in the same way under different pressure and / or temperature conditions.

[0004] Furthermore, the "hull contraction" phenomenon induces deformation of the hull subjected to this phenomenon along several combined directions. Indeed, the deformed and compressed structure, under the effect of pressure or temperature, deforms in a cylindrical frame of reference, in the radial direction but also in the longitudinal direction.

[0005] The difficulty is to reproduce this type of stress in a laboratory or workshop environment in order to verify in a simplified way the mechanical strength of a structure subjected to this type of deformation.

[0006] To date, two solutions exist for verifying the resistance of a structure to shell contraction stress: - Numerical modeling, consisting of the schematic digital representation, using modeling software, of the analyzed structure and the stress conditions. However, this method requires significant knowledge of the structure's characteristics and, above all, the conjecture of the behavior of this structure with respect to the conditions imposed on it. More precisely, this method is essentially based on the establishment of operating assumptions that are difficult to quantify. This numerical method therefore involves modeling and implementation uncertainties. Thus, the reliability between the numerical model and the actual behavior may be uncertain; - Practical testing on a test structure to verify the material's performance under real-world conditions. However, this solution requires multiplying the number of materials for testing, making it costly. Furthermore, testing generally takes longer compared to numerical modeling.

[0007] Therefore, there is no device that allows for rapid and certain testing of the behavior of equipment subjected to precise external conditions.

[0008] The invention aims to overcome all or part of the problems mentioned above by proposing a motorized device that makes it possible to tangibly model a hull deformation on a surface so as to be able to estimate the deformation undergone or the behavior of this surface in a reduced time.

[0009] To this end, the invention relates to a device for simulating the deformation of a substantially planar or curved structure in a marine environment, configured to measure the deformation of a substantially planar or curved structure, the simulation device comprising: - a rotary drive system, the drive system comprising a motor and a rotary transmission shaft; - a chassis comprising: - at least one pusher movable in translation along an axis substantially parallel to the planar structure by means of a sliding link fixed against the chassis, at least one pusher being configured to be in contact with the planar structure so as to apply a force on the planar structure parallel to said axis; - a push button attached to the chassis; - at least one deformation actuator, a deformation actuator of at least one deformation actuator comprising: - a transmission system connected to the transmission shaft; - a means of fixing said deformation actuator against the chassis; - a cam connected to the transmission system, configured to transform rotary motion into transverse motion; - a connecting rod linked at one end to a pusher among at least one movable pusher and at a second end to the cam, the connecting rod being configured to drive the movable pusher in translation parallel to said axis.

[0010] The shell contraction simulation device makes it possible to verify, under real conditions, the mechanical strength of a substantially flat or curved structure under stress from deformations in accessible conditions and at atmospheric pressure.

[0011] More specifically, the simulation device is capable of stressing a hull by modeling local deformations at the hull level itself. These local deformations are obtained by the oscillatory displacement of movable pushrods in translation that bear against the hull. This displacement induces a stress on the pushrod against the hull. The pushrods are driven in translation by means of a motor connected to a transmission element capable of transforming a rotary motion into an axial motion, namely the deformation actuator. The cam-connecting rod system thus makes it possible to generate axial oscillatory movements of the pushrod while being driven by a rotary motor.

[0012] According to one aspect of the invention, the deformation actuator comprises a transmission system connected to the transmission shaft so as to be driven in rotation by the rotary drive system, the transmission system being configured to drive the cam in rotation.

[0013] According to one aspect of the invention, the transmission system is a transmission belt.

[0014] According to one aspect of the invention, the chassis includes a pusher fixed to the chassis.

[0015] According to one aspect of the invention, the chassis comprises: - a first movable pusher in translation along a first axis substantially parallel to the structure or substantially parallel to a plane tangent to the structure by means of a first sliding link fixed against the chassis, the first movable pusher being configured to be in contact with the structure so as to apply a force on the structure parallel to said first axis; - a second movable pusher in translation along a second axis substantially parallel to the structure or substantially parallel to a plane tangent to the structure by means of a second sliding link fixed against the chassis, the second movable pusher being configured to be in contact with the structure so as to apply a force on the structure parallel to said second axis; - the first axis and the second axis being symmetrical with respect to an axis of symmetry of the chassis.

[0016] According to one aspect of the invention, the cam comprises: - an axis of rotation orthogonal to the axis of translation of the movable pusher; - a lug connecting the cam to the second end of the connecting rod, the lug being attached to a surface of the cam, the lug being distant from the axis of rotation of the cam.

[0017] According to one aspect of the invention, the connecting rod is configured to drive said movable pusher parallel to said axis in a transverse movement such that the distance traveled by the pusher is greater than 1 millimeter.

[0018] According to one aspect of the invention, the connecting rod is configured to drive said movable pusher parallel to said axis in a transverse movement so that the distance traveled by the pusher is less than 10 millimeters.

[0019] According to one aspect of the invention, the first end of the connecting rod comprises a first connecting member and in which the second end of the connecting rod comprises a second connecting member, the first connecting member being distant from the second connecting member by a first predefined distance.

[0020] According to one aspect of the invention, the first end of the connecting rod includes a third connecting member and in which the second end of the connecting rod includes a fourth connecting member, the third connecting member being distant from the fourth connecting member by a second predefined distance greater than the first distance.

[0021] The invention will be better understood and other advantages will become apparent upon reading the detailed description of an exemplary embodiment, illustrated by the accompanying drawings in which: - [Fig. 1] [Fig. 1] represents a schematic view of a first face of a deformation simulation device according to the invention, - [Fig.2] [Fig.2] represents a schematic view of a second face of the deformation simulation device of the [Fig.1], - [Fig.3] [Fig.3] represents a schematic profile view of the device simulation of deformation applied to a hull - [Fig.4] [Fig.4] represents a schematic top view of the second facing the deformation simulation device, and - [Fig. 5] [Fig. 5] represents a type of deformation actuator of the deformation simulation device according to the invention.

[0022] For the sake of clarity, the same elements will bear the same references in the different figures.

[0023] Figure 1 shows a first face 1' of a simulation device 1 for the deformation of a substantially planar or curved structure 2, shown in Figure 3, in a marine environment. The simulation device 1 is configured to measure a deformation of the substantially planar or curved structure 2. The structure is defined as a structure extending primarily in two dimensions. A substantially planar or curved structure is a structure in which two of its three dimensions are significantly larger than its third dimension, such that the substantially planar or curved structure can be considered a flat or curved surface. Hull deformation is understood to mean an alteration of the dimensions of the surface that is observable locally, this alteration being quantifiable only in a plane, i.e., in two dimensions.

[0024] The simulation device 1 includes a rotary drive system 10. The drive system 10 further includes a motor 100 and a rotary transmission shaft 110. The motor 100 is configured to drive the rotary transmission shaft 110 in rotation. The motor 100 is connected to the rotary transmission shaft 110. The motor 100 thus generates a torque enabling the rotary transmission shaft 110 to rotate.

[0025] Alternatively, the motor 100 can be replaced by an actuator capable of generating sufficient force or torque to drive the rotating transmission shaft 110 in rotation.

[0026] The simulation device 1 also includes a chassis 12. The motor 100 can be fixed against the chassis 12 as shown in [Fig. 1]. The rotary transmission shaft 110 can also be fixed to the chassis 12.

[0027] The simulation device 1 comprises at least one deformation actuator 14. The at least one deformation actuator 14 is fixed against the chassis 12. [Fig. 1] thus shows nine deformation actuators 14 distributed against the chassis 12. However, only one deformation actuator 14 is sufficient to generate the simulation of a deformation on the shell 2. The at least one deformation actuator 14 is a mechanical system configured to generate a force and a transverse movement on a planar structure 2 from the rotational movement of the rotating transmission shaft 110.

[0028] In the following description, the substantially planar or curved structure 2 is interpreted as a shell 2. However, any substantially planar or curved planar structure can be considered.

[0029] Figure 2 represents a second face 1” of the simulation device 1, and more particularly of the chassis 12, opposite the first face 1'. The chassis 12 comprises at least one pusher 120 movable in translation along an axis A substantially parallel to the shell 2 or substantially parallel to a plane tangent to the shell 2 by means of a The sliding joint 122 is fixed against the frame 12, as shown in [Fig. 5]. The sliding joint 122 thus takes the form of a guide rail allowing the movable pusher 120 to translate parallel to the shell 2 and the frame 12, along its axis of translation A. The sliding joint 122 ensures the kinematics of the combined radial and longitudinal deformation stress on the shell 2. Alternatively, any joint allowing the movable pusher 120 to translate along its axis of translation A can be considered, such as a sliding pivot joint. [Fig. 2] thus shows nine movable pushers 120 as an example, each pusher 120 having its own axis of translation A. However, a single movable pusher 120 is sufficient to generate the simulation of a deformation on the shell 2.

[0030] At least one movable pusher 120 is configured to be in contact with the shell 2 so as to apply a force on the shell 2 parallel to said axis A.

[0031] The simulation device 1 may also include a fixed pusher 124 attached to the chassis 12. The fixed pusher 124 is recessed against the chassis 12 so that the fixed pusher 124 is stationary. The fixed pusher 124 is also configured to be in contact with the shell 2.

[0032] It is thus possible to measure in real time the behavior of a region of the shell 2 stressed by a mobile pusher 120 compared to a region of the shell 2 left free by the fixed pusher 124.

[0033] The movable pusher 120 is thus driven in translation by means of a deformation actuator 14 in contact with the movable pusher 120. Advantageously, the number of movable pushers 120 is equal to the number of deformation actuators 14. Each movable pusher 120 is thus simultaneously connected to at least one deformation actuator 14 and to the shell 2 to be analyzed, such that an overlap is observable between the shell 2, the movable pusher 120, and the frame 12. The movable pusher 120 is constrained between the shell 2 and the frame 12 by means of the deformation actuator 14. In other words, the pusher 120 is connected to the frame 120 by means of a sliding joint that allows it to move in translation along its axis of translation. And, push button 120 is also connected to shell 2 by means of a fixed connection which does not allow any freedom between push button 120 and shell 2.Therefore, when the pusher 120 is driven in translation by the deformation actuator 14, this translational movement generates a mechanical reaction at the contact area between the pusher 120 and the shell 2 due to their fixed connection. This mechanical reaction is thus a local deformation of the shell 2 at the contact area between the shell 1 and the pusher 120 driven in translation.

[0034] Each deformation actuator 14 includes a fixing member 142 of said deformation actuator 14 against the chassis 12. Each deformation actuator 14 is thus embedded against the chassis 12 so as to be immobilized. The fastening element 142 is preferably a set of screws for screwing the deformation actuator 14 against the frame 12. The fastening means is thus advantageously a reversible fastening means allowing the deformation actuator 14 to be moved against the frame 12. It is therefore possible to vary the deformation on the shell 2 so as to locally observe the behavior of the shell 2 as it undergoes the deformation caused by the displaced deformation actuator 14. Alternatively, the fastening element 142 can be a strap or any other reversible fastening means such as a reversible adhesive.

[0035] Alternatively, the fastening element 142 can be an irreversible fastening means. Thus, the fastening element 142 can be, for example, an adhesive or a weld. In other words, any fixed connection, whether removable or not, can be used to connect a deformation actuator 14 to the frame 12. This fixed connection must simply allow the deformation actuator 14 to remain fixed to the frame 12 without deforming.

[0036] In order to generate the translational movement of the movable pusher 120 from the rotational movement of the rotary transmission shaft 110, each deformation actuator 14 comprises a cam 144 connected to the rotary transmission shaft 110. The cam 144 is thus a mechanical element driven in rotation, along a first portion 1440, shown in [Fig. 1], by the rotary transmission shaft HO, capable of generating, at a second portion 1442, shown in [Fig. 2], a transverse movement. The cam 144 is thus configured to transform the rotary movement of the rotary transmission shaft 110 into a transverse movement at its second portion 1442. Alternatively, any other system or device capable of transforming the rotational movement from the motor 100 into a translational movement may be considered.

[0037] Furthermore, each deformation actuator 14 comprises a connecting rod 146 connected at a first end 1460 to a movable pusher from among at least one movable pusher 120 and at a second end 1462 to the second portion 1442 of the cam 144, shown in [Fig. 3]. The connecting rod 146 is configured to drive the movable pusher 120 in translation parallel to the axis of translation of said movable pusher 120.

[0038] In other words, the connecting rod 146 is capable of pushing and pulling the movable pusher 120 along its sliding joint 122 so as to generate a displacement of the movable pusher 120. The movable pusher 120 is thus forced to move by the movement of the connecting rod 146.

[0039] However, the movable pusher 120 is also in contact and under stress against the shell 2, the shell 2 undergoes the displacement of the connecting rod 146 so that the shell 2 is locally deformed at the point of contact between the movable pusher 120 and the shell 2. He then has a physical model of the deformation by the movement of the connecting rod 146 and the pusher 120 mobile against the hull 2.

[0040] As stated previously, the simulation device 1 can include several deformation actuators 14 and therefore several cams 144. Consequently, it can be envisaged that, for each deformation actuator 14 and each cam 144, the simulation device 1 includes a motor and a rotary drive shaft exclusive to said deformation actuator 14 and said cam 144. This configuration has the advantage of offering great freedom in the arrangement of the motors, rotary drive shafts, deformation actuators, and pushrods. However, this configuration also has the disadvantage of complicating the simulation device 1 by adding a large number of mechanical components.

[0041] Alternatively, a single motor 100 and a single rotary drive shaft 110 may be envisaged. Each deformation actuator 14 may include a transmission system 140 connected to the rotary drive shaft 110 and the cam 144. The transmission system 140 allows the torque from the rotary drive shaft 110 to be transmitted to at least one deformation actuator 14 so as to set in motion at least one deformation actuator 14 and the cam 144.

[0042] Therefore, a cam 144 is connected to the rotary transmission shaft 110 via the drive system 140. This configuration makes it possible to limit the number of mechanical components and motors in particular.

[0043] In other words, the simulation device 1 comprises a frame 12 against which the motor 100 is fixed. The motor 100 then sets in motion the rotary transmission shaft 110, which is fixed to the first face 1' of the simulation device 1 and the frame 12. This rotational motion and torque are then transmitted by the transmission system 140, connected to the rotary transmission shaft 110, to the first portion 1440 of the cam 144, so as to induce a rotation of the cam 144. The cam 144 passes through the frame such that the first portion 1440 of the cam 144 is against the first face 1' of the frame 12 of the simulation device 1, and the second portion 1442 of the cam 144 is against the second face 1" of the frame 12 of the simulation device 1. The rotational motion is thus transmitted to the second portion 1442 of the cam 144.The cam 144 then converts the rotational movement observable at the first portion 1440 into a translational movement at the second portion 1442. The second portion 1442 transmits the translational movement to the connecting rod 146 via the first end 1460 of the connecting rod 146. The connecting rod 146, which is positioned opposite the second face 1”, is thus movable in translation and guided by the second portion 1442 of the cam 144. The movable pusher 120 is then set in translation by the guided translation of the connecting rod 146, due to the connection of the second end 1462 of the connecting rod 146 with the pusher. The mobile pusher 120 moves along the frame 12 in a translational motion parallel to axis A via its sliding joint 122. The mobile pusher 120, which is also in contact with the shell 2 to be analyzed, thus imposes this movement on the shell 2. Since the shell 2 is static relative to the frame 12 and the mobile pusher 120, the shell 2 is locally deformed at the contact area between the mobile pusher 120 and the shell 2. This local deformation of the shell 2, due to the opposition between the force required for the rectilinear movement of the mobile pusher 120 and the reaction of the static shell 2, is quantifiable with respect to the shell 2 left at rest in contact with the fixed pusher 124.

[0044] Advantageously, the transmission system 140 can be a transmission belt. The transmission belt has the advantage of being a mechanical component that allows the transmission of circular motion from a main transmission shaft, namely the rotary transmission shaft 110, to a secondary transmission shaft, namely the first portion 1440 of the cam 144.

[0045] However, any transmission system between the rotating transmission shaft 110 and the cam 144 by angle drive can be envisaged, such as for example the use of a worm gear.

[0046] Figure 3 is a side view of the simulation device 1 and the shell 2, which more precisely shows the contact areas, referenced 20, between the pushers 120 and the shell 2. When a pusher 120 is in motion, a local deformation due to the opposition between the force required for the rectilinear movement of the moving pusher 120 and the reaction of the static shell 2 is observable at the contact area 20 between said pusher 120 and the shell 2. As stated previously, the moving pusher 120, like the fixed pusher 124, is supported against a face 2' of the shell 2. Therefore, the rectilinear movement of the moving pusher 120 locally generates a stretching of the face 2' in a direction parallel to the translational movement and to the axis A.Local is understood to mean that the deformation of the shell 2 by the transverse displacement of the pusher 120 is observable at the contact zone 20 between said pusher 120 and the shell 2 or near the contact zone 20 on the face 2'.

[0047] Figure 4 shows a front view of the second face 1” of the simulation device 1. As previously stated, the simulation device can include several deformation actuators 14, movable pushers 120 or fixed pushers 124. By way of example, Figure 4 shows a simulation device 1 comprising nine deformation actuators 14, nine movable pushers 120 and two fixed pushers 124.

[0048] The frame 12 may include a first pusher 120' movable in translation about a first axis Al substantially parallel to the shell 2 by means of a first sliding joint 122' fixed against the frame 12. The first movable pusher 120' is configured to be in contact with the hull 2 ​​so as to apply a first force on the hull 2 ​​parallel to said first axis Al.

[0049] The chassis 12 can also include a second pusher 120” movable in translation about a second axis A2 substantially parallel to the shell 2 by means of a second sliding link 122” fixed against the chassis 12. The second movable pusher 120” is configured to also be in contact with the shell 2 so as to apply a second force Asur the shell 2 parallel to said second axis A2.

[0050] The first mobile pusher 120' being distant from the second mobile pusher 120”, two forces, namely the first force f} and the second force / 2, are applied against the shell 2.

[0051] The first axis A1 and the second axis A2 can intersect so that it is possible to observe the behavior and deformation of the shell along two distinct rectilinear movements by means of the movement of the first movable pusher 120' and the second movable pusher 120" . The use of several movable pushers 120, and therefore of several deformation actuators 14, thus has the advantage of being able to simulate the deformation of the shell 2 in several deformation zones, namely at the contact between the first movable pusher 120' and the face 2' of the shell 2 and at the contact between the second movable pusher 120" and the face 2' of the shell 2 simultaneously. It is thus possible to generate numerous local deformation stresses to observe the overall behavior of the shell 2.

[0052] The first axis Al can be symmetrical to the second axis A2 along an axis of symmetry S of the frame 12. Axial symmetry can be observed between the first axis Al and the second axis A2 and between the movement of the first movable pusher 120' and the movement of the second movable pusher 120". It is thus possible to generate forces such as the first force or the first force f1, whose direction, related to the movement of the first movable pusher 120' for the first force f1 and to the movement of the second movable pusher 120" for the second force f2, is substantially opposite.

[0053] The frame 12 may also include a third movable 120" pusher and a fourth movable 120" pusher. The third and fourth movable 120" pushers may have the same axis of translation. In other words, the third axis of translation A3 of the third movable 120" pusher and the fourth axis of translation A4 of the fourth movable 120" pusher may coincide. This configuration has the advantage of increasing the deformation in one direction through the movement of two movable pushers.

[0054] The movement between two movable pushers, such as the third movable pusher 120” and the fourth movable pusher 120” can be synchronous. In other words, when the third movable pusher 120” translates in a third direction D3 parallel to the third axis A3, then the fourth movable pusher 120” translates in a fourth direction D4 parallel to the fourth axis A4.

[0055] The movement between two movable pushers can also be asynchronous. In other words, when the third movable pusher 120” translates in the third direction D3, then the fourth movable pusher 120” translates in the opposite direction to the fourth direction D4 parallel to the fourth axis A4.

[0056] This asynchronous movement makes it possible to localize the deformation of the shell 2 on a smaller surface and to observe the behavior of the shell 2 with respect to two different, or even opposite, stresses.

[0057] These non-synchronous or asynchronous translations can be obtained by offsetting the rotation of the cams 144 of the deformation actuators 14. Thus, as soon as the cam 144 is driven in rotation by the rotating transmission shaft 110, the pusher 120 is always mobile since it oscillates parallel to its axis of translation. In other words, the pusher 120 is not fixed.

[0058] Figure 5 shows an enlarged view of the mechanical connections between the second portion 1442 of the cam 144, the connecting rod 146, and the movable pusher 120. As stated previously, the cam 144 is fixed against the second face 1” of the frame 12 by means of the fastening member 142, which is preferably screws passing through the frame 12. The cam 144 is movable in rotation about an axis of rotation R orthogonal to the axis of translation A of each movable pusher 120 of at least one movable pusher 120. In other words, the first portion 1440 and the second portion 1442 of the cam 144 can rotate about an axis of rotation R.

[0059] The cam 144 may also include a lug 1444 connecting the second portion 1442 of the cam 144 to the second end 1462 of the connecting rod 146. The lug 1444 takes the form of a protrusion extending from the second portion 1442 of the cam 144. The lug 1444 is integral with a surface 1442' of the second portion 1442 of the cam 144 parallel to the second face 1” of the simulation device 1 and the chassis 12. The lug 1444 is distant from the axis of rotation R of the cam 144 such that when the second portion 1442 is rotating, the lug 1444 also undergoes rotation.

[0060] In other words, the surface 1442' can have a radial dimension r if the cam 144, and more specifically the second portion 1442, has a cylindrical shape. The distance separating the axis of rotation R from the lug 1444 is then less than the radial dimension r.

[0061] The surface 1442' can have a different shape, such as a polygonal shape, when the cam 144, and more particularly the second portion 1442 of the cam 144, has a polygonal tubular shape. Therefore, the surface 1442' can have a diagonal dimension r. The diagonal dimension r is a diagonal of the polygon formed by the surface 1442' intersecting the axis of rotation R in the plane formed by the surface 1442'. The distance separating the axis of rotation R from the lug 1444 is then less than the diagonal dimension r.

[0062] Preferably, the ergot 1444 has a tubular shape, as shown in [Fig.5],

[0063] The first end 1460 of the connecting rod 146 may include a first connecting member 1461. As shown in [Fig. 5], the first connecting member 1461 is an opening allowing the lug 1444 to be inserted into the first connecting member 1461. The lug 1444 is thus fitted into the connecting rod 146 through the opening, namely the first connecting member 1461. Similar to a connection between a male device, namely the lug 1444, and a female receiving device, namely the first connecting member 1461, the lug 1444 passes through the opening and the billet 146.

[0064] Preferably, the lug 1444 and the first connecting member 1461 have complementary shapes and dimensions.

[0065] It may also be envisaged to add a first fixing member 147 such as a nut or a fixing clip so that the lug 1444 is immobilized in the first connecting member 1461 and that the connecting rod 146 is immobilized against the surface 1442' of the first portion 1442 of the cam 144.

[0066] Alternatively, the connecting rod 146 can be fixed against the surface 1442' of the second portion 1442 of the cam 144 by means of a reversible bond such as a reversible adhesive or glue.

[0067] The introduction of the lug 1444 into the first connecting member 1461 allows the connecting rod 146 to be driven in a translational movement thanks to the conversion of movement generated by the offset rotation of the lug 1444 with respect to the axis of rotation R. And, the distance separating the lug 1444 from the axis of rotation R of the cam 144 allows the amplitude of the transverse displacement of the connecting rod 146 and the movable pusher 120 to be determined and therefore the deformation generated on the shell 2.

[0068] The second end 1462 can also include a second connecting member 1463. As shown in [Fig.5], the second connecting member 1463 is an opening.

[0069] The movable pusher 120 includes an opening 1200. A second fastening member comprising a screw 148' connects the second connecting member 1463 of the link 146 to the opening 1200 of the movable pusher 120. The screw 148' passes through the link 146 via the opening, namely the second connecting member 1463. and passes through the opening 1200 of the movable pusher 120 so as to fix the connecting rod 146 by its second end 1462 against the movable pusher 120. A superposition of the second connecting member 1463 and the opening 1200 of the movable pusher 120 is observable in a plane perpendicular to the second face 1”. The screw 148' can be replaced by a stud or a rod allowing the superposition of the second connecting member 1463 and the opening 1200 of the movable pusher 120 in the plane perpendicular to the second face 1”.

[0070] The translational movement of the connecting rod 146 is thus transmitted to the movable pusher 120 which also translates along its axis A of translation by means of the sliding link 122. The movable pusher 120 is thus successively pushed and pulled by the connecting rod 146 which undergoes the rotational movement of the lug 1444.

[0071] To improve the attachment of the connecting rod 146 against the movable plunger 120, the second fastening member may include a nut 148” or a fastening clip so that the screw 148' is immobilized in the second connecting member 1463 and in the opening 1200 of the movable plunger 120, and the connecting rod 146 is immobilized against the movable plunger 120. An overlap of the second connecting member 1463, the opening 1200 of the movable plunger 120, and the nut 148” or fastening clip is observable in the plane perpendicular to the second face 1”.

[0072] Since the first connecting member 1461 and the second connecting member 1463 are openings, the connecting rod 146 is a simple mechanical part to machine.

[0073] Alternatively, the second connecting member 1463 can be a lug capable of being introduced into the opening 1200 of the movable pusher 120, in a similar way to the lug 1444 and the first connecting member 1461. In this configuration, the screw 148' is then no longer needed.

[0074] Alternatively, the connecting rod 146 can be fixed against the movable pusher 120 by means of a reversible connection such as a reversible adhesive or glue.

[0075] The first connecting member 1461 is distant from the second connecting member 1463 by a first predefined distance.

[0076] The first end 1460 of the connecting rod 146 may include a third connecting member 1464 identical to the first connecting member 1461. And, the second end 1462 of the connecting rod 146 may also include a fourth connecting member 1465 identical to the second connecting member 1463. The third connecting member 1464 is separated from the fourth connecting member 1465 by a second predefined distance L2 greater than the first distance. The lug 1444 can thus be inserted into the first connecting member 1461 or into the third connecting member 1464 and the opening 1200 of the movable pusher 120 can be superimposed with the second connecting member 1463 or with the fourth connecting member 1465 so that the screw 148' is inserted either in the second connecting body 1463 or the fourth connecting body 1465.

[0077] Since the second distance L2 between the third connecting member 1464 and the fourth connecting member 1465 is greater than the first distance fq between the first connecting member 1461 and the second connecting member 1463, it is thus possible to control the amplitude of the displacement of the movable pusher 120. More precisely, by connecting the cam 144 to the movable pusher 120 via the first connecting member 1461 and the second connecting member 1463, the cam 144 is separated from the movable pusher 120 by a distance equivalent to the first distance L1. By increasing the distance separating the cam 144, which is fixed against the chassis 12, from the movable pusher 120, the movable pusher 120 is then naturally pushed away from the cam 144 by a distance equivalent to the second distance. Since the movable pusher 120 is already in contact with the shell 2, moving the movable pusher 120 is equivalent to constraining the shell 2.

[0078] As stated previously, the translation of the connecting rod 146 and the displacement of the movable pusher 120 can be easily determined from the distance or eccentricity separating the lug 1444 from the axis of rotation R of the cam 144. The change in the distance separating the two connecting members, namely the first distance between the first connecting member 1461 and the second connecting member 1463 or the second distance L? between the third connecting member 1464 and the fourth connecting member 1465, of the connecting rod 146 makes it possible to generate a translation of different and increased amplitude in order to further constrain the shell 2.

[0079] This variation in the distance between the two connecting members of the connecting rod 146 also has the advantage of allowing easy connection of the cam 144 to the movable pusher 120 for any eccentricity of the lug 1444 of the cam 144 with respect to its axis of rotation R.

[0080] Increasing the distance separating the cam 144 from the movable pusher 120, by connecting the second position 1442 of the cam 144 to the third linking member 1464 and the opening 1200 of the movable pusher 120 to the fourth linking member 1465, makes it possible to over-stress the shell 2 even before the dynamic movement of the movable pusher 120 driven by the rotation of the cam 144.

[0081] Alternatively, the connecting rod 146 may include a predefined number of connecting members, which may be greater than the four connecting members 1461, 1462, 1464 and 1465. In this way, it is possible to control with great precision the distance separating the lug 1444 from the pusher 120 and to predefine several deformations accordingly on the shell 2.

[0082] This configuration has the advantage of allowing the constraints at the level of the shell 2 to be increased so as to observe the shell under greater deformations.

[0083] It is then possible to control the movement of the mobile pusher 120.

[0084] The displacement of the movable pusher 120 is controlled by the distance separating the axis of rotation R of the cam 144 from the lug 1444. The distance between the cam 144 and the movable pusher 120, namely the first distance L1 or the second distance L2, is deduced from the eccentricity of the lug 1444 with respect to the axis of rotation R so as to guarantee the maintenance of the initial position of the movable pusher 120.

[0085] The further the lug 1444 is from the axis of rotation R of the cam 144 on the surface 1442' of the second portion 1442, the greater the amplitude of the displacement and therefore the greater the translations of the movable pusher 120.

[0086] The cam system 144 allows the appropriate stresses to be applied according to the intended immersion depth, but also proportionally according to the position of each fixing point relative to a given fixed reference. Any planar deformation of the hull 2 ​​can be generated by a pair of cam 144 and connecting rod 146 which allows a different amplitude of translation to be applied to the movable pusher 120.

[0087] The motorization by the motor 100 and the transmission, by means of the rotary transmission shaft 110 and the transmission system 140, make it possible to apply a repeated and cyclic stress, representing operational stress on the hull 2.

[0088] The connecting rod 146 can be configured to drive the movable pusher 120 parallel to its axis A of translation in a transverse movement such that the distance traveled by the pusher 120 is greater than 1 millimeter. By way of indicative example, when the cam 144 is separated from the movable pusher 120 by a distance equivalent to the first distance L, the displacement of the movable pusher 120 is on the order of 1 millimeter, depending on the distance between the lug 1444 and the axis of rotation of the cam R on the surface 1442'.

[0089] And, when the cam is distant from the movable pusher 120 by a distance equivalent to the second distance L2, the displacement of the movable pusher 120 is on the order of 10 millimeters, depending on the distance between the lug 1444 and the axis of rotation of the cam R at the surface 1442'.

[0090] The hull deformation simulation device therefore makes it possible to verify the mechanical resistance of a material to the contraction stress linked to immersion, under accessible conditions and in air at atmospheric pressure.

[0091] The simulation device 1 allows modeling a deformation on an arbitrary structure 2. Preferably, the structure 2 is a so-called planar structure in which two of its dimensions, such as its length and width, are significantly greater than its third dimension, so that a deformation in a plane coinciding with the two significantly greater dimensions is observable. The structure 2 can be a planar structure, that is to say, a structure in which its two significantly greater dimensions Structures in the third dimension are contained within a plane. Alternatively, structure 2 can be a curved structure such as a shell 2.

Claims

Demands

1. A simulation device (1) for the deformation of a structure (2) configured to measure a deformation of a structure (2), the simulation device (1) comprising: - a rotary drive system (10) comprising a motor (100) and a rotary transmission shaft (110), the motor (100) being configured to drive the rotary transmission shaft (110) in rotation; - a frame (12) comprising: - a pusher (120) movable in translation along a direction (A) substantially parallel to the structure (2) or substantially parallel to a plane tangent to the structure (2) by means of a sliding joint (122) fixed against the frame (12), the movable pusher (120) being configured to be in contact with the structure (2) so as to apply a force (f? / 2) on the structure (2) parallel to said direction (A),- a deformation actuator (14) comprising: - a fixing member (142) for said deformation actuator (14) to the frame (12), - a cam (144) driven in rotation by the rotary transmission shaft (110), configured to transform said rotation into a translation parallel to the direction (A), a connecting rod (146) connected at a first end (1460) to the movable pusher (120) and at a second end (1462) to the cam (144), the connecting rod (146) being configured to drive the movable pusher (120) in translation parallel to said direction (A).

2. Deformation simulation device (1) according to claim 1, wherein the deformation actuator (14) comprises a transmission system (140) connected to the transmission shaft (110) so as to be driven in rotation by the rotary drive system (110), the transmission system (140) being configured to drive in rotation the cam (144).

3. Simulation device (1) of deformation according to claim 2, wherein the transmission system (140) is a transmission belt.

4. Deformation simulation device (1) according to any one of claims 1 to 3, wherein the chassis (12) includes a pusher (124) fixed to the chassis.

5. A deformation simulation device (1) according to any one of claims 1 to 4, wherein the frame (12) comprises: - a first pusher (120') movable in translation about a first axis (A1) substantially parallel to the structure (2) or substantially parallel to a plane tangent to the structure (2) by means of a first sliding joint (122') fixed against the frame (12), the first movable pusher (120') being configured to be in contact with the structure (2) so as to apply a force (yJ) on the structure (2) parallel to said first axis (A1), - a second pusher (120") movable in translation about a second axis (A2) substantially parallel to the structure (2) or substantially parallel to a plane tangent to the structure (2) by means of a second sliding joint (122") fixed against the frame (12),the second movable pusher (120”) being configured to be in contact with the structure (2) so as to apply a force (fj) on the structure (2) parallel to said second axis (A2), - the first axis (A1) and the second axis (A2) being symmetrical with respect to an axis of symmetry (S) of the chassis (12).

6. Simulation device (1) of deformation according to any one of claims 1 to 5, in which the cam (144) comprises: - an axis of rotation (R) orthogonal to the axis (A) of translation of the movable pusher (120), - a lug (1444) connecting the cam (144) to the second end (1462) of the connecting rod (146), the lug (1444) being integral with a surface (1442') of the cam (144), the lug (1444) being distant from the axis of rotation (R) of the cam (144).

7. Deformation simulation device (1) according to any one of claims 1 to 6, wherein the connecting rod (146) is configured to drive said pusher (120) movable parallel to said axis (A) in a transverse movement such that the distance traveled by the pusher (120) is greater than 1 millimeter.

8. Deformation simulation device (1) according to any one of claims 1 to 7, wherein the connecting rod (146) is configured to drive said pusher (120) movable parallel to said axis (A) in a transverse movement such that the distance traveled by the pusher (120) is less than 10 millimeters.

9. Deformation simulation device (1) according to any one of claims 1 to 8, wherein the first end (1460) of the connecting rod (146) comprises a first connecting member (1461) and wherein the second end (1462) of the connecting rod (146) comprises a second connecting member (1463), the first connecting member (1461) being distant from the second connecting member (1462) by a first predefined distance (L^).

10. A deformation simulation device (1) according to claim 9, wherein the first end (1460) of the connecting rod (146) comprises a third connecting member (1464) and wherein the second end (1462) of the connecting rod (146) comprises a fourth connecting member (1465), the third connecting member (1464) being distant from the fourth connecting member (1465) by a second predefined distance (^2) greater than the first distance (

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