A slant-plate nonlinear inertia vessel with adjustable inertia

Abstract

The present invention relates to a swash plate type nonlinear inertia chamber with adjustable inertia, comprising: a slide rail assembly, a mounting base, a support plate, a swash plate assembly, a connecting rod, a shaft seat, and a connecting ring; the mounting base is slidably mounted on the slide rail assembly, and the support plate is hingedly connected to the mounting base; the swash plate assembly comprises: a swash plate, a flywheel, a ball joint bearing, a fixing nut, an internal gear ring, a sun gear, and planetary gears; the swash plate assembly is mounted on a fixed shaft, and the swash plate forms an adjustable angle with the horizontal plane; the connecting rod comprises a crankshaft and an input shaft connected to each other; and the connecting ring comprises: a front bearing seat, a bidirectional thrust ball bearing, a locking nut, and a rear bearing seat. Compared with the prior art, the present invention has the advantages of adaptively changing inertia with input displacement, a simple and compact mechanical structure, adaptive nonlinear variation of inertia, and adjustable inertia coefficient.

Description

Technical Field

[0001] The present invention relates to the field of vibration control technology, in particular to a swash plate type nonlinear inertia container with adjustable inertia. Background Art

[0002] An inertia chamber is a mechanical component whose two ends can move relative to each other, and whose output is proportional to the relative acceleration between the two ends. It has the advantages of small mass, small size, and flexible installation under the same mass effect at both ends. The ratio of the output to the relative acceleration at both ends is called the "inertia coefficient" or "inertia". Through the proper design of the inertia chamber, an inertia chamber can generate an inertia far greater than its own physical mass.

[0003] Various types of inertia capacitors exist, but their performance is limited by their respective operating principles and structures. Hydraulic inertia capacitors face issues with connection stiffness and fluid leakage, while electromagnetic inertia capacitors suffer from circuit stability, which can affect their operational stability. Mechanical inertia capacitors have the advantage of requiring no oil supply or circuitry, resulting in stable operation. Mechanical inertia capacitors typically utilize a transmission mechanism to alter the form of motion, such as converting translational motion into rotational motion, thereby generating an inertia effect. Common types include rack and pinion and ball screw types. However, current mechanical inertia capacitors are mostly fixed inertia capacities, unable to adapt to the need to change the inertia coefficient on demand. Existing variable inertia capacitors also present difficulties in changing inertia and making it difficult to adjust inertia steplessly. Furthermore, they have complex mechanical structures, require high machining precision, and are expensive to manufacture.

[0004] Patent CN202420229474.2 provides a double-crank inertia container with variable inertia, including a support frame, a flywheel, a crank, a connecting rod, a transmission rod, a translation rod, and a translation rod support frame; there are multiple flywheels and two cranks; the flywheel is connected to the crank, the bottom of the crank is limited to rotate on the support frame, the tops of the two cranks are respectively connected to the two ends of the connecting rod, the connecting rod is connected to the transmission rod, the transmission rod is connected to the translation rod, the translation rod support frame is fixed to the support frame, and the translation rod is supported by the translation rod support frame. The translation rod support frame includes a linear bearing and a support plate, the support plate is fixed to the support frame, the linear bearing is fixed to the bottom of the support plate, the linear bearing is used to install the translation rod, and the translation rod slides under the constraint of the linear bearing. However, the structure is complex and occupies a large space; the adjustment of the inertia characteristics is inconvenient. Summary of the Invention

[0005] The present invention aims to overcome the drawbacks of the prior art, such as the difficulty in changing inertia, the difficulty in steplessly adjusting inertia, the complex mechanical structure, the high machining precision, and the high manufacturing cost. By providing a nonlinear inertia chamber with adjustable inertia, the present invention provides a swash plate type inertia chamber. Adjusting the swash plate's tilt angle, and thus the chamber's inertia coefficient, is adjustable by adjusting the push rod. The inertia chamber exhibits distinct nonlinear characteristics, allowing its inertia to adaptively change with input displacement. Furthermore, the inertia chamber features a simple and compact mechanical structure, a large inertia ratio, and more efficient absorption and dissipation of vibration energy, improving system stability and vibration resistance. The chamber achieves adaptive nonlinear variation of the inertia, and its inertia coefficient is adjustable.

[0006] The present invention provides a swash plate type nonlinear inertia container with adjustable inertia, comprising: a slide rail assembly, a mounting base, a support plate, a swash plate assembly, a connecting rod, an axle seat, and a connecting ring; one end of the connecting rod is connected to the swash plate assembly, and the other end of the connecting rod is inserted into the axle seat;

[0007] The slide rail assembly includes: a linear slide rail and a slider, the slider is installed in the linear slide rail; the mounting base includes: a bracket, an adjustment rod, and a hinge support, the bracket is installed on the slider; the support plate includes: a flange, a hinge, and a fixed shaft, the support plate is installed on the hinge support via a hinge;

[0008] The mounting base is slidably arranged on the slide rail assembly, and the support plate is hinged to the mounting base;

[0009] The swash plate assembly includes a swash plate, a flywheel, a ball joint bearing, a fixing nut, an inner ring gear, a sun gear, and planetary gears. The swash plate assembly is integrally mounted on a fixed shaft. The inner ring gear is fixedly connected to the support plate via a flange. The planetary gears are mounted on the swash plate, and the sun gear is fixedly connected to the flywheel. The swash plate assembly is mounted on the fixed shaft, and the swash plate forms an adjustable angle with the horizontal plane. The fixing nut is located at the center of the swash plate and is fixedly connected to the swash plate via threads for axial positioning.

[0010] One end of the connecting rod is connected to the ball joint bearing; the connecting rod includes a crankshaft and an input shaft connected to each other; a sliding bearing is installed in the shaft seat; the connecting ring includes: a front bearing seat, a bidirectional thrust ball bearing, a locking nut, and a rear bearing seat; the bidirectional thrust ball bearing is installed between the front bearing seat and the rear bearing seat to bear axial loads and play a supporting and rotating role; the locking nut is used to fix the connecting rod.

[0011] Furthermore, the adjusting push rod is connected to the bracket via a threaded connection, the adjusting push rod performs linear motion relative to the bracket, and a spherical push head is provided at the end of the adjusting push rod, which supports the support plate via the push head.

[0012] Furthermore, the swash plate assembly is connected to the fixed shaft via a rolling bearing, and the support plate does not rotate but only rotates around the hinge support to change the inclination angle of the swash plate.

[0013] Furthermore, the crankshaft is connected to the swash plate assembly via a ball joint bearing, and the crankshaft is simultaneously connected to the input shaft via a hinge. The crankshaft rotates in a vertical plane with the axis of the input shaft as the center.

[0014] Furthermore, the rotation center of the crankshaft in the plane facing the swash plate, that is, the input shaft and the geometric center of the swash plate do not coincide with each other, but are offset to the horizontal direction by a certain distance.

[0015] Furthermore, the crank arm length of the crankshaft is equal to the rotation radius of the ball joint bearing in the plane facing the swash plate, and the overall axial length of the crankshaft is greater than or equal to 3.5 times the rotation radius of the ball joint bearing in the plane facing the swash plate.

[0016] Furthermore, a planetary gear system is installed in the swash plate device, wherein the inner ring gear is fixedly connected to the support plate through a flange, the planetary gears are installed on the swash plate, and the sun gear is fixedly connected to the flywheel.

[0017] Furthermore, the input shaft is installed in a sliding bearing, and the input shaft performs both linear reciprocating motion and rotational motion relative to the shaft seat, and at the same time, the connecting ring installed at the end of the input shaft performs linear reciprocating motion.

[0018] Furthermore, the connecting ring is connected to the end of the input shaft through the front bearing seat, the bidirectional thrust ball bearing, the locking nut and the rear bearing seat.

[0019] Furthermore, the slider is installed in a linear slide rail and moves up and down along the linear slide rail. The slider is fixed by a locking screw.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] The present invention provides a swashplate-type nonlinear inertia chamber with adjustable inertia. This chamber utilizes a swashplate mechanism to convert between translational and rotational motion, thereby achieving an inertia effect. The input shaft serves as the driving element, the swashplate as the driven element, and a planetary gear system amplifies the inertia. Adjusting the push rod adjusts the swashplate's inclination angle, thereby adjusting the chamber's inertia coefficient. The chamber's inertia characteristics exhibit distinct nonlinearities, allowing its inertia to adaptively change with input displacement. The chamber boasts a simple and compact mechanical structure, a large inertia ratio, and more efficient absorption and dissipation of vibration energy, improving system stability and vibration resistance. The chamber achieves adaptive nonlinear variation of the inertia coefficient and an adjustable inertia coefficient. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1The schematic diagram of the structure of a slant-plate nonlinear inertia container with adjustable inertia is shown in FIG.

[0023] Figure 2 It is a side cross-sectional schematic diagram of a swash plate type nonlinear inertia container with adjustable inertia;

[0024] Figure 3 The figure is a schematic diagram of a slide rail assembly of a swash plate type nonlinear inertia container with adjustable inertia;

[0025] Figure 4 The figure is a schematic diagram of the support plate structure of a slant-plate nonlinear inertia container with adjustable inertia;

[0026] Figure 5 The figure is a schematic diagram of the structure of a swash plate assembly of a swash plate type nonlinear inertia container with adjustable inertia;

[0027] Figure 6 A schematic diagram of the planetary gear structure of a swash plate assembly of a nonlinear inertia container with adjustable inertia;

[0028] Figure 7 The figure is a side cross-sectional schematic diagram of a swash plate assembly of a swash plate type nonlinear inertia container with adjustable inertia;

[0029] Figure 8 This is a schematic diagram of the connecting ring structure of a swash plate type nonlinear inertia container with adjustable inertia;

[0030] Figure 9 The figure is a schematic diagram of a front view of a swash plate of a nonlinear inertia container with adjustable inertia;

[0031] Figure 10 The diagram is a schematic diagram of the mechanism of a swash plate type nonlinear inertia container with adjustable inertia.

[0032] Figure markings: 1-slide rail assembly; 101-linear slide rail; 102-slider; 103-locking screw; 2-mounting base; 201-bracket; 202-adjusting push rod; 203-hinge support; 3-support plate; 301-flange; 302-hinge; 303-fixed shaft; 4-swash plate assembly; 401-swash plate; 402-flywheel; 403-ball joint bearing; 404-fixing nut; 405-inner ring gear; 406-sun gear; 407-planet gear; 5-connecting rod; 501-crankshaft; 502-input shaft; 6-axle seat; 601-sliding bearing; 7-connecting ring; 701-front bearing seat; 702-double-direction thrust ball bearing; 703-locking nut; 704-rear bearing seat. DETAILED DESCRIPTION

[0033] The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. Component models, material names, connection structures, control methods, algorithms, and other features not explicitly described in this technical solution are considered common technical features disclosed in the prior art.

[0034] Example 1

[0035] This embodiment provides a swash plate type nonlinear inertia container with adjustable inertia, such as Figure 1-8 As shown, it includes: a slide rail assembly 1, a mounting base 2, a support plate 3, a swash plate assembly 4, a connecting rod 5, an axle seat 6, and a connecting ring 7; one end of the connecting rod 5 is connected to the swash plate assembly 4, and the other end of the connecting rod 5 is inserted into the axle seat 6;

[0036] The slide rail assembly 1 includes: a linear slide rail 101, a slider 102, and the slider 102 is installed in the linear slide rail 101; the mounting base 2 includes: a bracket 201, an adjustable push rod 202, and a hinge support 203, and the bracket 201 is installed on the slider 102; the support plate 3 includes: a flange 301, a hinge 302, and a fixed shaft 303, and the support plate 3 is installed on the hinge support 203 via the hinge 302;

[0037] The mounting base 2 is slidably disposed on the slide rail assembly 1, and the support plate 3 is hinged to the mounting base 2;

[0038] The swash plate assembly 4 includes: a swash plate 401, a flywheel 402, a ball joint bearing 403, a fixing nut 404, an inner ring gear 405, a sun gear 406, and planetary gears 407. The swash plate assembly 4 is integrally mounted on the fixed shaft 303. The inner ring gear 405 is fixedly connected to the support plate 3 via the flange 301. The planetary gears 407 are mounted on the swash plate 401. The sun gear 406 is fixedly connected to the flywheel 402. The swash plate assembly 4 is mounted on the fixed shaft 303. The swash plate 401 forms an adjustable bevel angle with the horizontal plane. The fixing nut 404 is located at the center of the swash plate 401 and is fixedly connected to the swash plate 401 via threads for axial positioning.

[0039] One end of the connecting rod 5 is connected to the ball joint bearing 403; the connecting rod 5 includes a crankshaft 501 and an input shaft 502 that are connected to each other; a sliding bearing 601 is installed in the shaft seat 6; the connecting ring 7 includes: a front bearing seat 701, a bidirectional thrust ball bearing 702, a locking nut 703, and a rear bearing seat 704; the bidirectional thrust ball bearing 702 is installed between the front bearing seat 701 and the rear bearing seat 704, and is used to bear axial loads and play a supporting and rotating role; the locking nut 703 is used to fix the connecting rod 5.

[0040] In a specific embodiment, the adjusting push rod 202 is connected to the bracket 201 through a threaded connection, and the adjusting push rod 202 makes a linear motion relative to the bracket 201. The adjusting push rod 202 has a spherical head at the end, which supports the support plate 3 through the head.

[0041] In a specific embodiment, the swash plate assembly 4 is connected to the fixed shaft 303 via a rolling bearing. The support plate 3 does not rotate but only rotates around the hinge support 203 to change the bevel angle of the swash plate 401 .

[0042] In a specific embodiment, the crankshaft 501 is connected to the swash plate assembly 4 via a ball joint bearing 403 , and the crankshaft 501 is also connected to the input shaft 502 via a hinge. The crankshaft 501 rotates in a vertical plane around the axis of the input shaft 502 .

[0043] In a specific embodiment, the rotation center of the crankshaft 501 in the plane facing the swash plate 401, that is, the input shaft 502 and the geometric center of the swash plate do not coincide with each other, but are offset horizontally by a distance to avoid the dead point of the device.

[0044] In a specific embodiment, the crank arm length of the crankshaft 501 is equal to the rotation radius of the ball joint bearing 403 in the plane facing the swash plate 401, and the overall axial length of the crankshaft 501 is greater than or equal to 3.5 times the rotation radius of the ball joint bearing 403 in the plane facing the swash plate 401. This ensures that the effect of the crankshaft rotation angle on the output is negligible.

[0045] In a specific embodiment, a planetary gear system is installed in the swash plate assembly 4, wherein the inner ring gear 405 is fixedly connected to the support plate 3 via the flange 301, the planetary gears 407 are mounted on the swash plate 401, and the sun gear 406 is fixedly connected to the flywheel 402. The inertia effect is enhanced by changing the transmission ratio.

[0046] In a specific embodiment, the input shaft 502 is installed in the sliding bearing 601. The input shaft 502 performs both linear reciprocating motion and rotational motion relative to the shaft seat 6. At the same time, the connecting ring 7 installed at the end of the input shaft 502 performs linear reciprocating motion.

[0047] In a specific embodiment, the connecting ring 7 is connected to the end of the input shaft 502 through a front bearing seat 701 , a bidirectional thrust ball bearing 702 , a locking nut 703 and a rear bearing seat 704 .

[0048] In a specific embodiment, the slider 102 is installed in the linear guide rail 101 and moves up and down along the linear guide rail 101. The slider 102 is fixed by a locking screw 103. This ensures that the position of the input shaft remains unchanged and the rotation center height of the swash plate is always aligned with the input shaft axis height.

[0049] The present invention proposes a swash plate type nonlinear inertia device with adjustable inertia. When the inertia size needs to be adjusted, the locking screw 103 is first unlocked to allow the slider 102 to move up and down along the linear guide rail 101. Then, the adjustment rod 202 is adjusted to change the bevel angle of the swash plate assembly 4. At the same time, because the axis of the input shaft 502 and the rotation center of the swash plate 401 remain relatively stationary at a height, the height of the bracket 2 will change with the slider 102.

[0050] The smaller the angle of the swash plate assembly 4, the smaller the inertia generated. The larger the angle of the swash plate assembly 4, the larger the inertia generated. After adjusting the inertia, tighten the locking screw 103 to keep the slider 102 fixed. At this point, the input end should be in a balanced state, and the inertia container can begin operation.

[0051] When input shaft 502 reciprocates, the crankshaft 501, connected to swash plate 401, generates a force component perpendicular to the swash plate's plane and a force component parallel to the swash plate's plane. The force component parallel to the swash plate's plane generates a rotational torque on swash plate 401, causing it to rotate and thus achieving an inertia effect. Due to the connecting rod's snap-back characteristics, the device's inertia exhibits significant nonlinear characteristics.

[0052] By connecting the swash plate 401 to the planetary gears 407 while keeping the ring gear 405 fixed, the sun gear 406 can achieve the maximum transmission ratio. The flywheel 402 is fixedly connected to the sun gear 406 to amplify its inertia, thereby obtaining a greater inertia-capacity effect.

[0053] The derivation process of the inertia capacity characteristic principle of the inertia container is as follows:

[0054] like Figure 9 、 Figure 10 As shown, it is assumed that the rotation radius of the ball joint bearing in the plane of the swash plate is r, the offset distance of the crankshaft rotation center (input shaft) is e, the displacement input by the input shaft end is x, the angle between the swash plate and the horizontal plane is an acute angle α, the angle the crankshaft rotates around its rotation center is θ, the angle the swash plate rotates from the equilibrium position is θ0, and the inertia vessel end output is F in , the equivalent moment of inertia of the device is I. Assume that the moment of inertia of the swash plate (planet carrier), planet gear, sun gear and flywheel are I C , I P , I S , I F The number of teeth of the ring gear, planet gear and sun gear are z respectively. R 、z P 、z S , then the transmission ratio of the planetary gear train is:

[0055]

[0056] According to the law of conservation of energy, the equivalent moment of inertia is equal to the sum of the moment of inertia of each component multiplied by the square of the ratio of the angular velocity of each component to the angular velocity of the equivalent component. Taking the swash plate (planet carrier) as the equivalent component, the equivalent moment of inertia I of the device is:

[0057]

[0058] As can be seen from formula (2), the planetary gear system effectively amplifies the moment of inertia of the device, so that the device can have a larger inertia coefficient.

[0059] The relationship between the input displacement x and the rotation angle θ is as follows:

[0060] x=rcosα·sinθ (3)

[0061] By taking the derivative of formula (3), we can get:

[0062]

[0063] in represents the input acceleration, then the angular acceleration of the swash plate is It can be expressed as:

[0064]

[0065] If we temporarily ignore the eccentricity and assume that e = 0, then θ0 = θ. According to the torque relationship of the swash plate, we can obtain:

[0066]

[0067] Substitute equation (5) into equation (6) and solve for F in :

[0068]

[0069] Let the limit stroke rcosα be X, then we have the following relationship:

[0070]

[0071] Substituting formula (8) into formula (7), we can get F in It can be expressed as:

[0072]

[0073] When e≠0, when the crank angle θ rotates to 90°, the angle of the swash plate The theoretical limit stroke of the device is:

[0074]

[0075] Substitute the angle θ0 and recalculate. Then equation (9) becomes:

[0076]

[0077] Formula (11) can be simplified as:

[0078] F in =Bx+Cx 2 (12)

[0079] Among them, B is the inertia coefficient, C is the damping coefficient, B and C are functions with input displacement x as the independent variable, and the expression of the inertia coefficient B is:

[0080]

[0081] The expression of the damping coefficient C is:

[0082]

[0083] Equation (12) shows that the output of the inertia chamber is related to the square of the input acceleration and input velocity, and is a combination of inertia and nonlinear damping forces, with inertia being the primary output. Equation (13) shows that the inertia chamber has a small inertia when the input displacement is small and a large inertia when the input displacement is large, exhibiting adaptive nonlinear inertia characteristics. Equation (14) shows that the damping force is in the opposite direction of the inertia force, increasing and then decreasing with increasing displacement. This characteristic reduces the output under small displacement conditions without affecting the inertia characteristics under large displacement conditions. When the swash plate angle α is adjusted, α changes. When α increases, the limit stroke X decreases, and the inertia coefficient A increases. Conversely, when α decreases, the inertia coefficient A decreases, indicating the adjustability of the inertia coefficient.

[0084] Components not described in detail in this embodiment are all existing components that can be purchased through public channels.

[0085] The above description of the embodiments is intended to facilitate understanding and use of the invention by those skilled in the art. It will be apparent that those skilled in the art can readily make various modifications to these embodiments and apply the general principles described herein to other embodiments without requiring inventive effort. Therefore, the present invention is not limited to the above-described embodiments. Improvements and modifications made by those skilled in the art based on the disclosure of the present invention, without departing from the scope of the present invention, should be within the scope of protection of the present invention.

Claims

1. A swash plate type nonlinear inertia container with adjustable inertia, characterized in that: include: A slide rail assembly (1), a mounting base (2), a support plate (3), a swash plate assembly (4), a connecting rod (5), an axle seat (6), and a connecting ring (7); one end of the connecting rod (5) is connected to the swash plate assembly (4), and the other end of the connecting rod (5) is inserted into the axle seat (6); The mounting base (2) is slidably arranged on the slide rail assembly (1), and the support plate (3) is hinged to the mounting base (2); The support plate (3) comprises: a flange (301), a hinge (302), and a fixed shaft (303); the support plate (3) is mounted on the hinge support (203) via the hinge (302); the swash plate assembly (4) is connected to the fixed shaft (303) via a rolling bearing; the support plate (3) rotates around the hinge support (203) to change the bevel angle of the swash plate (401); The swash plate assembly (4) comprises: a swash plate (401), a flywheel (402), a ball joint bearing (403), a fixing nut (404), an inner gear ring (405), a sun gear (406), and a planetary gear (407). The swash plate assembly (4) is integrally mounted on a fixed shaft (303). The inner gear ring (405) is fixedly connected to the support plate (3) via a flange (301). The planetary gear (407) is mounted on the swash plate (401). The sun gear (406) is fixedly connected to the flywheel (402). The swash plate assembly (4) is mounted on the fixed shaft (303). The swash plate (401) forms an oblique angle with a horizontal plane, and the oblique angle is adjustable. The fixing nut (404) is located at the center of the swash plate (401). The fixing nut (404) is fixedly connected to the swash plate (401) via a thread and is used for axial positioning. One end of the connecting rod (5) is connected to the ball joint bearing (403); the connecting rod (5) includes a crankshaft (501) and an input shaft (502) connected to each other; the connecting ring (7) includes: a front bearing seat (701), a bidirectional thrust ball bearing (702), a locking nut (703), and a rear bearing seat (704); the bidirectional thrust ball bearing (702) is installed between the front bearing seat (701) and the rear bearing seat (704); the locking nut (703) is used to fix the connecting rod (5); The connecting ring (7) is connected to the end of the input shaft (502) via a front bearing seat (701), a bidirectional thrust ball bearing (702), a locking nut (703), and a rear bearing seat (704).

2. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The mounting base (2) comprises: a bracket (201), an adjusting push rod (202), and a hinge support (203); the bracket (201) is mounted on the slider (102) of the slide rail assembly (1); the adjusting push rod (202) is connected to the bracket (201) by a thread, the adjusting push rod (202) performs linear motion relative to the bracket (201), and the adjusting push rod (202) has a spherical top at the end, which supports the support plate (3) through the top.

3. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The crankshaft (501) is connected to the swash plate assembly (4) via a ball joint bearing (403), and the crankshaft (501) is also connected to the input shaft (502) via a hinge. The crankshaft (501) rotates in a vertical plane with the axis of the input shaft (502) as the center.

4. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The rotation center of the crankshaft (501) in the plane facing the swash plate (401), that is, the input shaft (502) does not coincide with the geometric center of the swash plate, but is offset in the horizontal direction by a distance.

5. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The crank arm length of the crankshaft (501) is equal to the rotation radius of the ball joint bearing (403) in the plane facing the swash plate (401), and the overall axial length of the crankshaft (501) is greater than or equal to 3.5 times the rotation radius of the ball joint bearing (403) in the plane facing the swash plate (401).

6. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The input shaft (502) is installed in the sliding bearing (601), and the input shaft (502) performs both linear reciprocating motion and rotational motion relative to the shaft seat (6). At the same time, the connecting ring (7) installed at the end of the input shaft (502) performs linear reciprocating motion.

7. The swash plate type nonlinear inertia container with adjustable inertia according to claim 1, characterized in that: The slide rail assembly (1) comprises: a linear slide rail (101) and a slider (102), wherein the slider (102) is installed in the linear slide rail (101); the slider (102) is installed in the linear slide rail (101) and moves up and down along the linear slide rail (101), and the slider (102) is fixed by a locking screw (103).

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