Marine diesel engine vibration isolation base

Abstract

The present application relates to the field of marine power equipment vibration isolation, especially to a marine diesel engine vibration isolation base, comprising: a lower crossbeam base and an upper crossbeam base, a hydraulic damping module is arranged between the lower crossbeam base and the upper crossbeam base, the hydraulic damping module is sequentially provided with a vertical damping rubber pad, an oblique buffer module, a guide body block and a mechanical damping module from top to bottom, a mounting groove at the upper part of the upper crossbeam base and the 45-degree oblique buffer module form a matched mechanical transmission structure, the vertical damping rubber pad bears the absorption and buffering of vertical vibration, and the mechanical damping module is used for absorbing redundant vibration in the system transmission process; beneficial effects: by installing a composite multi-stage damping structure, the 45-degree oblique buffer module cooperates with the vertical damping rubber pad and the mechanical damping module, synchronous buffering of oblique, lateral and multidirectional vibration of the diesel engine is realized, the purpose of omnidirectional vibration isolation is achieved, the damping efficiency is improved, and vibration transmission to the ship body is avoided.

Description

Technical Field

[0001] This invention is a vibration isolation base for marine diesel engines, belonging to the field of vibration isolation for marine power equipment. Background Technology

[0002] In marine propulsion systems, diesel engines, as power equipment, generate periodic vibrations and impact loads during operation. If such vibrations are directly transmitted to the hull structure, they can easily affect the stability of equipment operation and the comfort of passengers. Traditional marine diesel engine vibration damping devices mostly use independent rubber damping pads, vertically arranged hydraulic dampers, or simple spring assemblies. Vibration buffering is achieved through the compression and rebound of elastic elements, and vibration energy is consumed by hydraulic damping structures to reduce the vibration transmission efficiency between the diesel engine and the hull. This is currently a common technical form for vibration isolation and reduction of marine propulsion equipment.

[0003] Traditional vibration reduction devices are mostly based on a single-direction, single-form damping structure. Through the cooperation of vertically arranged elastic elements and damping mechanisms, they can effectively absorb and attenuate the vertical vibrations generated by diesel engines. Under normal operating conditions, they can meet the vibration isolation requirements of the foundation and provide relatively mature technical support for the stable operation of marine diesel engines. They are widely used in vibration reduction installation structures of various ship power bases.

[0004] Existing vibration isolation devices for marine diesel engines mainly consist of vertically arranged rubber damping pads or single-stage hydraulic dampers, which can only buffer vertical vibrations and are difficult to withstand and attenuate the lateral composite loads and impacts generated during diesel engine operation. The vibration reduction direction is singular and the adaptability is poor. At the same time, traditional structures generally adopt a single damping or single elastic vibration reduction mode. Hydraulic vibration reduction and mechanical vibration reduction are independent of each other and cannot work together. Redundant vibration is difficult to further eliminate, and the multi-stage vibration reduction effect is insufficient. Summary of the Invention

[0005] To address the shortcomings of existing technologies, the present invention aims to provide a vibration isolation base for marine diesel engines. This addresses the problems of existing vibration isolation devices for marine diesel engines, which mainly consist of vertically arranged rubber damping pads or single-stage hydraulic dampers. These devices can only buffer vertical vibrations and are unable to withstand or attenuate lateral composite loads and impacts generated during diesel engine operation. Furthermore, they have a single damping direction and poor adaptability. In addition, traditional structures generally adopt a single damping or single elastic damping mode, and hydraulic and mechanical damping are independent and cannot work together, making it difficult to further eliminate redundant vibrations and resulting in insufficient multi-stage damping effect.

[0006] To achieve the above objectives, the present invention is implemented through the following technical solution: a marine diesel engine vibration isolation base, the structure of which includes: a lower crossbeam base and an upper crossbeam base, wherein a plurality of paired hydraulic vibration damping modules are arranged between the lower crossbeam base and the upper crossbeam base, and a special molding installation groove is provided at the bottom of the upper crossbeam base, wherein the hydraulic vibration damping module is provided with, from top to bottom, a vertical vibration damping rubber pad, an oblique buffer module, a guide block, and a mechanical vibration damping module, and the oblique buffer module is arranged at a 45° angle and adapted to be installed in the special molding installation groove at the bottom of the upper crossbeam base; The mounting groove on the upper part of the upper crossbeam base and the 45° inclined buffer module form a matching mechanical transmission structure, so that the vibration generated by the diesel engine can be stably transmitted to the inclined buffer module to achieve buffering and energy dissipation. The vertical vibration damping rubber pad is set inside the special molded mounting groove and is located between the guide block and the upper crossbeam base. The lower crossbeam base and the upper crossbeam base are elastically connected by the vertical vibration damping rubber pad. The vertical vibration damping rubber pad simultaneously undertakes the absorption and buffering of vertical vibration. The mechanical vibration damping module is used to absorb the redundant vibration during the transmission process of the system.

[0007] Preferably, the guide block is fastened to the lower crossbeam base by bolts. The guide block has a hydraulic damping groove adapted to the inclined buffer module. Two cylindrical guide walls are integrally formed and extend into the hydraulic damping groove. The cylindrical guide walls extend into the inclined buffer module to form a guiding fit. The inclined buffer module includes an inclined rubber pad, a metal base plate, and a vibration transmission block. The left and right sides of the vibration transmission block have symmetrical guide grooves adapted to the cylindrical guide walls. The cylindrical guide walls and the corresponding guide grooves form a sliding guiding fit. The inclined buffer module also includes a hydraulic rod, a working piston, and a two-stage progressive damping module. The working piston is coaxially arranged inside the cylindrical guide wall. The two-stage progressive damping module is located at the bottom of the working piston and is equipped with a matching oil reservoir and a damping piston valve. The two-stage progressive damping module and the working piston form a series hydraulic damping structure. A square main damping spring is also provided between the vibration transmission block and the hydraulic damping groove.

[0008] Preferably, the tail end of the vibration transmission block is connected to a vibration transmission rocker plate, which is located inside the guide block. The vibration transmission rocker plate and the vibration transmission block are connected by an arc groove structure to form a transmission fit. The mechanical vibration damping module is connected between the head of the vibration transmission rocker plate and the upper crossbeam base. The mechanical vibration damping module can directly absorb the vertical vibration transmitted from the upper beam base, and can also receive the oblique vibration from the oblique buffer module through the vibration transmission rocker, thus achieving composite absorption of vertical and oblique multi-directional vibrations.

[0009] Preferably, the working piston is fixedly connected to the vibration transmission block via a hydraulic rod. The inclined rubber pad, metal base plate, vibration transmission block, hydraulic rod, working piston, and secondary progressive vibration damping module are all arranged along the same inclined direction, and the inclination angle is consistent with the installation inclination angle of the inclined buffer module. The working piston slides in cooperation with the inner wall of the cylindrical guide wall, and the working piston and the vibration transmission block form an annular oil cavity. The two-stage progressive vibration damping module is installed at the bottom of the inner wall of the cylindrical guide wall, and divides the internal space of the cylindrical guide wall into a main buffer chamber near the working piston and a high-pressure chamber at the bottom. The high-pressure chamber is connected to the damping piston valve through an oil pipeline. The lower end of the damping piston valve is connected to the annular oil chamber. The annular oil chamber is equipped with a matching one-way valve inlet. The annular oil chamber adopts a non-full oil structure and has a built-in compressible gas space.

[0010] Preferably, the working piston has an upper buffer oil guide hole and a return oil hole inside. The upper buffer oil guide hole is provided with a low-pressure throttle valve plate in the middle. The low-pressure throttle valve plate is equipped with a low-pressure spring that abuts against it. The oil outlet end of the return oil hole is provided with a rubber flow limiting valve plate.

[0011] Preferably, the two-stage progressive vibration damping module includes a main block, a high-pressure one-way valve, a main rebound spring, a high-pressure spring, and a high-pressure throttle valve plate. A high-pressure oil guide hole is axially opened in the middle of the main block, and a high-pressure one-way valve is installed inside the high-pressure oil guide hole. The main block is installed at the bottom of the inner wall of the cylindrical guide wall, and an oil outlet hole is provided at the bottom of the high-pressure one-way valve on the main block. The oil outlet hole is connected to the high-pressure chamber. The high-pressure chamber and the main buffer chamber are connected by a connecting flow channel. A high-pressure throttling valve plate is provided in the connecting flow channel. The high-pressure throttling valve plate is equipped with a corresponding high-pressure spring. The high-pressure chamber is connected to a damping piston valve through an oil pipeline. The lower end of the damping piston valve is connected to the annular oil chamber.

[0012] Preferably, the mechanical vibration damping module includes a bottom guide seat, a spring limiting base arranged symmetrically at the top and bottom, several main vibration damping springs, vibration damping limiting rods arranged symmetrically at the left and right, a square buffer spring, and a top pressure plate. The bottom guide seat is fastened to the head of the vibration transmission rocker plate by bolts, and the top pressure plate is fastened to the bottom of the upper crossbeam base by bolts. The vibration damping limiting rod is axially connected to the lower side of the top pressure plate, and a square buffer spring is provided between the vibration damping limiting rod and the top pressure plate. The vibration damping limiting rod has an arc-shaped structure and is coaxially arranged with the rotation axis of the vibration transmission rocker. The vibration damping limiting rod is slidably sleeved on both sides of the bottom guide seat. The bottom guide seat has an arc-shaped groove that matches the vibration damping limiting rod. Several main vibration damping springs are sandwiched between the upper and lower sets of spring limiting bases. The main vibration damping springs are allowed to undergo adaptive lateral displacement with the arc guide.

[0013] Preferably, the side wall of the guide block is provided with symmetrically arranged maintenance through holes, which are connected to the internal cavity of the cylindrical guide wall. A sealing plug is detachably installed at the maintenance through hole by bolts, and the sealing plug is used to achieve internal cavity sealing and disassembly and maintenance.

[0014] The vibration isolation base for marine diesel engines of the present invention has the following effects: 1. By installing a composite multi-stage vibration reduction structure, using a 45-degree oblique buffer module in conjunction with vertical vibration reduction rubber pads and mechanical vibration reduction modules, synchronous buffering of vertical, oblique, and lateral vibrations of the diesel engine is achieved, thus achieving all-round vibration isolation, improving vibration reduction efficiency, preventing vibration from being transmitted to the hull, and enhancing the operational stability and service life of the equipment.

[0015] 2. By installing a two-stage progressive hydraulic vibration damping module, a graded vibration damping effect is achieved by first gently buffering and then high-pressure current limiting. The initial vibration impact is small and the later resistance to heavy loads is strong, achieving a smooth vibration damping process without hard impact. At the same time, the automatic rebound reset is achieved by relying on oil pressure and springs, ensuring fast response and no jamming during continuous operation.

[0016] 3. By installing a circular arc groove transmission structure and a circular arc guide vibration damping mechanism, the traditional rigid pin connection is abandoned, achieving smooth movement, no wear, and no jamming. This results in more stable vibration transmission and more uniform force distribution, effectively improving the overall structural strength and reliability. It is especially suitable for marine working conditions involving long-term heavy loads and high-frequency vibrations. Attached Figure Description

[0017] Other features, objects, and advantages of the present invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings: Figure 1 This is a schematic diagram of the structure of a marine diesel engine vibration isolation base according to the present invention; Figure 2 This is a schematic cross-sectional view of the overall structure of the present invention; Figure 3 This is a schematic diagram of the hydraulic vibration damping module structure of the present invention; Figure 4 This is a schematic diagram of the exploded structure of the hydraulic vibration damping module of the present invention; Figure 5 This is a cross-sectional view of the hydraulic vibration damping module of the present invention; Figure 6 This is a detailed structural diagram of the two-stage progressive vibration reduction module of the present invention; Figure 7 This is a detailed structural diagram of the working piston of the present invention; Figure 8 This is a detailed structural diagram of the mechanical vibration damping module of the present invention.

[0018] Explanation of reference numerals in the attached figures: 1. Lower crossbeam base; 11. Upper crossbeam base; 111. Mounting groove; 2. Hydraulic vibration damping module; 21. Vertical vibration damping rubber pad; 23. Guide block; 231. Hydraulic vibration damping groove; 232. Cylindrical guide wall; 233. Oil storage chamber; 234. Oil delivery pipeline; 235. One-way valve inlet; 236. Inspection through hole; 25. Sealing plug; 22. Angled buffer module; 221. Angled rubber pad; 222. Metal base plate; 223. Vibration transmission block; 2231. Guide groove; 2232. Circular arc slide groove; 224. Hydraulic rod; 227. Damping piston valve; 228. Square main damping spring; 225. Working piston; 2251. Upper buffer oil guide hole; 2252. Oil return hole; 2253. Low-pressure throttle valve plate; 2254. Low-pressure spring; 2255. Rubber flow limiting valve plate; 226. Two-stage progressive vibration damping module; 2261. Main block; 22611. Oil outlet; 22612. Connecting flow channel; 2262. High-pressure check valve; 2263. Main rebound spring; 2264. High-pressure spring; 2265. High-pressure throttle valve plate; 24. Mechanical vibration damping module; 241. Bottom guide seat; 2411. Arc groove; 242. Spring limiting base; 243. Main vibration damping spring; 244. Vibration damping limiting rod; 245. Square buffer spring; 246. Top pressure plate; 247. Vibration transmission rocker plate; 3. Annular oil chamber; 31. Main buffer chamber; 32. High-pressure chamber. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to specific embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0020] Furthermore, in the description of this invention, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, 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 this invention.

[0021] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral unit; 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. However, specifying a direct connection indicates that the two main bodies are not connected through a transitional structure, but rather formed as a whole through a connecting structure. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0022] In this invention, unless otherwise expressly specified and limited, the first feature "on" or "below" the second feature may be in direct contact with the first and second features, or indirect contact through an intermediate medium. In the description of this specification, references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0023] Please see Figures 1 to 8 The present invention provides a vibration isolation base for a marine diesel engine. The technical solution is as follows: The vibration isolation base for a marine diesel engine of the present invention consists of two bearing bases, an upper and a lower one, which are arranged parallel to each other and corresponding to each other, forming the bearing foundation of the entire vibration isolation device. The upper bearing base is used to fix the diesel engine body, and the lower bearing base is used to be stably connected to the ship hull foundation. At the bottom of the upper bearing base, a dedicated molded mounting groove 111 is provided. This mounting groove 111 is used to adapt to the installation of the inclined buffer module 22, ensuring that the vibration load can be stably transmitted to the vibration damping structure. Between the upper and lower bearing bases, several pairs of hydraulic vibration damping modules 2 are arranged. The hydraulic vibration damping module 2 adopts a layered integrated structure, with vertical vibration damping rubber pads 21, inclined buffer modules 22, guide blocks 23, and mechanical vibration damping modules 24 arranged sequentially from top to bottom. The inclined buffer modules 22 are arranged at a 45° angle and are adapted to be installed in the dedicated molded mounting groove 111 at the bottom of the upper bearing base. This inclined arrangement can effectively cope with multi-directional vibration impact. The guide blocks 23 are installed on the lower bearing base by bolt fastening, serving as the mounting base for the entire hydraulic vibration damping module 2 and providing stable installation and movement space for each component. The inclined buffer module 22, as a hydraulic vibration damping unit, consists of an inclined rubber pad 221, a metal base plate 222, a vibration transmission block 223, a hydraulic rod 224, a working piston 225, a two-stage progressive vibration damping module 226, a damping piston valve 227, and a square main vibration damping spring 228. The inclined rubber pad 221 is located at the top of the inclined buffer module 22 and fits tightly against the inner wall of the special molded mounting groove 111 of the upper bearing base. It is used to initially absorb vibration and avoid rigid collisions between metal parts. The metal base plate 222 is located below the inclined rubber pad 221 and plays the role of bearing and transmitting force, transmitting vibration to the vibration transmission block 223. The vibration transmission block 223 has symmetrical guide grooves 2231 on both sides, which form a sliding fit with the cylindrical guide structure in the guide body block 23. A square main damping spring 228 is also provided between the vibration transmission block 223 and the hydraulic damping groove 231 to directly and elastically buffer the vibration transmission block 223 and further absorb vibration energy. The tail of the vibration transmission block 223 is connected to the vibration transmission rocker plate 247, which is located inside the guide block 23. The two are connected by a circular arc groove 2232 structure to form a transmission fit. The vibration transmission block 223 is fixedly connected to the working piston 225 through the hydraulic rod 224 to ensure that the vibration of the vibration transmission block 223 can be synchronously transmitted to the working piston 225, driving the working piston 225 to reciprocate inside the cylindrical guide structure. All components in the inclined buffer module 22 are arranged along the same inclined direction, consistent with the 45° installation angle of the inclined buffer module 22, to avoid motion interference. The working piston 225 is coaxially arranged inside the cylindrical guide structure, forming a sliding fit with the inner wall of the guide structure. The working piston 225 and the vibration transmission block 223 enclose an annular oil chamber 3, which provides space for the storage and flow of hydraulic oil. It is equipped with a one-way valve inlet 235 to replenish hydraulic oil and prevent backflow of oil. At the same time, the annular oil chamber 3 adopts a non-full oil structure and has a built-in compressible gas space. The gas elasticity is combined with the hydraulic oil damping to improve the buffering stability. There are two oil guide channels inside the working piston 225: an upper buffer oil guide hole 2251 and a return oil hole 2252. A low-pressure throttle valve plate 2253 is provided in the middle of the upper buffer oil guide hole 2251. The valve plate is equipped with a low-pressure spring 2254 that abuts against it. The opening and closing of the valve plate is controlled by the spring preload, thereby controlling the flow rate of hydraulic oil. The oil outlet end of the return oil hole 2252 is equipped with a rubber flow limiting valve plate 2255 to realize one-way flow limiting and damping control of oil. The secondary progressive damping module 226 is located at the bottom of the working piston 225, forming a series hydraulic damping structure with the working piston 225. The main body block 2261 is installed on the bottom of the inner wall of the cylindrical guide structure, serving as the mounting base for the secondary progressive damping module 226. A high-pressure oil guide hole is axially opened in the middle of the block, and a high-pressure one-way valve 2262 is installed inside to control the one-way flow of hydraulic oil. The bottom of the main body block 2261 is provided with an oil outlet hole 22611, which is connected to the high-pressure chamber 32. The high-pressure chamber 32 is connected to the main buffer chamber 31 through a connecting flow channel 22612. A high-pressure throttle valve plate 2265 is installed in the connecting flow channel 22612, and the valve plate is equipped with a high-pressure spring 2264 to form a high-pressure damping structure. Mechanical vibration damping modules 24 are connected between the head of the vibration transmission rocker 247 and the upper bearing base to absorb redundant vibrations during system transmission. The bottom guide seat 241 is fastened to the head of the vibration transmission rocker 247 with bolts, and the top pressure plate 246 is fastened to the bottom of the upper bearing base with bolts. A vibration damping limiting rod 244 is axially connected to the lower side of the top pressure plate 246, and a square buffer spring 245 is provided between the two for initial buffering of vertical vibrations. The vibration damping limiting rod 244 adopts an arc-shaped structure. The vibration-transmitting rocker 247 is coaxially mounted with the rotation axis of the rocker arm 247 and is slidably sleeved on both sides of the bottom guide seat 241. The bottom guide seat 241 is provided with an arc-shaped groove 2411 that is adapted to the vibration damping limit rod 244, ensuring that the vibration damping limit rod 244 can slide smoothly along the arc trajectory. Several main vibration damping springs 243 are sandwiched between the upper and lower sets of spring limit bases 242. The main vibration damping springs 243 are allowed to make adaptive lateral offsets with the arc guide, and can simultaneously bear vertical and oblique vibrations to achieve multi-directional buffering.

[0024] When in use, when the diesel engine starts and runs, the vertical, oblique and combined vibration loads generated during its operation are first transmitted to the upper bearing base. The special molded mounting groove 111 at the bottom of the upper bearing base directs the vibration into the oblique buffer module 22. At the same time, the vertical vibration damping rubber pad 21 located inside the special molded mounting groove 111 takes the lead in playing a role in providing preliminary elastic isolation and buffering of vertical vibration. After the vibration load is initially attenuated by the vertical damping rubber pad 21, it is transmitted to the inclined rubber pad 221 of the inclined buffer module 22. The inclined rubber pad 221 further absorbs the high-frequency micro-vibration, and then the vibration is transmitted to the vibration transmission block 223 through the metal base plate 222. At this time, the square main damping spring 228 between the vibration transmission block 223 and the hydraulic damping groove 231 exerts force synchronously to directly and elastically buffer the vibration transmission block 223, further consuming the vibration energy. Under the action of vibration, the vibration transmission block 223 moves obliquely at 45° along the cylindrical guide structure in the guide block 23. At the same time, the vibration transmission rocker plate 247 is driven smoothly through the arc slide groove 2232 structure. This arc slide groove 2232 connection method solves the problem of easy breakage of traditional rigid hinges.

[0025] Throughout the entire process, the hydraulic vibration damping module 2 and the mechanical vibration damping module 24 work together to attenuate various vibration loads generated by the diesel engine through the combination of multi-stage progressive hydraulic damping and composite mechanical buffering. When it is necessary to inspect and maintain the internal components of the device, the sealing plug 25 on the side wall of the guide block 23 can be removed, and the internal working piston 225, the secondary progressive vibration damping module 226 and other components can be disassembled, maintained and hydraulic oil replenished through the inspection through hole 236.

[0026] Detailed structure and working principle of working piston 225: Working piston 225 is the damping component of the entire inclined buffer module 22. It integrates a multi-stage damping valve system and oil flow channel. The piston body has an upper buffer guide oil hole 2251 and a return oil hole 2252. The upper buffer guide oil hole 2251 is equipped with an annular one-way valve plate, a low-pressure throttling valve plate 2253 and a throttling valve plate spring, forming a series one-way damping structure. The end of the return oil hole 2252 is equipped with a rubber flow limiting valve plate 2255, which is used to control the oil return flow rate and the damping magnitude.

[0027] During the buffer stroke, the main buffer chamber 31 is squeezed to generate high-pressure oil. The oil pressure overcomes the elastic force of the throttle valve spring, opening the low-pressure throttle valve 2253 and the annular one-way valve, allowing the oil to flow into the annular oil chamber 3 through the upper buffer guide hole 2251. Vibration energy is consumed through oil throttling and valve resistance. During the reset process, under the action of the external reset spring and the system's elastic restoring force, the oil in the annular oil chamber 3 flows in the opposite direction, overcoming the resistance of the rubber flow limiting valve 2255 and flowing back to the main buffer chamber 31 through the return oil hole 2252, so that the working piston 225 and the hydraulic rod 224 return to their initial positions, preparing for the next vibration damping and buffering.

[0028] Detailed Structure and Operation of the Second-Level Progressive Vibration Damping Module 226: The second-level progressive vibration damping module 226 serves as the high-pressure buffer and automatic rebound reset unit of this device. It is a key structure for realizing multi-level progressive vibration damping. The main body block 2261 serves as the mounting base, integrating components such as the high-pressure one-way valve 2262, oil outlet 22611, connecting flow channel 22612, high-pressure throttle valve plate 2265, and high-pressure spring 2264. It is fixedly installed at the bottom of the cylindrical guide wall 232, dividing the internal hydraulic working area into the main buffer chamber 31 and the high-pressure chamber 32. The main buffer chamber 31 is the main buffer area of ​​the entire device, with a stable and sufficient pressure-bearing volume, which can ensure that the vibration buffering process is smooth, without sudden jumps or hard impacts.

[0029] When vibration is transmitted and the working piston 225 begins to compress the main buffer chamber 31, initial gentle buffering is achieved through the volume of the main buffer chamber 31 itself and the oil damping. At this time, the oil pressure is low, and the high-pressure check valve 2262 remains closed, preventing immediate entry into the high-pressure flow restriction stage. This ensures smooth vibration reduction and no abrupt impact during initial vibration and small-amplitude vibration conditions. As the vibration load increases and the compression stroke of the working piston 225 deepens, the oil pressure in the main buffer chamber 31 continuously rises and reaches the set pressure threshold. Only then will the high-pressure check valve 2262 be opened, allowing the high-pressure oil inside the main buffer chamber 31 to flow steadily into the high-pressure chamber 32 through the oil outlet 22611. Entering the secondary high-pressure buffer stage, the oil entering the high-pressure chamber 32 is divided into two circulating damping paths. One path flows through the oil pipeline 234 to the damping piston valve 227 group, and after throttling and flow restriction, it flows into the oil storage chamber 233 to complete the low-pressure side unloading. The other path overcomes the pre-tightening force of the high-pressure spring 2264 to open the high-pressure throttling valve plate 2265, and flows back to the main buffer chamber 31 in a small flow and high-damping form. Through high-pressure throttling, the impact energy is further consumed, forming a progressive vibration reduction effect from low-pressure gentle buffering to high-pressure strong flow restriction. This avoids the problems of traditional shock absorbers being too stiff at the start and having too large an impact, and can provide sufficient damping support under heavy load impact.

[0030] During the rebound and reset phase, this module fully follows the automatic reset principle of mature hydraulic vibration dampers. When the external vibration load weakens or disappears, a pressure difference is quickly formed between the main buffer chamber 31 and the high-pressure chamber 32. The high-pressure spring 2264 releases its elastic potential energy to push the high-pressure throttle valve 2265 to reset and close. The high-pressure check valve 2262 automatically closes and locks under the action of reverse oil pressure to prevent oil backflow and pressure relief. At this time, the compressible gas space in the oil storage chamber 233 and the main rebound spring 2263 release the reset force synchronously. Together with the pressure difference between the high and low pressure chambers, they generate a stable and uniform rebound thrust, which pushes the working piston 225, hydraulic rod 224 and vibration transmission block 223 to return smoothly upward. Under the action of reset pressure, the residual oil in the high-pressure chamber 32 slowly and controllably flows back to the main buffer chamber 31 through the damping piston valve 227 group and the oil passage, so that the entire mechanism accurately returns to the initial standby position.

[0031] Working principle of mechanical vibration damping module 24: The mechanical vibration damping module 24 in this invention serves as an important auxiliary vibration damping unit for the vibration isolation base. Together with the oblique buffer module 22, it forms a dual vibration damping system combining high and low pressure and hydraulic-mechanical components. This system can effectively absorb redundant vibrations transmitted during hydraulic vibration damping, further improving the overall vibration isolation effect. The mechanical vibration damping module 24 mainly includes a bottom guide seat 241, symmetrically arranged spring limit bases 242, several main vibration damping springs 243, symmetrically arranged vibration damping limit rods 244, square buffer springs 245, and a top pressure plate 246. The components are assembled using a combination of directional guidance and elastic buffering, which can simultaneously adapt to vertical linear vibration and oblique circular trajectory vibration, avoiding the jamming, wear, and off-center load problems that are prone to occur in traditional rigid connections.

[0032] The bottom guide seat 241 is bolted to the head of the vibration transmission rocker 247 and can move synchronously with the vibration transmission rocker 247 to stably transmit oblique vibration to the mechanical vibration damping module 24. The top pressure plate 246 is bolted to the bottom of the upper crossbeam base 11 and can directly bear the vertical impact load transmitted by the upper crossbeam base 11 to realize direct vibration input. The vibration damping limit rod 244 is axially connected to the lower side of the top pressure plate 246. A square buffer spring 245 is set between the vibration damping limit rod 244 and the top pressure plate 246. The square buffer spring 245 can initially buffer and unload the vertical vibration, while ensuring the coaxiality and stability of the vibration damping limit rod 244 during the movement process and avoiding radial movement.

[0033] Explanation of the working principle of the transverse micro-floating vibration damping structure: The transverse micro-floating vibration damping structure adopted in this invention is a key innovative design proposed to address the inherent defects of the traditional rigid base of marine diesel engines. It achieves effective buffering and absorption of the transverse vibration of the diesel engine and the lateral force of the ship's roll by using a reasonable, controllable, and small-amplitude transverse floating gap in conjunction with an elastic damping mechanism, fundamentally solving the industry pain point that the traditional rigid base cannot cope with multi-directional composite vibration.

[0034] Traditional marine diesel engine vibration isolation bases generally employ a completely rigid constraint structure, with no lateral movement allowance between the base and the engine or hull. This is not because lateral movement would damage the power transmission structure, but rather due to the limitations of traditional structural design, which lacks lateral vibration reduction and displacement compensation capabilities. This rigid connection method allows the lateral vibrations generated by the diesel engine during operation and the roll loads during ship navigation to be directly and rigidly transmitted to the engine mounts, drive shaft system, and bearing components. Long-term operation can easily lead to problems such as engine mount cracking, drive shaft wear, and premature bearing failure, seriously affecting the stability and service life of the power system.

[0035] This invention achieves flexible buffering of lateral vibration by setting a reasonable and controllable micro-lateral floating gap inside the vibration isolation base and cooperating with special elastic damping elements. This structural design is fully in line with the working characteristics of marine diesel engine power transmission systems. The high-elasticity couplings, elastic floating joints or universal joints that are standard on marine diesel engines have the ability to absorb micro-radial and axial displacements. The lateral floating gap is strictly limited within the safe compensation range allowed by the transmission shaft system, which will not damage the coaxiality of the power transmission, nor affect the transmission accuracy and running stability, thus ensuring the safety and reliability of the transmission system in principle.

[0036] The lateral micro-float of this invention is not unlimited free swaying, but a controllable elastic float under the constraint of a mechanical limiting structure. It can provide lateral vibration reduction while avoiding transmission interference caused by excessive displacement. By changing the traditional rigid resistance to flexible buffer absorption of lateral vibration, it can significantly reduce the damage of lateral impact to the drive shaft, bearings and engine body, effectively reduce stress concentration and fatigue failure, and enable the vibration isolation base to have multi-dimensional vibration reduction capabilities in vertical, oblique and lateral directions. It can truly achieve all-directional composite vibration isolation and improve the operating stability, safety and service life of marine diesel engines under complex working conditions.

[0037] The above description only outlines the basic principles and preferred embodiments of the present invention. Those skilled in the art can make many changes and modifications based on the above description, and these changes and modifications should fall within the protection scope of the present invention.

[0038] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

Claims

1. A vibration isolation base for a marine diesel engine, comprising a lower crossbeam base (1) and an upper crossbeam base (11), characterized in that: Several pairs of hydraulic vibration damping modules (2) are arranged between the lower crossbeam base (1) and the upper crossbeam base (11). The bottom of the upper crossbeam base (11) is provided with a special molding installation groove (111). The hydraulic vibration damping module (2) includes a vertical vibration damping rubber pad (21), an inclined buffer module (22), a guide block (23), and a mechanical vibration damping module (24). The inclined buffer module (22) is arranged at a 45° angle and is adapted to be installed in the special molding installation groove (111) at the bottom of the upper crossbeam base (11). The vibration generated by the diesel engine can be stably transmitted to the inclined buffer module (22) to achieve buffering and energy dissipation. The vertical vibration damping rubber pad (21) is located inside the special molding installation groove (111) and between the guide block (23) and the upper crossbeam base (11). The lower crossbeam base (1) and the upper crossbeam base (11) are elastically connected through the vertical vibration damping rubber pad (21). The vertical vibration damping rubber pad (21) simultaneously undertakes the absorption and buffering of vertical vibration. The mechanical vibration damping module (24) is used to absorb the redundant vibration during the transmission process of the system. The guide block (23) is fastened to the lower crossbeam base (1) by bolts. The guide block (23) has a hydraulic damping groove (231) adapted to the inclined buffer module (22) inside. Two cylindrical guide walls (232) are integrally formed and extended inside the hydraulic damping groove (231). The cylindrical guide walls (232) extend into the inclined buffer module (22) to form a guiding fit. The inclined buffer module (22) includes an inclined rubber pad. (221) Metal base plate (222) and vibration transmission block (223). The vibration transmission block (223) has symmetrical guide grooves (2231) on its left and right sides that are adapted to the cylindrical guide wall (232). The cylindrical guide wall (232) and the corresponding guide groove (2231) form a sliding guide fit. An inclined rubber pad (221) is provided above the metal base plate (222), and a vibration transmission block (223) is provided below the metal base plate (222). The tail of the vibration transmission block (223) is connected to a vibration transmission rocker plate (247). The vibration transmission rocker plate (247) is located inside the guide body block (23), and the vibration transmission rocker plate (247) and the vibration transmission block (223) are connected by an arc groove (2232) structure to form a transmission fit. The mechanical vibration damping module (24) is connected between the head of the vibration transmission rocker plate (247) and the upper crossbeam base (11). The mechanical vibration damping module (24) can directly absorb the vertical vibration transmitted by the upper beam base (11), and can also receive the oblique vibration from the oblique buffer module (22) through the vibration transmission rocker (247), thus realizing the composite absorption of vertical and oblique multi-directional vibration.

2. The marine diesel engine vibration isolation base according to claim 1, characterized in that: The inclined buffer module (22) also includes a hydraulic rod (224), a working piston (225), and a two-stage progressive damping module (226). The working piston (225) is coaxially arranged inside the cylindrical guide wall (232). The two-stage progressive damping module (226) is located at the bottom of the working piston (225) and is equipped with a matching oil storage chamber (233) and a damping piston valve (227). The two-stage progressive damping module (226) and the working piston (225) form a series hydraulic damping structure. A square main damping spring (228) is also provided between the vibration transmission block (223) and the hydraulic damping groove (231). The working piston (225) is fixedly connected to the vibration transmission block (223) through the hydraulic rod (224).

3. The marine diesel engine vibration isolation base according to claim 2, characterized in that: The inclined rubber pad (221), metal base plate (222), vibration transmission block (223), hydraulic rod (224), working piston (225), and secondary progressive vibration damping module (226) are all arranged along the same inclined direction, and the inclination angle is consistent with the installation inclination angle of the inclined buffer module (22). The working piston (225) slides with the inner wall of the cylindrical guide wall (232), and the working piston (225) and the vibration transmission block (223) enclose an annular oil cavity (3). The secondary progressive vibration damping module (226) is installed at the bottom of the inner wall of the cylindrical guide wall (232) and divides the internal space of the cylindrical guide wall (232) into a main buffer chamber (31) near the working piston (225) and a high-pressure chamber (32) at the bottom. The high-pressure chamber (32) is connected to the damping piston valve (227) through the oil pipeline (234). The lower end of the damping piston valve (227) is connected to the oil storage chamber (233).

4. The marine diesel engine vibration isolation base according to claim 3, characterized in that: The working piston (225) has an upper buffer oil guide hole (2251) and a return oil hole (2252) inside. The upper buffer oil guide hole (2251) is provided with a low-pressure throttle valve plate (2253) in the middle. The low-pressure throttle valve plate (2253) is equipped with a low-pressure spring (2254) that abuts against it. The oil outlet end of the return oil hole (2252) is provided with a rubber flow limiting valve plate (2255).

5. The marine diesel engine vibration isolation base according to claim 4, characterized in that: The secondary progressive vibration damping module (226) includes a main block (2261), a high-pressure one-way valve (2262), a main rebound spring (2263), a high-pressure spring (2264), and a high-pressure throttle valve plate (2265). The main block (2261) has a high-pressure oil guide hole axially opened in the middle. The high-pressure one-way valve (2262) is installed in the high-pressure oil guide hole. The main block (2261) is installed at the bottom of the inner wall of the cylindrical guide wall (232). The main block (2261) has an oil outlet hole (22611) at the bottom of the high-pressure one-way valve (2262). The oil outlet hole (22611) is connected to the high-pressure chamber (32). The main rebound spring (2263) is sleeved on the outside of the main block (2261). The high-pressure chamber (32) is connected to the main buffer chamber (31) through a connecting channel (22612). The connecting channel (22612) is equipped with a high-pressure throttle valve plate (2265). The high-pressure throttle valve plate (2265) is equipped with a corresponding high-pressure spring (2264). The high-pressure chamber (32) is connected to the damping piston valve (227) through an oil pipeline (234). The lower end of the damping piston valve (227) is connected to the oil storage chamber (233).

6. The marine diesel engine vibration isolation base according to claim 1, characterized in that: The mechanical vibration damping module (24) includes a bottom guide seat (241), a spring limiting base (242) arranged symmetrically on the top and bottom, several main vibration damping springs (243), vibration damping limiting rods (244) arranged symmetrically on the left and right, a square buffer spring (245), and a top pressure plate (246). The bottom guide seat (241) is fastened to the head of the vibration transmission rocker (247) by bolts. The top pressure plate (246) is fastened to the bottom of the upper crossbeam base (11) by bolts. The vibration damping limiting rod (244) is axially connected to the lower side of the top pressure plate (246). A square buffer spring (245) is provided between the vibration damping limiting rod (244) and the top pressure plate (246). The vibration damping limiting rod (244) has an arc-shaped structure and is coaxially arranged with the rotation axis of the vibration transmission rocker (247). The vibration damping limiting rod (244) is slidably sleeved on both sides of the bottom guide seat (241). The bottom guide seat (241) is provided with an arc-shaped groove (2411) that is adapted to the vibration damping limiting rod (244). Several main vibration damping springs (243) are sandwiched between the upper and lower sets of spring limiting bases (242). The main vibration damping springs (243) are allowed to make adaptive lateral offsets with the arc guide.

7. The marine diesel engine vibration isolation base according to claim 2, characterized in that: The side wall of the guide block (23) is provided with symmetrically arranged maintenance through holes (236). The maintenance through holes (236) are connected to the internal cavity of the cylindrical guide wall (232). A sealing plug (25) is detachably installed at the maintenance through hole (236) by bolts. The sealing plug (25) is used to achieve internal cavity sealing and disassembly and maintenance.

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