A high static and low dynamic vibration isolator for marine diesel engines

Abstract

The present invention discloses a high static and low dynamic vibration isolator for a ship diesel engine, which relates to the field of vibration isolators, and comprises a bottom shell, the bottom shell is mounted on a mounting block at the bottom of a ship main engine, a bearing plate is slidably mounted on the inner top side of the bottom shell, the top of the bearing plate is fixedly connected with symmetrically arranged guide rods, the bearing plate is slidably mounted on a fixed block through the guide rods, the fixed blocks are provided with two, the mounting block is fixed between the two fixed blocks, a screw is inserted on the fixed block, and a symmetrically arranged guide groove is provided on the bottom wall of the bottom shell. The present invention adopts multiple groups of springs to improve the vibration isolation efficiency, and can effectively prevent the vibration isolator from being too statically deformed while bearing a higher load, and has a good vibration isolation effect, so that the resonance frequency of the ship diesel engine vibration isolator is reduced, and at the same time, the stability of the ship main engine can be ensured, and the low-frequency vibration isolation effect can be effectively improved.

Description

Technical Field

[0001] The invention relates to the field of vibration isolators, and in particular to a high-static and low-dynamic vibration isolator for a ship diesel engine. Background Art

[0002] When the ship diesel engine is running under certain working conditions, the piston reciprocates, the crankshaft rotates, the small end of the connecting rod reciprocates with the piston, the large end of the connecting rod rotates with the crank pin, and the rod body swings around the pin or crosshead pin. The complex movement of the crank-connecting rod mechanism will inevitably produce periodically changing unbalanced forces and moments. These unbalanced forces and moments are easily transmitted to the hull to cause vibration of other equipment, and at the same time act on the hull to generate vibration noise, which is easy to fatigue damage, and further generate underwater noise, affecting the acoustic stealth of the ship. Therefore, it is necessary to install a vibration isolator at the bottom of the ship main engine to isolate the excitation force generated by the vibration of the ship main engine. The excitation force of the ship diesel engine at the normal operating speed is a low-frequency disturbance force. Therefore, in order to isolate low-frequency vibrations, the stiffness of the existing vibration isolator is often made relatively soft. Although it meets the vibration isolation requirements, it produces a large static deformation, which makes the diesel engine shake more, which is not conducive to the normal operation of the diesel engine; therefore, designing a high static and low dynamic vibration isolator can effectively solve the above problems. Since the high static and low dynamic vibration isolator is a nonlinear vibration isolator, in addition, when the weight of the diesel engine exceeds the design load of the high static and low dynamic vibration isolator, the vibration isolator will deviate from its static equilibrium position and the vibration isolation effect will deteriorate. Therefore, the high static and low dynamic vibration isolator for a ship diesel engine of the present invention can effectively solve the contradiction between the above-mentioned large static deformation and low-frequency vibration isolation, as well as the problem of poor vibration isolation effect when the diesel engine is too heavy. Summary of the invention

[0003] The object of the present invention is to provide a high static and low dynamic vibration isolator for a marine diesel engine to solve the problems raised in the above-mentioned background technology.

[0004] To achieve the above-mentioned purpose, the present invention provides the following technical solutions: a high-static and low-dynamic vibration isolator for a marine diesel engine, comprising a bottom shell, the bottom shell is mounted on a mounting block at the bottom of a marine main engine, a bearing plate is slidably mounted on the inner top side of the bottom shell, a symmetrically arranged guide rod is fixedly connected to the top of the bearing plate, the bearing plate is slidably mounted on the fixed block through the guide rod, the fixed block is provided with two, the mounting block is fixed between the two fixed blocks, a screw is inserted on the fixed block, a symmetrically arranged guide groove is provided on the bottom wall of the bottom shell, a first reinforcing rod and a limiting rod are fixedly mounted on the inner top side and the bottom side of the guide groove respectively, a sliding seat is slidably mounted on the inner side of the guide groove, a first auxiliary spring is sleeved on the first reinforcing rod, an active cavity is arranged in the raised portion of the bottom wall of the bottom shell, a central shaft is fixedly connected to the middle of the bottom of the bearing plate, the bottom end of the central shaft passes through the top wall of the active cavity and is fixedly connected to a baffle, and a main spring is sleeved on the outer surface of the central shaft;

[0005] A second reinforcing rod is fixedly installed inside the movable cavity, the baffle is slidably connected to the second reinforcing rod, a limiting groove is provided on one side of the fixed block close to the end face of the guide rod, and the right end of the guide rod is fixedly connected to the limiting plate.

[0006] Optionally, the mounting block is T-shaped;

[0007] The fixing block is L-shaped.

[0008] Optionally, the screw rod passes through the interior of the mounting block, and nuts are threadedly mounted on both ends of the screw rod.

[0009] Optionally, the first reinforcing rod and the limiting rod both slide through the interior of the sliding seat;

[0010] The number of the second reinforcing rods is two.

[0011] Optionally, a connecting rod is hinged between the top of the sliding seat and the bottom of the bearing plate.

[0012] Optionally, a second auxiliary spring is sleeved on the outer side of the second reinforcing rod.

[0013] Optionally, the limiting plate is located in the limiting groove, and the surface of the limiting plate is in contact with the limiting groove.

[0014] Technical effects and advantages of the present invention:

[0015] 1. The present invention adopts multiple groups of springs to improve the vibration isolation efficiency by utilizing the characteristics of high static and low dynamic stiffness. It can effectively prevent the vibration isolator from being excessively deformed statically while bearing a higher load, and reduce noise, with good vibration isolation effect.

[0016] 2. The present invention can reduce the resonance frequency of the ship main engine vibration isolator, and at the same time can reduce the static displacement of the ship main engine when the diesel engine weight exceeds the rated load, ensure the stability of the vibration isolator, and effectively improve the low-frequency vibration isolation effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 It is a schematic diagram of the installation structure of the vibration isolator of the present invention.

[0018] Figure 2 It is a schematic cross-sectional view of the bottom shell of the present invention.

[0019] Figure 3 For the present invention Figure 2 A schematic diagram of the enlarged structure in the middle.

[0020] Figure 4 For the present invention Figure 2 Enlarged schematic diagram of the structure at point B in the middle.

[0021] In the figure: bottom shell 1, ship main engine 2, mounting block 3, bearing plate 4, guide rod 5, fixing block 6, screw 7, nut 8, guide groove 9, first reinforcing rod 10, limiting rod 11, slide seat 12, connecting rod 13, first auxiliary spring 14, movable cavity 15, central axis 16, baffle 17, main spring 18, second reinforcing rod 19, second auxiliary spring 20, limiting groove 21, limiting plate 22. DETAILED DESCRIPTION

[0022] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0023] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0024] In the present invention, unless otherwise clearly specified and limited, the terms "set", "install", "connect", "connect", "fix" and the like should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection; it can be a mechanical connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0025] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0026] The present invention provides Figure 1-4 The high static and low dynamic vibration isolator of a marine diesel engine shown in FIG. comprises a bottom shell 1, Figure 1 and Figure 2As shown, the bottom shell 1 is installed on the mounting block 3 at the bottom of the ship main engine 2, and a bearing plate 4 is slidably installed on the inner top side of the bottom shell 1. A symmetrically arranged guide rod 5 is fixedly connected to the top of the bearing plate 4. The bearing plate 4 is slidably installed on the fixed block 6 through the guide rod 5. Two fixed blocks 6 are provided. The mounting block 3 is fixed between the two fixed blocks 6. The mounting block 3 is T-shaped, and the fixed block 6 is L-shaped. A screw 7 is inserted into the fixed block 6, and the screw 7 passes through the interior of the mounting block 3. Nuts 8 are threadedly installed at both ends of the screw 7. Through such an arrangement, the vibration isolator can be installed on the mounting block 3 of the ship main engine 2, and the fixing effect is good. The bottom wall of the bottom shell 1 is provided with symmetrically arranged guide grooves 9, and the inner top and bottom sides of the guide grooves 9 are respectively fixedly installed with a first reinforcing rod 10 and The limiting rod 11 and the guide groove 9 are slidably installed with a slide seat 12. The first reinforcing rod 10 and the limiting rod 11 are both slidably penetrated into the interior of the slide seat 12. A connecting rod 13 is hinged between the top of the slide seat 12 and the bottom of the bearing plate 4. A first auxiliary spring 14 is sleeved on the first reinforcing rod 10. When the slide seat 12 slides along the first reinforcing rod 10 close to the side wall of the bottom shell 1, the slide seat 12 compresses the first auxiliary spring 14. An active cavity 15 is arranged in the raised portion of the bottom wall of the bottom shell 1. A central axis 16 is fixedly connected to the middle of the bottom of the bearing plate 4. The bottom end of the central axis 16 penetrates the top wall of the active cavity 15 and is fixedly connected to a baffle 17. A main spring 18 is sleeved on the outer surface of the central axis 16. The bearing plate 4 can drive the central axis 16 to move downward and compress the main spring 18.

[0027] Depend on Figure 3 and Figure 4 As shown, a second reinforcing rod 19 is fixedly installed inside the movable cavity 15, and two second reinforcing rods 19 are provided. The baffle plate 17 is slidably connected to the second reinforcing rod 19, and a second auxiliary spring 20 is sleeved on the outer side of the second reinforcing rod 19. The baffle plate 17 can slide downward along the second reinforcing rod 19 to compress the second auxiliary spring 20. A limiting groove 21 is provided on one side of the fixed block 6 close to the end face of the guide rod 5, and a limiting plate 22 is fixedly connected to the right end of the guide rod 5. The limiting plate 22 is located in the limiting groove 21, and the surface of the limiting plate 22 fits with the limiting groove 21.

[0028] Working principle:

[0029] During use, when the load is less than the rated load, the second auxiliary spring 20 does not work, the main spring 18 in the center shaft 16 is deformed, and bears the gravity load of the ship diesel engine. At the same time, the first auxiliary spring 14 is compressed by the slide seat 12, and forms a high static and low dynamic vibration isolator with the first auxiliary spring 14, which plays a role in isolating the low-frequency vibration of the diesel engine. When the load exceeds the rated load, the bearing plate 4 drives the center shaft 16 to move downward, thereby further compressing the main spring 18, and the center shaft 16 moves further downward. At this time, the second auxiliary spring 20 is compressed by the baffle 17, and the second auxiliary spring 20 begins to work. In this way, the main spring 18 and the second auxiliary spring 20 jointly bear the gravity load of the ship diesel engine, the static stiffness is enhanced, the stiffness ratio of the high static and low dynamic vibration isolator is reduced, and the load-bearing capacity is improved, ensuring that the static deformation is not too large, and the system continues to maintain static balance near the design position point. At the same time, the first auxiliary spring 14 is compressed by the slide seat 12, and together with the main spring 18 and the second auxiliary spring 20, forms a high-static and low-dynamic vibration isolator, which ensures the bearing capacity of the vibration isolator, and the system has a good vibration isolation effect.

[0030] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, it is still possible for those skilled in the art to modify the technical solutions described in the aforementioned embodiments or to make equivalent substitutions for some of the technical features therein. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention shall be included in the protection scope of the present invention.

Claims

1. A high static and low dynamic vibration isolator for a marine diesel engine, comprising a bottom shell (1), the bottom shell (1) being mounted on a mounting block (3) at the bottom of a marine main engine (2), a bearing plate (4) being slidably mounted on the inner top side of the bottom shell (1), a symmetrically arranged guide rod (5) being fixedly connected to the top of the bearing plate (4), the bearing plate (4) being slidably mounted on a fixed block (6) via the guide rod (5), the fixed block (6) being provided with two, the mounting block (3) being fixed between the two fixed blocks (6), the fixed block (6) being plugged with a screw (7), the bottom wall of the bottom shell (1) being provided with symmetrically arranged guide rods (5) and the like. A guide groove (9), a first reinforcing rod (10) and a limiting rod (11) are fixedly installed on the top and bottom sides of the guide groove (9), a sliding seat (12) is slidably installed inside the guide groove (9), a first auxiliary spring (14) is sleeved on the first reinforcing rod (10), a movable cavity (15) is arranged in the raised portion of the bottom wall of the bottom shell (1), a central axis (16) is fixedly connected to the middle of the bottom of the bearing plate (4), the bottom end of the central axis (16) passes through the top wall of the movable cavity (15) and is fixedly connected to a baffle (17), and a main spring (18) is sleeved on the outer surface of the central axis (16); A second reinforcing rod (19) is fixedly installed inside the movable chamber (15), the baffle plate (17) is slidably connected to the second reinforcing rod (19), a limiting groove (21) is provided on one side of the fixed block (6) close to the end surface of the guide rod (5), and the right end of the guide rod (5) is fixedly connected to a limiting plate (22); A second auxiliary spring (20) is sleeved on the outer side of the second reinforcing rod (19).

2. The high static and low dynamic vibration isolator for marine diesel engines according to claim 1 is characterized in that: The mounting block (3) is T-shaped; The fixing block (6) is L-shaped.

3. The high static and low dynamic vibration isolator for marine diesel engines according to claim 1 is characterized in that: The screw rod (7) passes through the interior of the mounting block (3), and nuts (8) are threadedly mounted on both ends of the screw rod (7).

4. The high static and low dynamic vibration isolator for marine diesel engines according to claim 1 is characterized in that: The first reinforcing rod (10) and the limiting rod (11) both slide through the interior of the sliding seat (12); The number of the second reinforcing rods (19) is two.

5. The high static and low dynamic vibration isolator for marine diesel engines according to claim 1 is characterized in that: A connecting rod (13) is hinged between the top of the sliding seat (12) and the bottom of the bearing plate (4).

6. The high static and low dynamic vibration isolator for marine diesel engines according to claim 1, characterized in that: The limiting plate (22) is located in the limiting groove (21), and the surface of the limiting plate (22) is in contact with the limiting groove (21).

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