Automatic turnover device and method for marine diesel engine cylinder block

Abstract

The invention discloses an automatic turnover device and method for a marine diesel engine cylinder block. The automatic turnover device for the marine diesel engine cylinder block comprises a pit, a supporting bracket, a turnover support and two driving assemblies. The overturning support comprises two supporting frames which are vertically connected, and the overturning support has a first posture in which the outer wall of one supporting frame abuts against the supporting bracket in parallel and a second posture in which the outer wall of the other supporting frame abuts against the supporting bracket in parallel. Each driving assembly comprises at least one hydraulic cylinder, one end of each hydraulic cylinder is rotationally installed on the bottom face of the pit through a supporting base, the other end of each hydraulic cylinder penetrates through the corresponding supporting bracket and is hinged to the outer wall of the corresponding supporting frame, and the two driving assemblies are matched to drive the overturning support to overturn between the first posture and the second posture in a reciprocating mode. The driving assembly is simple in structure and convenient to control, mounting steps of a turnover device mechanism and the air cylinder body can be simplified, meanwhile, steel wire ropes are prevented from pulling the surface of the air cylinder body, and operation efficiency and product quality are improved.

Description

Technical Field

[0001] This invention relates to the field of diesel engine technology, and in particular to an automatic cylinder block tilting device and method for marine diesel engines. Background Technology

[0002] The cylinder block is a large structural component of marine low-speed diesel engines. It has a rectangular shape, with dimensions of up to 10 meters long, 2 meters wide, and 2.5 meters high. The cylinder block is generally composed of multiple single-cylinder sections, typically made of ductile iron. In large low-speed diesel engines, a single cylinder block section can weigh over 30 tons, and the entire cylinder block can weigh over 100 tons. The cylinder block is one of the three major structural components of marine low-speed diesel engines, used to support the installation of numerous other engine parts, and requires high machining precision. During cylinder block production, all four planes and the holes on them need to be machined. The entire cylinder block is generally machined on a CNC floor-type milling machine, machining only one plane at a time. After one plane is finished, it needs to be rotated 90 degrees to machine another plane. The existing technology uses a crane and wire ropes to tilt the cylinder block. For horizontal lifting, the middle section of the wire rope is attached to the crane hook, and both ends of the wire rope pass through the cylinder block from both sides and are connected by shackles. Fabric-covered shims are used for protection at the machined surfaces and corners. The hook rises smoothly, lifting the cylinder block. For tilting the cylinder block, two sets of wire rope main hooks are suspended from the main hook and auxiliary hook of the crane. The wire ropes pass through the flange holes on the sides and are connected by shackles on the other side of the cylinder block. The same operation is performed on the wire ropes attached to the auxiliary hooks. Fabric-covered shims are used for protection at all points where the wire ropes contact the machined surfaces of the cylinder block. Then, the main hook is slowly raised, and the auxiliary hook is gradually lowered, causing the cylinder block to slowly tilt from one side to the other until it tilts 90 degrees. Finally, all fabric-covered shims are removed, completing one tilt.

[0003] The machined surface of the cylinder block needs to be protected from damage by the wire rope during the flipping process. However, using the current conventional cylinder block flipping method, multiple flipping operations are required during the machining of a single cylinder block. Since cylinder blocks are large components, with a single cylinder block typically weighing over 100 tons, the wire ropes used are thick and heavy, and threading the wire ropes requires considerable physical strength. The flipping process also easily causes the wire rope to damage the workpiece surface, making it difficult to avoid damage and resulting in quality defects. Furthermore, the operation is cumbersome and places high demands on the lifting operators. Summary of the Invention

[0004] The purpose of this invention is to provide an automatic cylinder block tilting device for marine diesel engines, which is simple to operate and will not damage the cylinder block surface.

[0005] To achieve this objective, the present invention adopts the following technical solution: an automatic tilting device for marine diesel engine cylinder blocks, comprising a pit, a support bracket, a tilting support, and two drive components. The support bracket is placed on the ground and spans across the pit. The tilting support includes two vertically connected support frames, each with an inner support surface suitable for supporting the cylinder block to be processed. The tilting support has a first posture in which the outer wall of one support frame abuts parallel to the support bracket, and a second posture in which the outer wall of the other support frame abuts parallel to the support bracket. The two drive components are symmetrically arranged along the length of the support bracket and correspond one-to-one with the support frames. Each drive component includes at least one hydraulic cylinder, one end of which is rotatably mounted on the bottom of the pit via a support seat, and the other end passes through the support bracket and is hinged to the outer wall of the corresponding support frame. The two drive components cooperate to drive the tilting support to reciprocate between the first posture and the second posture.

[0006] Preferably, the drive assembly further includes a controller, the support base is equipped with a first angle sensor for detecting the rotation angle of the hydraulic cylinder, the tilting bracket is equipped with a second angle sensor for detecting the rotation angle of the tilting bracket, and the controller is connected to the first angle sensor, the second angle sensor and the hydraulic cylinder respectively.

[0007] Preferably, the hydraulic cylinder is a double-acting hydraulic cylinder.

[0008] Preferably, the support bracket is provided with a central longitudinal beam and a central transverse beam, which are arranged perpendicularly to each other. A hollow portion is defined between the central longitudinal beam, the central transverse beam and the inner wall of the support bracket for the hydraulic cylinder to pass through. When the flipping bracket is in the first posture or the second posture, the outer wall of the flipping bracket abuts against the central longitudinal beam and the central transverse beam.

[0009] Preferably, the outer wall at the connection between the two support frames has a rounded corner structure.

[0010] Preferably, a non-metallic protective component is provided between the support surface and the diesel engine, the non-metallic protective component being fixedly connected to the support surface and abutting against the cylinder block.

[0011] Preferably, the non-metallic protective component includes a plurality of sleepers, which extend along the length of the support frame and are equidistant from each other along the width of the support frame.

[0012] Preferably, a weight-reducing hole is provided between two adjacent sleepers, and the weight-reducing hole extends through the support frame along the wall thickness direction of the support frame.

[0013] Preferably, the length of the sleeper is greater than the width or height of the cylinder body along the length direction of the support bracket.

[0014] Another objective of this invention is to provide a method for automatically tilting the cylinder block of a marine diesel engine, which is simple to operate and does not damage the surface of the cylinder block.

[0015] To achieve this objective, the present invention adopts the following technical solution: a method for automatically tilting the cylinder block of a marine diesel engine, implemented by the aforementioned automatic tilting device for the cylinder block of a marine diesel engine, comprising: Set the flipping speed and start the drive component; Acquire the angle signal detected by the second angle sensor, and calculate the desired angle after n seconds based on the angle signal and the flipping speed; The output pressure of the hydraulic cylinder is controlled according to the desired angle.

[0016] The beneficial effects of this invention are as follows: When the flipping device is in use, the cylinder body with one side processed is placed on the flipping bracket. At this time, one of the support frames is parallel to and abuts against the support bracket, and the support surfaces of the two support frames abut against the two sides of the cylinder body respectively. The processed sidewall of the cylinder body is located at the top of the cylinder body and is parallel to the support bracket. Then, the two drive components are activated. The hydraulic cylinder of one drive component extends, and the hydraulic cylinder of the other drive component retracts, driving the flipping bracket and the cylinder body to rotate. After the flipping bracket rotates 90°, the other support frame is parallel to and abuts against the support bracket, causing the unprocessed sidewall of the cylinder body that is not in contact with the support frame to flip to the top of the cylinder body and be parallel to the support bracket, thus realizing the flipping of the cylinder body. By setting up the flipping bracket and drive components, there is no need for fasteners or wire ropes to connect the flipping bracket and the cylinder body. The drive component has a simple structure and is easy to control, which can simplify the flipping device mechanism and the cylinder body installation steps, while avoiding the wire rope from damaging the cylinder body surface, improving work efficiency and product quality. In addition, by setting up a pit-mounted hydraulic cylinder, the support bracket can be directly fixed to the bottom surface, reducing the height of the cylinder body, facilitating subsequent lifting, and further improving work efficiency.

[0017] The present invention also provides an automatic tilting method for marine diesel engine cylinder blocks, which uses a tilting bracket to tilt the cylinder block and controls the tilting bracket to rotate at a uniform speed to ensure stable tilting and avoid damage to the hydraulic cylinder. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the automatic cylinder tilting device of the marine diesel engine in the first position according to an embodiment of this application; Figure 2 This is a schematic diagram of the automatic cylinder tilting device of the marine diesel engine in the second posture according to an embodiment of this application; Figure 3This is a top view of the automatic tilting device for marine diesel engine cylinder blocks according to an embodiment of this application; Figure 4 This is a schematic diagram of the cylinder block installation according to an embodiment of this application; Figure 5 This is a force analysis diagram of the automatic tilting device for marine diesel engine cylinder block according to an embodiment of this application; Figure 6 This is a flowchart illustrating the steps of an automatic cylinder block tilting method for marine diesel engines according to an embodiment of this application.

[0019] In the diagram: 1. Pit; 11. Support base; 2. Support bracket; 21. Central longitudinal beam; 22. Central transverse beam; 23. Hollowed-out section; 3. Tilting bracket; 31. Support frame; 32. Non-metallic protective component; 33. Weight reduction hole; 34. Hinge seat; 4. Drive assembly; 41. Hydraulic cylinder; 5. Cylinder body. Specific Implementation The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, and not all of the structures.

[0021] In the description of this invention, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0023] In the description of this embodiment, the terms "upper," "lower," "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the present invention. In addition, the terms "first" and "second" are used only for distinction in description and have no special meaning.

[0024] Reference Figures 1 to 5 As shown, an automatic tilting device for a marine diesel engine cylinder block 5 according to an embodiment of this application includes a pit 1, a support bracket 2, a tilting bracket 3, and two drive components 4. The pit 1 is located on the ground and has an inverted trapezoidal cross-section. The support bracket 2 is placed on the ground and spans across the pit 1. The tilting bracket 3 includes two vertically connected support frames 31, i.e., the tilting bracket 3 has a symmetrical structure with an L-shaped cross-section. The inner sides of both support frames 31 have support surfaces suitable for supporting the cylinder block 5 to be processed. The tilting bracket 3 has a first posture in which the outer wall of the right support frame 31 abuts parallel to the support bracket 2, and a second posture in which the outer wall of the left support frame 31 abuts parallel to the support bracket 2. Two drive components 4 are symmetrically arranged along the length of the support bracket 2 and correspond one-to-one with the support frame 31. Each drive component 4 includes at least one hydraulic cylinder 41, which has a fixed end and a telescopic end. The fixed end is rotatably connected to the support base 11 fixed to the bottom of the pit 1, and the telescopic end passes through the support bracket 2 and is hinged to the hinge seat 34 on the outer wall of the corresponding support frame 31. The two drive components 4 cooperate to drive the flipping bracket 3 to reciprocate between a first posture and a second posture. In this embodiment, both the support bracket 2 and the flipping bracket 3 are made of high-strength alloy steel. Each drive component 4 includes two hydraulic cylinders 41, which are spaced apart along the width of the support frame 31. In this embodiment, the length direction of the support bracket 2 is the left-right direction, which is specifically mentioned here and will not be repeated hereafter.

[0025] Understandably, when the flipping device is in use, the cylinder body 5, which has been processed on one side, is placed on the flipping bracket 3. At this time, one of the support frames 31 is parallel to and abuts against the support bracket 2, and the support surfaces of the two support frames 31 abut against the two sides of the cylinder body 5 respectively. The processed side wall of the cylinder body 5 is located at the top of the cylinder body 5 and is parallel to the support bracket 2. Then, the two drive components 4 are started. The hydraulic cylinder 41 of one drive component 4 extends, and the hydraulic cylinder 41 of the other drive component 4 retracts, driving the flipping bracket 3 and the cylinder body 5 to rotate. After the flipping bracket 3 rotates 90°, the other support frame 31 is parallel to and abuts against the support bracket 2, so that the unprocessed side wall of the cylinder body 5, which is not in contact with the support frame 31, flips to the top of the cylinder body 5 and is parallel to the support bracket 2, thus realizing the flipping of the cylinder body 5.

[0026] By setting up the tilting bracket 3 and the drive assembly 4, no fasteners or wire ropes are needed to connect the tilting bracket 3 and the cylinder body 5. The drive assembly 4 has a simple structure and is easy to control, which simplifies the installation steps of the tilting device mechanism and the cylinder body 5, while avoiding damage to the surface of the cylinder body 5 by the wire rope, thus improving work efficiency and product quality. In addition, by setting up a pit 1 to house the hydraulic cylinder 41, the support bracket 2 can be directly fixed to the bottom surface, reducing the height of the cylinder body 5 and facilitating subsequent lifting, further improving work efficiency.

[0027] Since the hydraulic cylinders 41 of the two drive components 4 need to extend and retract synchronously to achieve the tilting of the cylinder body 5, when the extension amount (or output pressure) of one hydraulic cylinder 41 and the retraction amount (or output pressure) of the other hydraulic cylinder 41 are mismatched, the tilting bracket 3 will stall. This may not only cause pressure fluctuations and slippage of the cylinder body 5, but may also cause a sharp increase in load on the retracted hydraulic cylinder 41, resulting in the hydraulic cylinder 41 losing pressure and being damaged.

[0028] Reference Figure 5 As shown, the drive assembly 4 also includes a controller. The support base 11 is equipped with a first angle sensor for detecting the rotation angle of the hydraulic cylinder 41, and the tilting bracket 3 is equipped with a second angle sensor for detecting the rotation angle of the tilting bracket 3. The controller is connected to the first angle sensor, the second angle sensor, and the hydraulic cylinder 41 respectively. In this embodiment, the controller can be centralized or distributed. For example, the controller can be a single microcontroller or composed of multiple distributed microcontrollers. The microcontroller can run a control program to control and implement its functions.

[0029] By setting up angle sensors and controllers, during the rotation of cylinder body 5, the first angle sensor can detect the rotation angle of hydraulic cylinder 41 (the angle between hydraulic cylinder 41 and the horizontal plane), and the second angle sensor can detect the rotation angle of the rotating bracket 3. The controller can control the output pressure of hydraulic cylinder 41 according to the rotation angle of hydraulic cylinder 41, ensuring that the horizontal pressure components of the two hydraulic cylinders 41 cancel each other out, ensuring that the rotation center of the rotating bracket 3 is horizontally stable. At the same time, the controller controls the output net torque of hydraulic cylinder 41 according to the rotation angle of the rotating bracket 3, so that the output torque of drive assembly 4 cancels out the gravitational torque of hydraulic cylinder 41. The hydraulic cylinders 41 of the two drive assemblies 4 work together to achieve uniform rotation of cylinder body 5, avoid slippage of cylinder body 5, and at the same time ensure stable load on hydraulic cylinder 41, extending the service life of hydraulic cylinder 41.

[0030] Preferably, the hydraulic cylinder 41 is a double-acting hydraulic cylinder.

[0031] A double-acting hydraulic cylinder is a hydraulic cylinder 41 in which pressurized oil can be supplied to both sides of the piston. By setting a double-acting hydraulic cylinder, the double-acting hydraulic cylinder provides stroke output in two directions, so that the hydraulic cylinder 41 can provide stable pressure when extending or retracting, further improving the stability of the tilting device.

[0032] Reference Figure 3 As shown, it can be understood that the support bracket 2 is provided with a central longitudinal beam 21 and a central transverse beam 22. The central longitudinal beam 21 is located at the center of the support bracket 2 along the length direction of the support bracket 2 and extends from one end of the support bracket 2 to the other end along the width direction of the support bracket 2. The central transverse beam 22 is located at the center of the support bracket 2 along the width direction of the support bracket 2 and extends from one end of the support bracket 2 to the other end along the length direction of the support bracket 2. The central longitudinal beam 21 and the central transverse beam 22 are arranged perpendicularly and intersectingly. A hollow portion 23 is defined between the central longitudinal beam 21, the central transverse beam 22 and the inner wall of the support bracket 2 for the hydraulic cylinder 41 to pass through (since each drive assembly 4 in this application includes two hydraulic cylinders 41, there are four hollow portions 23 in total). When the flipping bracket 3 is in the first posture or the second posture, the outer wall of the flipping bracket 3 abuts against the central longitudinal beam 21 and the central transverse beam 22. Specifically, when the flip bracket 3 is in the first posture, the connection between the two support frames 31 of the flip bracket 3 abuts against the central longitudinal beam 21, and the right support frame 31 abuts against the central cross beam 22 and the right side of the support bracket 2; when the flip bracket 3 is in the second posture, the connection between the two support frames 31 of the flip bracket 3 abuts against the central longitudinal beam 21, and the left support frame 31 abuts against the central cross beam 22 and the left side of the support bracket 2.

[0033] By setting the central longitudinal beam 21 and the central transverse beam 22, on the one hand, the central longitudinal beam 21 and the central transverse beam 22 are respectively connected to the four side walls of the support frame 31, which can play a strengthening role, effectively improve the mechanical structural strength of the support bracket 2, and improve the structural stability of the support bracket 2; on the other hand, the central longitudinal beam 21 and the central transverse beam 22 provide stable support for the tilting bracket 3 before and after tilting, disperse the pressure of the cylinder body 5, and improve the installation stability of the cylinder body 5.

[0034] Furthermore, the outer wall of the connection between the two support frames 31 (i.e., the corner of the flip bracket 3) is a rounded corner structure.

[0035] The outer wall of the corner of the tilting bracket 3 is set as a rounded structure. When the hydraulic cylinder 41 drives the tilting bracket 3 to rotate, the rounded structure makes linear contact with the central longitudinal beam 21 and can evenly distribute the friction force to the two support frames 31, reducing the friction and wear between the tilting bracket 3 and the support bracket 2, and further improving the stability of the tilting device.

[0036] Reference Figures 1 to 4As shown, it can be understood that a non-metallic protective component 32 is provided between the support surface and the diesel engine. The non-metallic protective component 32 is fixed to the support surface and abuts against the cylinder block 5.

[0037] By setting a non-metallic protective component 32, direct contact between the cast iron cylinder block 5 and the alloy material flipping bracket 3 can be avoided, which plays a buffering and protective role and prevents the machined surface of the cylinder block 5 from directly contacting the metal flipping bracket 3 during flipping, thus avoiding scratches or damage.

[0038] Furthermore, the non-metallic protective component 32 includes a plurality of sleepers, which extend along the length of the support frame 31 and are equidistant from each other along the width of the support frame 31.

[0039] Setting the non-metallic protective component 32 as a sleeper has several advantages. Firstly, wood is relatively soft and easy to cut and drill according to the specific size and shape of the flip bracket 3, which can reduce the layout cost of the non-metallic protective component 32 and facilitate its assembly and use.

[0040] Preferably, a weight-reducing hole 33 is provided between two adjacent sleepers, and the weight-reducing hole 33 penetrates through the support frame 31 along the wall thickness direction of the support frame 31. In other words, the support frame 31 itself is a hollow structure, and the sleeper spans the hollow part 23 of the support frame 31, so that the hollow part 23 not covered by the sleeper forms the weight-reducing hole 33.

[0041] By setting the weight reduction hole 33, the weight of the support frame 31 can be significantly reduced. Combined with the lighter sleepers, the load on the hydraulic cylinder 41 can be effectively reduced, which helps to reduce the complexity and operation difficulty of the entire tilting device.

[0042] Reference Figure 4 As shown, it can be understood that the length of the sleeper is greater than the width or height of the cylinder block 5 along the length direction of the support bracket 2.

[0043] The length of the sleeper is set to be greater than the width or height of the cylinder block 5 it is in contact with, ensuring that the sleeper is completely in contact with the side wall of the cylinder block 5, distributing the weight of the cylinder block 5, and further improving the support stability of the sleeper.

[0044] Reference Figure 6 As shown, a method for automatically tilting a marine diesel engine cylinder block 5 according to an embodiment of this application is implemented using the aforementioned automatic tilting device for the marine diesel engine cylinder block 5, and includes: S1. Set the flipping speed and start drive component 4; Specifically, in the initial state, the tilting bracket 3 is in a first posture (or a second posture), and both the cylinder body 5 and the tilting bracket 3 are stationary relative to the support base 11. At this time, the right hydraulic cylinder 41 extends and applies a first pressure to the tilting bracket 3, while the left hydraulic cylinder 41 retracts simultaneously and provides a second pressure (less than the first pressure). This causes the tilting bracket 3 to overcome the gravitational torque of the cylinder body 5 and obtain an initial torque. Under the action of the initial torque, the tilting bracket 3 and the cylinder body 5 begin to rotate. The first and second pressures output by the two hydraulic cylinders 41 directly determine the magnitude of the initial torque, and thus the rotational speed of the tilting bracket 3. Therefore, the operator can control the initial rotational speed of the tilting bracket 3 by controlling the output pressure of the hydraulic cylinders 41.

[0045] S2. Obtain the angle signal detected by the second angle sensor, and calculate the expected angle of rotation of the flipping bracket 3 after n seconds based on the angle signal and the flipping speed. n is the total time required between the controller receiving the angle signal and the hydraulic cylinder 41 changing the pressure according to the control command. In this embodiment, n is 1 second. In other embodiments, n can also be set to 50 milliseconds or 3 seconds, etc. Under the premise that the flipping bracket 3 rotates at a constant speed, the rotation angle of the flipping bracket 3 at the current time is obtained by the second angle sensor. The controller can calculate the expected angle of the flipping bracket 3 in the subsequent time (before the flipping bracket 3 decelerates and stops), and define the expected angle as θ.

[0046] S3. Control the output pressure of hydraulic cylinder 41 according to the desired angle θ.

[0047] Specifically, in this embodiment, there are 2 hydraulic cylinders 41 on each side, the weight of the cylinder body 5 is G, the rotation angle of the right hydraulic cylinder 41 is a, the pressure is F1, the rotation angle of the left hydraulic cylinder 41 is b, the pressure is F2, the rotation center of the tilting bracket 3 is O, and the rotation angle is θ. For ease of calculation, it is necessary to ensure that the rotation center position of the tilting bracket 3 remains unchanged, and that the tilting bracket 3 has no lateral or vertical displacement. Therefore, the tilting bracket 3 must satisfy the following: F1×cosa=F2×cosb (1) F1×sina+F2×sinb≤G / 2 (2) When the vertical component of the pressure of the hydraulic cylinders 41 on both sides is less than the weight of the cylinder body 5, the central longitudinal beam 21 can distribute the weight of the cylinder body 5. Therefore, Equation 2 has a condition where the less than sign holds.

[0048] When the flipping bracket 3 rotates uniformly (with a constant angular velocity) around a fixed axis, its angular acceleration is zero, therefore the net torque is zero, meaning the algebraic sum of the torques of all external forces about the center of rotation O is zero. This leads to the following equation: M1(θ)+M2(θ)+M G (θ)=0 (3) Where: M1(θ) is the torque of the right hydraulic cylinder 41 (F1) about the rotation center O, its magnitude is equal to F1×d1(θ), and d1(θ) is the lever arm of F1 about the rotation center O; M2(θ) is the torque of the left hydraulic cylinder 41 (F2) about the rotation center O, its magnitude is equal to F2×d2(θ), and d2(θ) is the lever arm of F2 about the rotation center O; M G (θ) is the torque of gravity about the axis of rotation, and its magnitude is equal to G / 2×L. G (θ), the direction is opposite to the total torque of hydraulic cylinder 41, and LG(θ) is the perpendicular distance from the line of action of gravity to the axis of rotation. Therefore, equation 3 can be equivalently transformed into: F1d1(θ)+F2d2(θ)=M G (θ) (4) The angle θ in the formula can be measured by the second angle sensor. Since the position of the rotation center O remains unchanged, the lever arm function from the center of mass of cylinder block 5 to the rotation axis is L. G (θ) can be obtained through CAD model or calibration and is pre-stored in the controller. Therefore, the controller can directly calculate the gravitational torque M by the rotation angle θ of the flipping bracket 3. G (θ). Since the hinge 34 on the side wall of the flipping bracket 3 is fixed, the lever arm variation functions d1(θ) and d2(θ) with respect to the angle are derived from the installation geometry of the hydraulic cylinder 41 (hinge point coordinates, rotation center O position) with the rotation center O as the origin, establishing polar coordinates. Combining equations 1, 2, and 4, we can obtain: F1=M G (θ)cosb / (cosbd1(θ)+cosad2(θ)) F2= M G (θ)cosa / (cosbd1(θ)+cosad2(θ)) Understandably, the controller controls the output pressure of the hydraulic cylinder 41 based on the acquired angle parameters, thereby enabling the tilting bracket 3 to maintain a uniform rotation speed, ensuring stable tilting and preventing damage to the hydraulic cylinder 41.

[0049] Obviously, the above embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the implementation of the present invention. Those skilled in the art will be able to make various obvious changes, readjustments, and substitutions without departing from the scope of protection of the present invention. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the scope of protection of the claims of the present invention.

Claims

1. An automatic cylinder tilting device for a marine diesel engine, characterized in that, include: Pit (1); A support bracket (2) is placed on the ground and spans across the pit (1); The flipping bracket (3) includes two vertically connected support frames (31). The inner sides of the two support frames (31) each have a support surface suitable for supporting the cylinder body (5) to be processed. The flipping bracket (3) has a first posture in which the outer wall of one of the support frames (31) abuts parallel to the support bracket (2) and a second posture in which the outer wall of the other support frame (31) abuts parallel to the support bracket (2). Two drive components (4) are symmetrically arranged along the length of the support bracket (2) and are corresponding to the support frame (31). Each drive component (4) includes at least one hydraulic cylinder (41). One end of the hydraulic cylinder (41) is rotatably mounted on the bottom surface of the pit (1) through the support base (11), and the other end passes through the support bracket (2) and is hinged to the outer wall of the corresponding support frame (31). The two drive components (4) cooperate to drive the flipping bracket (3) to flip back and forth between the first posture and the second posture.

2. The automatic cylinder tilting device for marine diesel engines according to claim 1, characterized in that, The drive assembly (4) further includes a controller. The support base (11) is equipped with a first angle sensor for detecting the rotation angle of the hydraulic cylinder (41). The flipping bracket (3) is equipped with a second angle sensor for detecting the rotation angle of the flipping bracket (3). The controller is connected to the first angle sensor, the second angle sensor and the hydraulic cylinder (41) respectively.

3. The automatic cylinder tilting device for marine diesel engines according to claim 2, characterized in that, The hydraulic cylinder (41) is a double-acting hydraulic cylinder.

4. The automatic cylinder tilting device for marine diesel engines according to claim 2, characterized in that, The support bracket (2) is provided with a central longitudinal beam (21) and a central transverse beam (22). The central longitudinal beam (21) and the central transverse beam (22) are arranged perpendicularly and intersecting each other. A hollow part (23) is defined between the central longitudinal beam (21), the central transverse beam (22) and the inner wall of the support bracket (2) for the hydraulic cylinder (41) to pass through. When the flipping bracket (3) is in the first posture or the second posture, the outer wall of the flipping bracket (3) abuts against the central longitudinal beam (21) and the central transverse beam (22).

5. The automatic cylinder tilting device for marine diesel engines according to claim 2 or 4, characterized in that, The outer wall at the connection between the two support frames (31) has a rounded corner structure.

6. The automatic cylinder tilting device for marine diesel engines according to claim 2, characterized in that, A non-metallic protective component (32) is provided between the support surface and the diesel engine. The non-metallic protective component (32) is fixed to the support surface and abuts against the cylinder block (5).

7. The automatic cylinder tilting device for marine diesel engines according to claim 6, characterized in that, The non-metallic protective component (32) includes a plurality of sleepers, which extend along the length direction of the support frame (31) and are equidistant from each other along the width direction of the support frame (31).

8. The automatic cylinder tilting device for marine diesel engines according to claim 7, characterized in that, A weight-reducing hole (33) is provided between two adjacent sleepers, and the weight-reducing hole (33) penetrates the support frame (31) along the wall thickness direction of the support frame (31).

9. The automatic cylinder tilting device for marine diesel engines according to claim 7, characterized in that, Along the length of the support bracket (2), the length of the sleeper is greater than the width or height of the cylinder body (5).

10. A method for automatically tilting the cylinder block of a marine diesel engine, implemented using the automatic tilting device for the cylinder block of a marine diesel engine as described in any one of claims 2-9, characterized in that... include: Set the flipping speed and start the drive component (4); Acquire the angle signal detected by the second angle sensor, and calculate the desired angle after n seconds based on the angle signal and the flipping speed; The output pressure of the hydraulic cylinder (41) is controlled according to the desired angle.

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