Submarine with a lid

Abstract

The present invention relates to a submarine with at least one first opening 130 between the interior of the submarine and the surrounding water area, wherein the first opening 130 is connected to a first cover 120, wherein the first opening 130 can be closed with the first cover 120, wherein the first cover 120 is rotatably mounted about a first axis of rotation 70, wherein the submarine has a first rotary drive 10, wherein the first rotary drive 10 is placed on a second axis of rotation 80 and its drive shaft is rotatably mounted thereon, wherein the first axis of rotation 70 and the second axis of rotation 80 are parallel and offset from each other, wherein the first rotary drive 10 and the first cover 120 are frictionally connected via a first linkage 20, wherein the first linkage 20 comprises a first crank 50, a first rocker arm 40 and a first coupling 60.wherein the first rotary drive 10 is frictionally connected to the first crank 50, wherein the first crank 50 is rotatably mounted about the second axis of rotation 80, wherein the first cover 120 is frictionally connected to the first rocker arm 40, wherein the first rocker arm 40 is rotatably mounted about the first axis of rotation 70, wherein the first crank 50 and the first rocker arm 40 are frictionally connected to each other via the first coupling 60, wherein the first rocker arm 40 is rotatably connected to the first coupling 60, wherein the first crank 50 is rotatably connected to the first coupling 60.

Description

[0001] The invention relates to a submarine with an opening and a lid closing the opening.

[0002] For the purposes of the invention, an opening is understood to be a connection between the interior of the submarine, in particular the interior of the submarine's pressure hull, and the surrounding water. The term "opening" can also include the wall enclosing the actual passageway. This wall can be a tube, for example, a gun tube, a multi-purpose tube, an airlock, a storage container, a personnel hatch, and the like. In the case of a tube, there is a storage compartment inside which a weapon, for example, a torpedo, equipment, divers, or any other items can be placed. The tube can have a further opening to the interior of the pressure hull, for example, for a diver airlock or for reloading in the case of a gun tube.A multi-functional tube can even incorporate a module that remains connected to the interior of the submarine's pressure hull for the entire duration of its use. Alternatively, a tube can simply have an opening, for example, to accommodate equipment that divers need to access while submerged.

[0003] However, the higher the opening is positioned, the more important it is to reduce weight, as otherwise the submarine's center of gravity will be negatively affected. This is therefore most critical when the opening is located in the conning tower, especially at the top. The higher the center of gravity, the more unstable the submarine becomes.

[0004] Furthermore, the linkage bearings are in direct contact with seawater. Due to the rotational movement present there, the risk of dirt ingress is low, which is otherwise high with translational movement. Additionally, the cover, with its lever arm, has two further pivot points that are also exposed to seawater. To keep these functioning properly, two separate grease supply lines must be installed to ensure continuous operation.

[0005] Furthermore, it is particularly important to ensure that upward-facing openings are securely locked to prevent them from closing unintentionally. With an upward-facing opening, such as a hatch for boarding on deck, the cover opens upwards, against gravity. Additionally, a submarine has a very low deck, meaning waves can easily strike an open cover. Therefore, it is crucial to reliably prevent the cover from closing unexpectedly. This necessitates locking the cover into a stable dead center position and holding it securely in place even under adverse conditions, without allowing external forces to damage it.

[0006] A submarine with a lid-opening drive is known from DE 10 2018 215 489 A1.

[0007] A submarine with a lid-opening drive is known from DE 10 2019 203 073 A1.

[0008] From DE 10 2007 058 055 B3 a submarine with a pressure hull and an emergency escape hatch with hinged lid is known.

[0009] A locking device for torpedo ejection tubes is known from AT 41 826 B.

[0010] A submarine with a lid is known from DE 10 2019 212 043 A1.

[0011] The object of the invention is to provide a lid opening mechanism which is particularly stable even when open and subject to external forces.

[0012] This problem is solved by the submarine with the features specified in claim 1. Advantageous further developments are described in the dependent claims, the following description, and the drawings.

[0013] The submarine according to the invention has at least one first opening between the interior of the submarine and the surrounding water. The first opening can be the opening of a gun barrel, a multi-functional tube, an airlock, a storage tank, a personnel hatch, or the like. A submarine usually has more than one opening, so the invention can also be applied to a second, third, etc., opening. However, if, for example, there is a particularly large opening or only one opening on the freeboard, the invention can also be implemented only at the first opening. The first opening is connected to a first cover. The first opening can be closed with the first cover. The first cover is rotatably mounted about a first axis of rotation. Thus, the cover can be opened by flipping it open.In this process, the lid pivots outwards, as it must be able to withstand the external pressure when submerged.

[0014] The submarine has a first rotary drive. The first rotary drive is mounted on a second axis of rotation, and its drive shaft is rotatably mounted about this axis. The first and second axes of rotation are parallel and offset from each other. The first rotary drive and the first cover are frictionally connected via a first linkage mechanism. The first linkage mechanism comprises a first crank, a first rocker arm, and a first coupling. The first rotary drive is frictionally connected to the first crank. The first crank is rotatably mounted about the second axis of rotation. The first cover is frictionally connected to the first rocker arm. The first rocker arm is rotatably mounted about the first axis of rotation. The first crank and the first rocker arm are frictionally connected to each other via the first coupling. The first rocker arm is rotatably connected to the first coupling.The first crank is rotatably connected to the first coupling. Such a submarine is known, for example, and in particular from DE 10 2019 212 043 A1.

[0015] According to the invention, the first crank has a thrust element. The first coupling has a drive element, in particular a hook element. The thrust element and the drive element, in particular the hook element, are arranged such that the thrust element and the drive element, in particular the hook element, come into contact at the dead center and optionally up to 10° of rotation of the crank before the open end position. This optional early contact allows, for example, material changes or manufacturing tolerances to be compensated for in a very simple way. At the dead center, the coupling and crank are in a straight line. Even immediately before the dead center, the coupling and crank are almost in a straight line, so that contact is advantageous, for example, up to 10° before the dead center. Instead of 10°, other angles, for example 2° or 5°, can also be selected. This means that power transmission is practically only possible along the longitudinal direction.It is therefore difficult to move the cover past the dead center into a slightly more open, stable end position. To achieve a targeted force transmission from the crank to the coupling in the area of ​​the dead center and the end position, a push element and a drive element, in particular a hook element, are used. Preferably, the push element and the drive element, especially the hook element, are in contact between the dead center and the open end position. Between the dead center and the end position, the push element and the drive element, especially the hook element, are preferably in sliding contact. One advantage is that the push element and the drive element are thus not in contact in the closed position and also for most of the opening process. This makes it possible to dispense with a complex mechanism that compensates for the relative changes between the elements during opening.

[0016] In a further embodiment of the invention, the impact element is rotatably mounted. This allows for a simple arrangement that does not collide with other parts when closed or during opening. Particularly preferably, the impact element has an impact gear for rotating it. The submarine has a rigid toothed ring, which is fixed, for example, around the second axis of rotation. The impact gear and the toothed ring mesh with each other, so that when the first crank is turned, the impact gear is set into rotation by the toothed ring. This ensures that the impact element is reliably moved into the correct position at its end.The size of the impact gear and toothed ring allows the strength of the rotation of the impact element to be easily adjusted, ensuring that no conflict with another component occurs, either in the closed rest position or during opening, until the impact element intentionally meets the drive element, in particular the hook element.

[0017] In a further embodiment of the invention, the drive element, in particular the hook element, is spring-mounted. This springing is synergistic with the springing of the stop according to the invention, so that a further reduction of shock effects and wave impacts against the cover is achieved, and damage is prevented by a slight degree of movement of the first coupling mechanism. Preferably, the drive element, in particular the hook element, is spring-mounted by a tension spring arranged in the first coupling.

[0018] In a further embodiment of the invention, the drive element, in particular the hook element, has a plastic glide at the contact point with the impact element. This is particularly preferred when the drive element, in particular the hook element, and the impact element are in sliding contact between the dead center and the end position. Additionally, this plastic glide serves to minimize noise during sliding against each other, as well as during the initial impact in the movement sequence.

[0019] In a further embodiment of the invention, the linkage mechanism has a stop. The stop limits the maximum opening of the first cover. The cover can thus be opened up to the angle at which the stop contacts the static ship structure, thereby preventing further opening. This has several advantages. Firstly, it stabilizes the cover in the open position. Secondly, and more importantly, it prevents the cover from being opened beyond this point, for example by a wave, and then becoming impossible to close. However, the stop alone is not sufficient, as the forces generated by a wave impact would then be too great and could damage the cover and / or other parts of the ship. Therefore, the linkage has at least one spring element, in particular a disc spring or a stack of disc springs.The stop is movably connected to the rocker arm via the spring element, in particular the disc spring or the stack of disc springs. This cushions the strong forces that occur briefly during shock loads or wave action. Preferably, the spring element, especially disc springs, is so stiff that it acts practically rigidly under normal forces and only becomes effective under extremely high forces. Thus, a "hard" stop is present under normal conditions, but cushioning occurs under extreme forces, such as wave action. The ratio of spring force to spring travel can be very high, for example, generating a high spring force of more than 10 kN with less than 5 millimeters of travel.

[0020] In a further embodiment of the invention, the spring element, in particular the stack of disc springs, consists of spring assemblies. Each spring assembly comprises two to five disc springs aligned in the same direction. Adjacent spring assemblies are stacked alternately. This allows for the simple construction of a spring that withstands the high forces occurring during wave action and, during compression in the range of a few millimeters, cushions the peak force, thus protecting the cover and adjacent components from damage.

[0021] In a further embodiment of the invention, the spring element, in particular the disc spring or the stack of disc springs, is arranged around the longitudinal axis of the rocker arm.

[0022] In a further embodiment of the invention, the spring element, in particular the disc spring or the stack of disc springs, is pre-tensioned. Pre-tensioning ensures even better that the spring is not compressed under normal conditions, whereas, for example, the spring action then takes effect in the event of rough seas.

[0023] In a further embodiment of the invention, the movement of the stop is only possible along the longitudinal axis of the rocker arm. This allows a brief rotational movement of the rocker arm beyond the end position point. After external release, the spring element, in particular the disc spring or the disc spring assembly, relaxes and returns the rocker arm to the safe end position.

[0024] In a further embodiment of the invention, the first coupling mechanism has an end position when the first cover is open, wherein in the end position the axis of rotation between the first crank and the first coupling lies within the imaginary triangle formed by the first axis of rotation, the second axis of rotation and the axis of rotation between the first rocker arm and the first coupling.

[0025] This results in four axes of rotation. The first and second axes are fixed relative to the submarine. A third axis of rotation arises from the pivot point where the first rocker arm and the first coupling are rotatably connected. A fourth axis of rotation arises from the pivot point where the first crank is rotatably connected to the first coupling. The third and fourth axes of rotation change their position when the first lid is opened and closed. The four axes of rotation are all parallel and offset from each other. In cross-section, the four axes of rotation form a quadrilateral, the shape of which changes when the first lid is opened and closed.From a point during opening where the intersection points of the second, third, and fourth axes of rotation lie on a straight line, a torque acting on the first lid cannot be transmitted to the second axis of rotation, thus preventing it from being closed in the open position by an external force. However, the first lid can be easily closed by a rotation around the second axis of rotation, as generated by the first rotary drive.

[0026] In a further embodiment of the invention, the first lid can be pivoted between the closed and the open state in the end position by at least 90° to a maximum of 120°, preferably by at least 100° to a maximum of 115°.

[0027] The submarine according to the invention is explained in more detail below with reference to exemplary embodiments shown in the drawings. Fig. 1 Rotary drive and coupling gear Fig. 2 Schematic cross-section through a first embodiment of the coupling mechanism Fig. 3 Perspective view of a first embodiment of the coupling mechanism Fig. 4 Semi-transparent representation of a first embodiment of the coupling mechanism Fig. 5 Schematic cross-section through a first embodiment of the coupling mechanism during opening Fig. 6. Schematic representation of the axes Fig. 7. Perspective view of the plate spring stack Fig. 8 semi-transparent representation with impact element and hook element Fig. 9 Section through stop and disc spring stack in closed position Fig. 10. Cut through stop and disc spring stack in open position Fig. 11 Push element and hook element in closed position Fig. 12 Push element and hook element in open position

[0028] The Fig. 1 to Fig. Figure 6 shows the general operating principle for opening and closing the lid, which Fig. 7 to Fig. 12 go into more detail about the disc spring stack, the stop, the shock element and the hook element.

[0029] In Fig. Figure 1 shows a perspective view of a drive mechanism for opening and closing a cover 120 for an opening 130 in a submarine. The drive mechanism has a rotary drive 10. This is positively connected to the cover 120 (not shown here) via a coupling gear 20. This connection is made via the rocker arm 40.

[0030] Typically, a lid 120 is hinged to the submarine via two brackets, one on the right and one on the left side of the lid 120. To achieve redundancy, each of these brackets can be operated by a drive. Preferably, the two drives are arranged between the brackets. To allow the lid 120 to continue opening and closing even if one drive fails, the drives preferably have a cross coupling 30, via which one drive can move the other in the event of its failure.

[0031] Fig. 2 to Fig. Figure 5 shows a first embodiment of the coupling mechanism 20, in which the rocker arm 40 and the crank 50 are designed in a disc shape.

[0032] Fig. Figure 2 shows a semi-transparent cross-section through the coupling mechanism 20. The rocker arm 40, which is circular and disc-shaped, is located furthest forward. The rocker arm 40 has a thickening located behind the disc and in the same plane as the coupling 60. Behind the coupling 60 is the circular, disc-shaped crank 50. The rotary drive 10 is located behind the crank 50 (not shown here). The coupling 60 has a shape consisting of two semicircles and a rectangle between them.

[0033] The swing arm 40, the crank 50 and the coupling 60 are arranged inside a housing 110.

[0034] The axes of rotation 70, 80, 90, and 100 are also shown. The first axis of rotation 70 and the second axis of rotation 80 are fixed in place, as indicated by the triangles. The rocker arm 40 is rotatably mounted around the first axis of rotation 70. The crank 50 is mounted around the second axis of rotation 80. The first axis of rotation 70 and the second axis of rotation 80 are parallel and offset from each other.

[0035] The swing arm 40 and the coupling 60 are rotatably and frictionally connected to each other via the third axis of rotation 90. The crank 50 and the coupling 60 are rotatably and frictionally connected to each other via the fourth axis of rotation 100.

[0036] The in Fig. The position of the coupling mechanism 20 shown in Figure 2 corresponds to the stop in the open state. The flat side of the coupling 60 makes contact with the thickening 42 of the rocker arm 40, thereby creating a positive connection and preventing further opening of the cover 120, even under strong forces acting on the cover 120.

[0037] In Fig. Figure 3 shows the coupling gear 20 with semi-transparent housing 110. Fig. Figure 4 shows the linkage mechanism fully semi-transparently. This reveals how the disc-shaped rocker arm 40 and the disc-shaped crank 50 are arranged parallel to each other but with offset axes of rotation. The linkage 60 positioned between them is connected to the rocker arm 40 via a first pivot bearing 62 and to the crank 50 via a second pivot bearing 64. This enables power transmission in the linkage mechanism 20.

[0038] Based on Fig. Figure 4 shows the assembly of the coupling mechanism 20. First, the rocker arm 40 is inserted into the empty housing 110 from the side of the crank 50. The recess in the housing 110, in which the coupling 60 will be located, is large enough to encompass the area of ​​both the recess for the crank 50 and the rocker arm 40. This allows the rocker arm 40 to be moved laterally in this area and positioned in its final location. The coupling 60 is then inserted, followed by the crank 50. This design easily achieves a compact, pressure-resistant, and sealed construction.

[0039] Fig. Figure 5 shows the coupling mechanism 20 in various opening positions. The opening 130 and the cover 120 are shown schematically and not to scale.

[0040] In Fig. 5a shows the closed position, in Fig. 5b a middle position and in Fig. 5c shows an open position at the end stop. It can be seen how the coupling 60 essentially rolls along the thickening 42 of the rocker arm 40 until, in the end position, its side surface rests directly against the thickening 42 of the rocker arm 40. On the other side, the cover 120 resting on the opening 130 blocks any further movement of the coupling mechanism.

[0041] Fig. 6 shows the in Fig. The 5 positions shown in a purely schematic representation of the axes of rotation: The rocker arm 40, the coupling 60 and the crank 50 are simplified as lines to illustrate their function. Fig. It can be seen from 6c that a force acting on the lid 120 cannot introduce a force component in the form of a torque onto the crank 50, which would lead to a clockwise rotation. On the contrary, this force would cause the crank 50 to be pressed against the rocker arm 40 and thus held in the open position.

[0042] Fig. Figure 7 shows in particular the rocker arm 40 with the stop 140. The stop 140 is connected to the rocker arm 40 via slot-shaped openings, allowing it to move within a limited range along the longitudinal direction of the rocker arm 40. The counter-stop 142 is stationary and, in the closed state shown, is located away from the stop 140. The disc spring stack 150 is arranged inside the rocker arm 40. The interaction between the stop 140, the disc spring stack 150, and the rocker arm 40 is shown in the Fig. 9 and Fig. Figure 10 shows the gear ring 170, whose functionality is described in the Fig. 8, Fig. 11 and Fig. 12 will be explained further.

[0043] In Fig. Figure 8 shows the rocker arm 40 in a semi-transparent image, revealing the crank 50 with the impact element 160 and the coupling 60 with the hook element 180. The impact element 160 has an impact gear 162 which engages with the toothed ring 170, causing the impact element 160 to rotate when the crank 50 is moved. The hook element 180 is attached to the coupling.

[0044] Fig. Figure 9 shows a cross-section with the lid closed. 120 and Fig. Figure 10 shows the lid 120 open. A portion of the rocker arm 40 is depicted. In the closed position, the stop 140 is located at the top. A push rod 144 engages the stop 140 and can rotate around the pivot point 148. The force acting on the stop 140 can be transmitted via a slide 146, the push rod 144, and the slide 146 to the disc spring stack 150. This allows a certain degree of movement for the stop 140, provided the disc spring stack 150 is compressible. Due to the hardness of the disc spring stack 150, this compression only occurs under very high forces acting on the lid 120. This component can, for example, be made of high-strength stainless steel. This allows the component to withstand extreme external forces without plastic deformation. Ultimately, this compact component then only performs a linear movement.

[0045] The Fig. 11 and Fig. Figure 12 shows the interaction of the thrust element 160 and the hook element 180. Fig. Figure 11 shows the situation with the lid closed at 120 and Fig. Figure 12 shows the situation with the lid 120 open, where Fig.Figure 12 shows the coupling 60 semi-transparently to reveal the tension spring 182 located inside the coupling 60. When the cover 120 is opened, the crank 50 rotates counterclockwise, as shown. This causes the impact gear 162 to roll over the fixed toothed ring 170, rotating the impact element. In the final position with the cover 120 open, the impact element 160 and the hook element 180 are in contact. To prevent noise and wear, the hook element has a plastic glide 190 at the point where the hook element 180 and the impact element 160 make contact. To ensure a degree of flexibility in the final position with the cover 120 open, the hook element has a pivot point and a slotted hole, as well as a tension spring 182 opposite the slotted hole, which is located inside the coupling 60. Reference sign 10 Rotary drive 20 coupling gears 30 Cross coupling 40 swing arms 42 Thickening 50 crank 60 couplings 62 first pivot bearing 64 second pivot bearing 70 first axis of rotation 80 second axis of rotation 90 third axis of rotation 100 fourth axis of rotation 110 cases 120 lids 130 Opening 140 strokes 142 Counterattack 144 Pushrod 146 slides 148 pivot point 150 stacks of disc springs 160 impact element 162 Shock gear 170 toothed ring 180 hook element 182 Tension spring 190 plastic gliders QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2018 215 489 A1

[0006] DE 10 2019 203 073 A1

[0007] DE 10 2007 058 055 B3

[0008] AT 41 826 B

[0009] DE 10 2019 212 043 A1 [0010, 0014]

Claims

[1] Submarine with at least one first opening (130) between the interior of the submarine and the surrounding water area, wherein the first opening (130) is connected to a first cover (120), wherein the first opening (130) is closable with the first cover (120), wherein the first cover (120) is rotatably mounted about a first axis of rotation (70), wherein the submarine has a first rotary drive (10), wherein the first rotary drive (10) is placed on a second axis of rotation (80) and its drive shaft is rotatably mounted about this axis of rotation (80), wherein the first axis of rotation (70) and the second axis of rotation (80) are parallel and offset from each other, wherein the first rotary drive (10) and the first cover (120) are positively connected via a first linkage (20), wherein the first linkage (20) comprises a first crank (50), a first rocker arm (40) and a first coupling (60) haswherein the first rotary drive (10) is frictionally connected to the first crank (50), wherein the first crank (50) is rotatably mounted about the second axis of rotation (80), wherein the first cover (120) is frictionally connected to the first rocker arm (40), wherein the first rocker arm (40) is rotatably mounted about the first axis of rotation (70), wherein the first crank (50) and the first rocker arm (40) are frictionally connected to each other via the first coupling (60), wherein the first rocker arm (40) is rotatably connected to the first coupling (60), wherein the first crank (50) is rotatably connected to the first coupling (60), , characterized by , that the first crank (50) has a push element (160), wherein the first coupling (60) has a drive element, wherein the push element and the drive element are arranged such that the push element (160) and the drive element are in contact in the open end position. [2] Submarine according to claim 1, characterized by, that the impact element (160) is rotatably mounted. [3] Submarine according to claim 2, characterized by , that the impact element (160) has an impact gear (162) for rotating the impact element (160), wherein the submarine has a rigid toothed ring (170), wherein the impact gear (162) and the toothed ring (170) mesh together, so that the impact gear (162) is set into rotation by the toothed ring when the first crank (50) is turned. [4] Submarine according to one of claims 2 to 3, characterized by that the drive element is spring-mounted. [5] Submarine according to claim 4, characterized by , that the drive element is resiliently mounted with a tension spring (182) arranged in the first coupling (60). [6] Submarine according to any one of claims 2 to 5, characterized by , that the drive element has a plastic glider (190) at the contact point with the impact element (160). [7] Submarine according to any of the preceding claims, characterized by , that the carrying element is a hook element (180). [8] Submarine according to any of the preceding claims, characterized by , that the coupling mechanism (20) has a stop (140) wherein the stop (140) limits the maximum opening of the first cover (120) wherein the rocker arm (40) has at least one spring element, wherein the stop (140) is movably connected to the rocker arm (40) via the spring element. [9] Submarine according to claim 8, characterized by , that the spring element is at least a disc spring or a stack of disc springs (150). [10] Submarine according to claim 9, characterized by , that the disc spring stack (150) consists of spring packs, each spring pack consisting of 2 to 5 disc springs aligned in the same direction, with adjacent spring packs being stacked alternately. [11] Submarine according to one of claims 9 to 10, characterized by, that the disc spring or the stack of disc springs (150) are arranged around the longitudinal axis of the rocker arm (40). [12] Submarine according to any one of claims 9 to 11, characterized by , that the disc spring or the stack of disc springs (150) is pre-tensioned. [13] Submarine according to any of the preceding claims, characterized by , that the movement of the stop (140) is only possible along the longitudinal axis of the swing arm (40).

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