A horizontal motion type inertial mass coefficient variable inertial capacitor

Abstract

The application discloses a horizontal motion type inertial mass coefficient variable inertial container and relates to the technical field of vibration isolation and damping, which solves the problems of weak amplification effect, complex structure, difficult sealing and difficult adjustment of the number of inertia amplification units of the existing inertial container. The application comprises an inertial container core and an inertial container support. The inertial container support comprises a trapezoidal screw, a support seat and a support rod. The support rod and the trapezoidal screw are arranged between the two support seats. The inertial container core is fixedly arranged on the support rod. The trapezoidal screw of the inertial container core is engaged with the trapezoidal screw through a nut. The axial movement of the trapezoidal screw drives the rotation of the nut, the adapter transition disc and the eccentric flywheel disc of the trapezoidal screw of the inertial container core. The application provides the conversion from translation to rotation through the large lead angle trapezoidal screw. The eccentric flywheel disc with different thicknesses provides the amplification effect of variable rotational inertia. The mechanical form is simple. The logical progressive relationship between the structures is close. The inertial mass coefficient can be adjusted and effectively amplified.

Description

Technical Field

[0001] This invention relates to the field of vibration reduction and isolation technology, specifically to a horizontally moving inertial container with a variable inertial mass coefficient. Background Technology

[0002] Low-frequency vibrations generated by various mechanical devices during underwater vehicle navigation severely affect its acoustic stealth performance. Currently, passive vibration isolators are commonly used and have achieved good control of mid-to-high frequency vibrations. However, there is a contradiction between low-frequency vibration stability and vibration isolation effect. Introducing inertial capacitive elements is one of the effective and feasible means to solve this problem.

[0003] An inertial capacitance is a component with two independent endpoints, similar to a spring and a damper. The ratio of the force applied to the two endpoints of the inertial capacitance to its relative acceleration is called the mass coefficient. Due to the amplification effect of the motion conversion device, the mass coefficient of the inertial capacitance is much greater than its own weight. Furthermore, the combination of the inertial capacitance, damper, and spring can effectively improve vibration reduction and isolation effects.

[0004] After the inertial container prototype is manufactured, its inertial mass coefficient is constant. Existing research, such as gear-rack type inertial containers, mainly achieves motion conversion through the meshing between gears and racks. Compared with other structures, this structure has a weaker amplification effect on the inertial mass coefficient, and the meshing friction coefficient between gears is relatively large. Ball screw type inertial containers have a complex mechanical structure and can only be driven in high-energy vibration reduction and isolation systems. In addition, the manufacturing of ball screws for specific needs is quite troublesome, limiting their practical application in some engineering projects. Although hydraulic inertial containers can achieve a superior inertial amplification effect, the fluid pipeline is difficult to seal, resulting in weak leakage prevention capabilities and high manufacturing precision requirements. Furthermore, the above structures lack standardized adjustable designs, making it difficult to increase or decrease the inertial amplification unit according to actual needs after manufacturing. The vibration isolation range of underwater vehicles and other equipment is limited, and when general inertial container elements are arranged vertically, the effective range is exceeded. Summary of the Invention

[0005] To address the aforementioned problems in existing technologies, such as the weak amplification effect of rack and pinion inertial containers, the complex mechanical structure of ball screw inertial containers, the difficulty in sealing the pipelines of hydraulic inertial containers and the inability to adjust the number of inertial amplification units according to actual needs, and the limited vibration isolation range of underwater vehicles and other equipment, this invention proposes a horizontally moving inertial container with a variable inertial mass coefficient. This invention provides the conversion from translation to rotation through a trapezoidal screw with a large lead angle, and provides a variable amplification effect for rotational inertia through eccentric flywheel disks of different thicknesses. The mechanical form is simple, the logical progression between structures is close, and it is easy to select standardized components and implement, enabling adjustable and effective amplification of the inertial mass coefficient.

[0006] This invention proposes a horizontally moving variable inertia mass container, specifically comprising an inertia container core and an inertia container support. The inertia container core is mounted on the inertia container support, which includes two support seats, two support rods, and a trapezoidal lead screw. Two support rods and the trapezoidal lead screw are positioned between the two support seats. The inertia container core is mounted on the two support rods and the trapezoidal lead screw. The trapezoidal lead screw passes through the center of the inertia container core and engages with its threads. The inertia container core includes an outer fixed sleeve, rolling bearings, a transition plate, a nut for the trapezoidal lead screw, several eccentric flywheel discs, two fully threaded studs, and several... The dry nut has an inner ring connected to a rolling bearing, and an outer ring fixedly connected to two support rods. The inner ring of the rolling bearing is connected to a transition plate. A trapezoidal screw nut is located at the center of the transition plate, and the trapezoidal screw nut engages with the trapezoidal screw thread. Several eccentric flywheels are located on the left side of the transition plate and the right side of the trapezoidal screw nut, and the transition plate, the trapezoidal screw nut, and the eccentric flywheels are fixed together by two fully threaded studs and several nuts. When the trapezoidal screw moves axially, it drives the transition plate and the eccentric flywheels to rotate through the trapezoidal screw nut.

[0007] Furthermore, the outer fixed sleeve has a shoulder on its inner ring, one side of the rolling bearing outer ring rests against the shoulder, and the other side is pressed against the outer ring by several screws provided on the outer fixed sleeve; the transition plate has a shoulder on its outer ring, one side of the rolling bearing inner ring rests against the shoulder, and the other side is pressed against the inner ring by several screws provided on the transition plate.

[0008] Furthermore, the outer fixing sleeve is symmetrically provided with two shaft holes, through which the support rod passes and is fixedly connected to the outer fixing sleeve by several bolts.

[0009] Furthermore, the support base is provided with a connector, which connects to an external mechanism.

[0010] Furthermore, the two support seats include support seat one and support seat two. Support seat one includes a through hole one and two through holes two. One end of the support rod passes through the through hole two and is fixedly connected to support seat one by several bolts. One end of the trapezoidal lead screw passes through the through hole one and is slidably connected to support seat one. Support seat two includes two through holes three and four. The other end of the support rod passes through the through hole three and is slidably connected to support seat two. The other end of the trapezoidal lead screw passes through the through hole four and is fixedly connected to support seat two by several bolts.

[0011] Furthermore, the support base one also includes a graphite copper sleeve, which is disposed in the through hole one and slidably connected to the trapezoidal lead screw.

[0012] Furthermore, the second support base also includes two linear bearings, which are disposed in the third through hole and slidably connected to the support rod.

[0013] Furthermore, the plurality of eccentric flywheels includes two small eccentric flywheels, two medium eccentric flywheels, and two large eccentric flywheels. The two small eccentric flywheels are respectively connected to the transition plate and the trapezoidal lead screw with nuts. One end of the medium eccentric flywheel is connected to the small eccentric flywheel, and the other end is connected to the large eccentric flywheel.

[0014] Furthermore, the thickness of the small eccentric flywheel is less than that of the medium eccentric flywheel, and the thickness of the medium eccentric flywheel is less than that of the large eccentric flywheel.

[0015] Furthermore, the lead angle of the trapezoidal lead screw is greater than 45 degrees.

[0016] The beneficial effects of the horizontal motion variable inertial container described in this invention are as follows:

[0017] (1) The inertial container with variable inertial mass coefficient of horizontal motion described in this invention overcomes the problems of weak amplification effect of gear rack type inertial container, complex mechanical structure of ball screw type inertial container, difficulty in sealing hydraulic inertial container pipeline, difficulty in adjusting the number of inertial amplification units according to actual needs, and limited vibration isolation range of underwater vehicles and other equipment. By setting a trapezoidal screw with a large lead angle, translational motion is converted into rotational motion. The overall structure is simple and reduces the impact of low frequency vibration generated by mechanical equipment on the acoustic stealth performance of underwater vehicles.

[0018] (2) The inertial container with variable inertial mass coefficient of horizontal motion described in this invention provides a variable amplification effect of rotational inertia through eccentric flywheel disks of different thicknesses, which can play a role in flexibly adjusting the rotational inertia enhancement. In actual engineering, the inertial mass coefficient of the system can be adjusted by adding only the eccentric flywheel disk as needed, without changing other structures. Attached Figure Description

[0019] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an improper limitation of the invention.

[0020] In the attached diagram:

[0021] Figure 1 This is a schematic diagram of the overall structure of a horizontally moving variable inertia mass coefficient according to the present invention;

[0022] Figure 2 This is a schematic diagram of the connection structure of the outer fixed sleeve, rolling bearing, transition plate, and trapezoidal screw nut of a horizontal motion variable inertia container according to the present invention.

[0023] Figure 3This is a schematic diagram of the assembly relationship between the transition disk and the trapezoidal lead screw nut of a horizontal motion variable inertia container according to the present invention.

[0024] Figure 4 This is a schematic diagram of the trapezoidal lead screw eccentric wheel rotation structure of a horizontal motion inertial container with a variable inertial mass coefficient, as described in this invention.

[0025] Figure 5 This is a schematic diagram of the inertia container support (excluding the trapezoidal lead screw) of an inertia container with a variable inertia mass coefficient for horizontal motion, as described in this invention.

[0026] Figure 6 This is a schematic diagram of the structure of a support base for a horizontally moving inertial container with a variable inertial mass coefficient, as described in this invention.

[0027] Figure 7 This is a schematic diagram of the structure of a support base two for a horizontally moving inertial container with a variable inertial mass coefficient, as described in this invention.

[0028] Wherein: 1-Outer fixing sleeve, 101-Shaft hole, 102-End face one, 103-Threaded hole one, 104-End face two, 105-End face three, 106-End face four, 107-End face five, 2-Rolling bearing, 3-Transfer plate, 301-Threaded hole two, 302-Through hole one, 303-Through hole two, 304-Internal groove, 305-Threaded hole three, 4-Hex socket head cap screw one, 5-Phillips head screw, 6-Hex socket head cap screw, 7-Nut for trapezoidal lead screw, 8-Small eccentric flywheel, 9- 10-Centered eccentric flywheel, 11-Large eccentric flywheel, 12-Fully threaded stud, 13-Nut, 14-Trapezoidal lead screw, 15-Support rod, 16-Support seat, 17-Support seat one, 18-Through hole three, 19-Through hole four, 10-Support seat two, 11-Support seat two, 12-Support seat two, 13-Through hole five, 14-Through hole six, 15-Support seat hole, 15-Linear bearing, 16-Graphite copper sleeve, 17-Connector, 1801-Connector hole, 19-Socket headstock set screw two, 20-Socket headstock set screw three. Detailed Implementation

[0029] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings:

[0030] Specific implementation method one: See Figures 1-7This embodiment is described in detail. The horizontally moving variable inertia mass container described in this embodiment specifically includes an inertia container core and an inertia container support. The inertia container core is mounted on the inertia container support, which includes two support seats 15, two support rods 14, and a trapezoidal lead screw 13. Two support rods 14 and a trapezoidal lead screw 13 are disposed between the two support seats 15. The inertia container core is mounted on the two support rods 14 and the trapezoidal lead screw 13. The trapezoidal lead screw 13 passes through the center of the inertia container core and engages with its thread. The inertia container core includes an outer fixed sleeve 1, a rolling bearing 2, a transition plate 3, a nut 7 for the trapezoidal lead screw, several eccentric flywheel discs, and two fully threaded... The stud 11 and several nuts 12 are provided. The inner ring of the outer fixing sleeve 1 is connected to the rolling bearing 2, and the outer ring is fixedly connected to two support rods 14. The inner ring of the rolling bearing 2 is connected to the transition plate 3. A through hole 2 303 is provided at the center of the transition plate 3. The trapezoidal screw nut 7 is installed on the transition plate 3 through the through hole 2 303. The transition plate 3 is also provided with four through holes 1 302. The trapezoidal screw nut 7 is also provided with four through holes corresponding to the four through holes 1 302. The left and right through holes cooperate with the through holes 1 302 to position the trapezoidal screw nut 7 and the transition plate 3 through the positioning pin.

[0031] The trapezoidal lead screw nut 7 has a threaded hole at its center, which engages with the threads of the trapezoidal lead screw 13. Several eccentric flywheel discs are located on the left side of the transition plate 3 and the right side of the trapezoidal lead screw nut 7. Two fully threaded studs 11 are installed on the transition plate 3 through two symmetrically arranged threaded holes. The two ends of the fully threaded studs 11 pass through through holes on the eccentric flywheel discs and the trapezoidal lead screw nut 7, and cooperate with several nuts 12 to fix the transition plate 3, the trapezoidal lead screw nut 7, and the eccentric flywheel discs together. When the trapezoidal lead screw 13 moves axially, it drives the transition plate 3 and the eccentric flywheel discs to rotate via the trapezoidal lead screw nut 7. The transition plate 3 is made of copper. The lead angle of the trapezoidal lead screw 13 is greater than 45 degrees. The transition plate 3 is made of copper. In order to ensure that the eccentric flywheels do not interfere with the outer fixed sleeve 1 when they rotate, the total thickness of the transition plate 3 needs to exceed the thickness of the outer fixed sleeve 1. Therefore, a certain protrusion thickness is provided on one side of the transition plate 3.

[0032] The outer fixing sleeve 1 has a shoulder on its inner ring. One side of the outer ring of the rolling bearing 2 rests on the shoulder, and the other side is pressed against the outer ring of the rolling bearing 2 by a number of cross-head screws 5 provided on the outer fixing sleeve 1. The outer ring of the transition plate 3 has a shoulder on its outer ring. One side of the inner ring of the rolling bearing 2 rests on the shoulder, and the other side is pressed against the inner ring of the rolling bearing 2 by a number of large-head hexagon socket screws 6 provided on the transition plate 3 and threaded holes 301. In order to ensure that the screw heads of the large-head hexagon socket screws 6 have sufficient installation space, an inner groove 304 is provided on the transition plate 3.

[0033] The outer fixing sleeve 1 is symmetrically provided with two outer fixing lugs, each with a shaft hole 101 and two or more threaded holes on the end face 102. The support rod 14 passes through the shaft hole 101 and is fixedly connected to the outer fixing sleeve 1 by engaging with the internal hexagon set screw 4 through the threaded hole on the end face 102.

[0034] The support base 15 is provided with a connector 18, which is connected to an external mechanism. In order to reduce the weight of the support base 15, a number of support base holes 1505 are provided on the support base 15.

[0035] The two support seats 15 include support seat one 151 and support seat two 152. Support seat one 151 includes through hole three 1501 and two through holes four 1502. One end of the support rod 14 passes through through hole four 1502 and is fixedly connected to support seat one 151 through several hexagonal set screws two 19. One end of the trapezoidal screw 13 passes through through hole three 1501 and is slidably connected to support seat one 151. Support seat two 152 includes two through holes five 1503 and through hole six 1504. The other end of the support rod 14 passes through through hole five 1503 and is slidably connected to support seat two 152. The other end of the trapezoidal screw 13 passes through through hole six 1504 and is fixedly connected to support seat two 152 through several hexagonal set screws three 20. During operation, the external mechanism drives the trapezoidal screw 13 to move axially through the support seat 2 152. The support seat 2 152 slides on the support rod 14. Through the cooperation between the trapezoidal screw 13 and the trapezoidal screw nut 7, the translational motion is converted into rotational motion.

[0036] The support base 151 also includes a graphite copper sleeve 17, which is disposed in the through hole 1501 and is slidably connected to the trapezoidal lead screw 13.

[0037] The second support base 152 also includes two linear bearings 16, which are disposed in the fifth through hole 1503 and are slidably connected to the support rod 14.

[0038] The plurality of eccentric flywheels includes two small eccentric flywheels 8, two medium eccentric flywheels 9, and two large eccentric flywheels 10. The two small eccentric flywheels 8 are connected to the transition plate 3 and the trapezoidal lead screw respectively using nuts 7. One end of the medium eccentric flywheel 9 is connected to the small eccentric flywheel 8, and the other end is connected to the large eccentric flywheel 10. The small, medium, and large eccentric flywheels are similar to the weights on a mechanical scale of varying weights, and can flexibly adjust the rotational inertia to enhance efficiency. In practical engineering, the system's inertia coefficient can be adjusted by simply adding eccentric flywheels without changing other structural elements. The aforementioned eccentric flywheels can be selected according to the required rotational inertia, with appropriate mass and diameter. The eccentricity, structure, and thickness of the eccentric mass blocks are designed using an optimized method to achieve the optimal axial rotational inertia. Preferably, a fan-shaped structure is selected, with the lower half of the fan serving as the eccentric mass and the small rectangular blocks in the upper half of the fan serving to connect and fix other structures.

[0039] The thickness of the small eccentric flywheel 8 is less than that of the medium eccentric flywheel 9, and the thickness of the medium eccentric flywheel 9 is less than that of the large eccentric flywheel 10. In practical engineering, eccentric flywheels of different thicknesses and diameters can be set according to actual conditions. Preferably, the thickness ratio of the large eccentric flywheel, the medium eccentric flywheel, and the small eccentric flywheel is 3:2:1. The length of the fully threaded stud 11 depends on the thickness of the large eccentric flywheel 10, the medium eccentric flywheel 9, the small eccentric flywheel 8, the transition plate 3, and the trapezoidal screw nut 7 on the left and right symmetrical sides. The fully threaded stud 11 should not be too long, otherwise it will affect the movable displacement of the two support seats 15 when they move to the middle position before the movement begins.

[0040] When the external mechanism vibrates, the trapezoidal lead screw 13 with a large lead angle translates, causing the eccentric flywheel to rotate. However, when the vibration displacement is small, the eccentric flywheel actually oscillates back and forth around its axis, and its reaction torque... ,in, For rotational inertia, Angular velocity, The swing angle, specifically the actual physical mass and inertia coefficient, can be achieved by changing the value of the excitation displacement, thereby increasing the size of the swing angle.

[0041] The support rod 14, support base 15, and outer fixing sleeve 1 should be as lightweight as possible, and their proportion of the total system mass should be as small as possible, so as not to affect the manifestation of the eccentric flywheel's inertial capacitance amplification characteristics. Preferably, high-strength, lightweight aerospace aluminum is selected, and the support rod 14 structure should be hard anodized to make the surface smooth and hard, thereby avoiding scratches on its surface caused by the lateral tilting force generated by the slight tilt of the support base 15.

[0042] The outer diameter of the eccentric flywheel determines the lateral distance between the two support rods 14, which in turn affects the lateral distance between the two through holes on the left and right sides of the support base 15. The length of the support rod 14 and the trapezoidal lead screw 13 with a large lead angle depends on factors such as the horizontal movement distance of the external mechanism, the total cumulative thickness caused by the number of eccentric flywheels equipped, and sufficient movable displacement.

[0043] In summary, the horizontal motion variable inertia mass container of this invention overcomes the problems of weak amplification effect of rack and pinion type inertia capacity, complex mechanical structure of ball screw type inertia capacity, difficulty in sealing hydraulic inertia capacity pipelines, difficulty in adjusting the number of inertia amplification units according to actual needs, and limited vibration isolation range of underwater vehicles and other equipment in the prior art. By setting a trapezoidal screw 13 with a large lead angle, translational motion is converted into rotational motion, the overall structure is simple, and the impact of low-frequency vibration generated by mechanical equipment on the acoustic stealth performance of underwater vehicles is reduced. The horizontal motion variable inertia mass container of this invention provides a variable amplification effect of rotational inertia through eccentric flywheel disks of different thicknesses, which can flexibly adjust the rotational inertia enhancement effect. In actual engineering, the inertia mass coefficient of the system can be adjusted by adding only the eccentric flywheel disk as needed, without changing other structures.

[0044] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above descriptions are merely specific embodiments of the present invention and are not intended to limit the invention. They can also be reasonable combinations of the features described in the above embodiments. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A horizontally moving inertial container with a variable inertial mass coefficient, characterized in that: The system includes an inertial container core and an inertial container support. The inertial container core is mounted on the inertial container support, which includes two support seats (15), two support rods (14), and a trapezoidal screw (13). Two support rods (14) and a trapezoidal screw (13) are arranged between the two support seats (15). The inertial container core is mounted on the two support rods (14) and the trapezoidal screw (13). The trapezoidal screw (13) passes through the center of the inertial container core and engages with its threads. The inertial container core includes an outer fixed sleeve (1), a rolling bearing (2), a transition plate (3), a nut (7) for the trapezoidal screw, several eccentric flywheel discs, two fully threaded studs (11), and several nuts (12). The inner ring of the outer fixed sleeve (1) is connected to the rolling bearing. The moving bearing (2) is connected, and the outer ring is fixedly connected to two support rods (14); the inner ring of the rolling bearing (2) is connected to the transition plate (3); a trapezoidal screw nut (7) is provided at the center of the transition plate (3), and the trapezoidal screw nut (7) is threadedly engaged with the trapezoidal screw (13); several eccentric flywheels are provided on the left side of the transition plate (3) and the right side of the trapezoidal screw nut (7), and the transition plate (3), the trapezoidal screw nut (7) and several eccentric flywheels are fixed together by two fully threaded studs (11) and several nuts (12); when the trapezoidal screw (13) moves axially, the transition plate (3) and several eccentric flywheels are driven to rotate by the trapezoidal screw nut (7); The outer fixed sleeve (1) has a shoulder on its inner ring, and the outer ring of the rolling bearing (2) rests against the shoulder on one side. The other side of the outer ring is pressed by several screws on the outer fixed sleeve (1). The outer ring of the transition plate (3) has a shoulder on its outer ring, and the inner ring of the rolling bearing (2) rests against the shoulder on one side. The other side of the inner ring is pressed by several screws on the transition plate (3). The plurality of eccentric flywheels include two small eccentric flywheels (8), two medium eccentric flywheels (9) and two large eccentric flywheels (10). The two small eccentric flywheels (8) are connected to the transition plate (3) and the trapezoidal lead screw respectively with nuts (7); one end of the medium eccentric flywheel (9) is connected to the small eccentric flywheels (8) and the other end is connected to the large eccentric flywheels (10). The thickness of the small eccentric flywheel (8) is less than that of the medium eccentric flywheel (9), and the thickness of the medium eccentric flywheel (9) is less than that of the large eccentric flywheel (10).

2. The inertial container with variable inertial mass coefficient for horizontal motion according to claim 1, characterized in that: The outer fixing sleeve (1) is symmetrically provided with two shaft holes (101), and the support rod (14) passes through the shaft holes (101) and is fixedly connected to the outer fixing sleeve (1) by several bolts.

3. The inertial container with variable inertial mass coefficient for horizontal motion according to claim 1, characterized in that: The support base (15) is provided with a connector (18), which is connected to an external mechanism.

4. The inertial container with variable inertial mass coefficient for horizontal motion according to any one of claims 1-3, characterized in that: The two support seats (15) include support seat one (151) and support seat two (152). Support seat one (151) includes through hole three (1501) and two through holes four (1502). One end of the support rod (14) passes through through hole four (1502) and is fixedly connected to support seat one (151) by several bolts. One end of the trapezoidal screw (13) passes through through hole three (1501) and is slidably connected to support seat one (151). Support seat two (152) includes two through holes five (1503) and through hole six (1504). The other end of the support rod (14) passes through through hole five (1503) and is slidably connected to support seat two (152). The other end of the trapezoidal screw (13) passes through through hole six (1504) and is fixedly connected to support seat two (152) by several bolts.

5. The inertial container with variable inertial mass coefficient for horizontal motion according to claim 4, characterized in that: The support base (151) also includes a graphite copper sleeve (17), which is disposed in the through hole (1501) and is slidably connected to the trapezoidal lead screw (13).

6. The inertial container with variable inertial mass coefficient for horizontal motion according to claim 4, characterized in that: The second support base (152) also includes two linear bearings (16), which are disposed in the fifth through hole (1503) and are slidably connected to the support rod (14).

7. The inertial container with variable inertial mass coefficient for horizontal motion according to claim 1, characterized in that: The lead angle of the trapezoidal lead screw (13) is greater than 45 degrees.

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