High-damping-ratio steel spring viscous vibration isolator

Abstract

The utility model discloses a high-damping-ratio steel spring viscous vibration isolator, which is characterized in that a piston plate is added on the basis of a conventional damping fluid vibration isolator, a damping hole is arranged on the piston plate, and a gap is reserved between the piston plate and the inner wall of a lower cylinder. Damping liquid flows from the lower oil chamber to the upper oil chamber from the damping hole of the piston plate and the gap between the piston plate and the lower cylinder, when the vibration isolator vibrates, the damping liquid circularly flows in the two oil chambers, and the hole-gap mixed type damping hole vibration isolator is formed, that is, the piston plate greatly increases the flowing degree of the damping liquid; the energy dissipation capacity of the damping liquid is greatly improved, the damping ratio is correspondingly increased, and resonance is effectively avoided so that the vertical dynamic deformation of the floating slab can be reduced.

Description

Technical Field

[0001] The utility model belongs to the technical field of rail transit vibration damping devices, and specifically relates to a high-damping steel spring viscous isolator. Background Technique

[0002] Steel spring floating slab track beds are widely used in the field of rail transit vibration damping due to their excellent vibration damping effect. As an important vibration damping component among them, the performance of steel spring isolators plays a decisive role in the effect of steel spring floating slab track beds.

[0003] The process of train running presents the characteristic of variable frequency, which leads to the inevitable coincidence of the resonance frequency band of the vibration isolation system with the vibration frequency caused by the train, thus triggering a resonance phenomenon, resulting in an excessive vertical deformation amplitude of the steel spring floating slab track bed, which is not conducive to the safe running of the train. Figure 7 It can be seen that as the damping ratio of the vibration isolation and damping component increases, the acceleration in the resonance frequency band decreases significantly. Therefore, the vibration isolation system must have a certain damping ratio to reduce the deformation of the floating slab under resonance.

[0004] The damping performance of the steel spring isolator is reflected in that when the upper structure is subjected to a load, the steel spring compresses and vibrates, and the spring transfers the disturbance it receives to the damping liquid, while the damping liquid converts kinetic energy into heat energy and dissipates it. The vibration isolation and damping device with a higher damping ratio has a higher energy dissipation capacity. Therefore, the damping ratio of the isolator can be appropriately increased to reduce the vertical deformation of the floating slab track bed, and at the same time, dissipate the vibration energy input by the vehicle faster and make the floating slab return to the equilibrium state.

[0005] The current steel spring floating slab track specifications often have clear requirements for the damping ratio of steel spring isolators. The Ministry of Housing and Urban-Rural Development specification "Technical Specification for Floating Slab Track" (CJJ / T 191-2012) requires that the damping ratio of steel spring isolators is not less than 5%; the Shanghai local standard "Construction Quality Acceptance Standard for Urban Rail Transit Steel Spring Floating Slab Track" (DG / TJ 08-2416-2023) requires that the damping ratio of steel spring isolators is 5% - 10%; the Beijing local standard "Technical Standard for Urban Rail Transit Spring Floating Slab Track" (QGD-031-2020) requires this value to be 6% - 12%. The energy dissipation principle of the steel spring isolator is to increase the dissipation of vibration energy by the isolator by increasing the disturbance of the damping liquid. The damping ratio of existing common steel spring isolators is about 6% - 8%. Although it can meet the requirements of existing specifications, the damping ratio is still on the small side.

[0006] Based on this, the inventor of the present invention has further deeply studied the structural form of the isolator, hoping to design a high-damping steel spring isolator that can solve the above problems. Content of the Utility Model

[0007] In order to overcome the above problems, the inventor has conducted intensive research and designed a high-damping-ratio steel spring viscous isolator. On the basis of a conventional damping fluid isolator, a piston plate is added to this isolator, damping holes are opened on the piston plate, and a gap is left between the piston plate and the inner wall of the lower cylinder. When the piston plate moves, the damping fluid flows from the lower oil chamber to the upper oil chamber through the damping holes in the piston plate and the gap between the piston plate and the lower cylinder. When the isolator vibrates, the damping fluid circulates in the two oil chambers, forming a pore-gap hybrid damping hole isolator. That is, the piston plate greatly increases the flow degree of the damping fluid, the energy dissipation capacity of the damping fluid is greatly improved, the damping ratio is correspondingly increased, resonance is effectively avoided, and the vertical dynamic deformation of the floating slab is reduced, thus completing the present utility model.

[0008] Specifically, the purpose of the present utility model is to provide a high-damping-ratio steel spring viscous isolator, which includes an upper cover plate 1 and a lower cylinder 2, and a sealing strip 3 for sealing connection is arranged between the upper cover plate 1 and the lower cylinder 2;

[0009] A steel spring 4, a piston plate 5 and a damping fluid 6 are arranged in the lower cylinder 2, and both the steel spring 4 and the piston plate 5 are immersed in the damping fluid 6;

[0010] The piston plate 5 is horizontally arranged in the lower cylinder 2, and the piston plate 5 divides the lower cylinder 2 into an upper oil chamber and a lower oil chamber;

[0011] A through damping hole 51 is opened on the piston plate 5. The diameter of the piston plate 5 is slightly smaller than the inner diameter of the lower cylinder 2, and a gap is left between the piston plate 5 and the inner wall of the lower cylinder 2. The damping fluid 6 can circulate between the upper oil chamber and the lower oil chamber through the damping hole and the gap.

[0012] Among them, the isolator is installed in the floating slab track bed. When the floating slab track bed is in a static state, the liquid level height of the damping fluid 6 in the lower cylinder 2 is above the piston plate 5 and below the sealing strip 3.

[0013] Among them, the steel spring 4 is vertically arranged, its bottom abuts against the bottom of the lower cylinder 2, and its top abuts against the piston plate 5.

[0014] Among them, an annular support ring 11 extending downward is arranged on the upper cover plate 1, and the bottom of the support ring 11 abuts against the piston plate 5, so as to transmit the vertical force received in the upper cover plate 1 to the piston plate 5 and the steel spring 4 below it.

[0015] Among them, a threaded hole is opened in the middle of the upper cover plate 1,

[0016] An inwardly protruding limit boss 21 is arranged at the inner bottom of the lower cylinder 2; a bottom through hole for a bolt to pass through is opened on the limit boss 21,

[0017] A central hole 52 is formed in the middle of the piston plate 5.

[0018] The vibration isolator further includes a bolt 7 which sequentially passes through the bottom through-hole on the limit boss 21, the central hole 52 of the piston plate 5 and the threaded hole on the upper cover plate 1 from bottom to top, and is screwed and fixed with a nut 8, thereby consolidating the upper cover plate 1 and the lower cylinder 2 into one body.

[0019] Among them, the damping holes 51 on the piston plate 5 surround and are evenly distributed around the central hole 52.

[0020] The inner diameter of the lower cylinder 2 is 176 mm.

[0021] Among them, the radius dimension of the piston plate 5 is 172 - 168 mm.

[0022] The thickness of the piston plate 5 is 10 - 16 mm.

[0023] The total area of the damping holes 51 on the piston plate 5 is 1000 - 1600 mm 2 .

[0024] The beneficial effects of the present utility model include:

[0025] (1) The high-damping-ratio steel spring viscous vibration isolator provided by the present utility model proposes a structure in which the internal space of the vibration isolator is divided into two oil chambers by a piston plate, increasing the energy dissipation capacity of the steel spring vibration isolator, thereby improving the damping ratio of the steel spring vibration isolator.

[0026] (2) The high-damping-ratio steel spring viscous vibration isolator provided by the present utility model can adjust the damping ratio of the vibration isolator through the number and aperture of the damping holes on the piston plate, and further can adjust the damping ratio by only replacing the piston plate. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] Figure 1 Shows an exploded view of the high-damping-ratio steel spring viscous vibration isolator;

[0028] Figure 2 Shows a cross-sectional view of the high-damping-ratio steel spring viscous vibration isolator;

[0029] Figure 3 Shows a schematic structural diagram of the piston plate of the high-damping-ratio steel spring viscous vibration isolator;

[0030] Figure 4 Shows a schematic structural diagram of the upper cover plate of the high-damping-ratio steel spring viscous vibration isolator;

[0031] Figure 5 Shows the motion state of the vibration isolator when the load increases;

[0032] Figure 6Shows the motion state of the vibration isolator when the load decreases;

[0033] Figure 7 Shows the response schematic diagram of different damping ratio vibration reduction and isolation components in the resonance frequency band in the background technology.

[0034] Reference numerals

[0035] 1 - Upper cover plate

[0036] 11 - Support ring

[0037] 2 - Lower cylinder

[0038] 21 - Limit boss

[0039] 3 - Sealing strip

[0040] 4 - Steel spring

[0041] 5 - Piston plate

[0042] 51 - Damping hole

[0043] 52 - Central hole

[0044] 6 - Damping liquid

[0045] 7 - Bolt

[0046] 8 - Nut Detailed implementation manners

[0047] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments. Through these descriptions, the features and advantages of the present invention will become clearer and more distinct.

[0048] The special term "exemplary" here means "serving as an example, embodiment or illustration". Any embodiment described as "exemplary" here does not have to be construed as superior or better than other embodiments. Although various aspects of the embodiments are shown in the drawings, the drawings do not have to be drawn to scale unless otherwise specified.

[0049] The present invention provides a high damping ratio steel spring viscous vibration isolator, as shown in Figure 1 , Figure 2 . The vibration isolator includes an upper cover plate 1 and a lower cylinder 2, and a sealing strip 3 for sealing connection is arranged between the upper cover plate 1 and the lower cylinder 2; the sealing strip is preferably an annular rubber sealing strip, which can deform to a certain extent, so as to allow the distance between the upper cover plate 1 and the lower cylinder 2 to change within a certain range, that is, when the train passes by, the distance between the upper cover plate 1 and the lower cylinder 2 decreases, and after the train leaves, the distance between the upper cover plate 1 and the lower cylinder 2 returns to its original position.

[0050] A steel spring 4, a piston plate 5 and damping liquid 6 are arranged in the lower cylinder 2, and both the steel spring 4 and the piston plate 5 are immersed in the damping liquid 6;

[0051] The piston plate 5 is horizontally arranged in the lower cylinder 2. The piston plate 5 divides the lower cylinder 2 into an upper oil chamber and a lower oil chamber. That is, the space of the lower cylinder 2 below the piston plate 5 is the lower oil chamber, and the space above the piston plate 5 is the upper oil chamber;

[0052] A through damping hole 51 is formed in the piston plate 5. The diameter of the piston plate 5 is slightly smaller than the inner diameter of the lower cylinder 2. A gap is left between the piston plate 5 and the inner wall of the lower cylinder 2. The damping liquid 6 can circulate between the upper oil chamber and the lower oil chamber through the damping hole and the gap.

[0053] The vibration isolator is installed in the floating slab track bed. When the floating slab track bed is in a static state, the liquid level height of the damping liquid 6 in the lower cylinder 2 is above the piston plate 5 and below the sealing strip 3.

[0054] The steel spring 4 is vertically arranged. Its bottom abuts against the bottom of the lower cylinder 2, and its top abuts against the piston plate 5.

[0055] An annular support ring 11 extending downward is arranged on the upper cover plate 1. The bottom of the support ring 11 abuts against the piston plate 5, so that the vertical force received in the upper cover plate 1 can be transmitted to the piston plate 5 and the steel spring 4 below it.

[0056] In a preferred embodiment, a threaded hole is formed in the middle of the upper cover plate 1.

[0057] A limiting boss 21 protruding inward is arranged at the inner bottom of the lower cylinder 2; a bottom through hole for the bolt to pass through is formed in the limiting boss 21.

[0058] A central hole 52 is formed in the middle of the piston plate 5.

[0059] The vibration isolator further includes a bolt 7. The bolt 7 sequentially passes through the bottom through hole on the limiting boss 21, the central hole 52 of the piston plate 5 and the threaded hole on the upper cover plate 1 from bottom to top, and is screwed and fixed with a nut 8, so as to fix the upper cover plate 1 and the lower cylinder 2 into one body.

[0060] Preferably, the damping holes 51 on the piston plate 5 are arranged around and evenly distributed around the central hole 52.

[0061] The damping liquid 6 described in this application is a viscous material. The viscous material is a material with viscosity and elasticity and can also flow. When subjected to an external force, internal shear deformation and energy loss will occur; this characteristic enables the viscous material to effectively absorb and dissipate the energy generated by the structural vibration, thereby reducing the vibration amplitude and acceleration of the structure.

[0062] During the operation of a traditional vibration isolator with damping fluid: when the structure is subjected to an external force, the damping fluid will undergo internal shear deformation, thereby consuming energy. These energy losses will cause the vibration amplitude and acceleration of the structure to decrease.

[0063] When the vehicle drives onto the steel spring floating slab track bed in this application, the pressure transmission route is the upper cover plate - the piston plate - the steel spring. The steel spring compresses and vibrates under the action of the load, as Figure 5 shown. At this time, the piston plate has two motion states: downward movement and vibration. When the piston plate moves, the damping fluid flows from the lower oil chamber to the upper oil chamber through the damping holes of the piston plate and the gap between the piston plate and the lower cylinder. When vibrating, the damping fluid circulates between the two oil chambers;

[0064] When the displacement of the steel spring floating slab track bed tends to be stable under the action of the train load, the steel spring and the piston plate only maintain the vibration state, and the damping fluid circulates between the two oil chambers;

[0065] When the vehicle drives away from the steel spring floating slab track bed, the steel spring stretches and vibrates under the action of the load, as Figure 6 shown. At this time, the piston plate has two motion states: upward movement and vibration. When the piston plate moves, the damping fluid flows from the upper oil chamber to the lower oil chamber through the damping holes of the piston plate and the gap between the piston plate and the lower cylinder. When vibrating, the damping fluid circulates between the two oil chambers.

[0066] Therefore, it can be seen that the piston plate in this application greatly increases the flow degree of the damping fluid. Therefore, the energy consumption capacity of the damping fluid is greatly improved, and the damping ratio of the vibration isolator also increases accordingly.

[0067] Furthermore, the inventor of this application has found that the damping force is positively correlated with the area and movement speed of the piston plate, and negatively correlated with the gap width and the opening area of the piston plate. The magnitude of the damping force is obtained by the following formula:

[0068]

[0069] where F represents the damping force;

[0070] a represents the flow coefficient;

[0071] a1 represents the surface area of one side of the piston plate;

[0072] a2 represents the sum of the areas of the damping holes on one side of the piston plate;

[0073] γ represents the specific gravity of the fluid;

[0074] g represents the acceleration due to gravity;

[0075] v represents the movement speed of the piston plate.

[0076] Based on this, the inventor of the present invention found that changing the length of the damping hole, the inner diameter of the lower cylinder, and the diameter of the damping hole can all effectively change the damping coefficient of the damper. Increasing the length of the damping hole can effectively increase the damping ratio of the damper, while decreasing the length of the damping hole will result in a decrease in the damping coefficient of the damper; decreasing the diameter of the damping hole will cause a significant increase in the damping coefficient of the damper, and increasing the diameter of the damping hole will lead to a decrease in the damping coefficient of the damper.

[0077] Furthermore, in the present application, multiple piston plates can be configured for the vibration isolator, and the sizes of the multiple piston plates are not the same, so that a vibration isolator with an appropriate damping coefficient can be selected according to the construction requirements.

[0078] Preferably, the radius of the piston plate 5 is 168 - 172 mm, preferably 170 mm; correspondingly, the inner diameter of the lower cylinder is 176 mm;

[0079] The thickness of the piston plate 5 is 10 - 16 mm, preferably 12 mm;

[0080] The total area of the damping holes 51 on the piston plate 5 is 1000 - 1600 mm 2 , preferably 1200 mm 2 ; The total area refers to the sum of the areas of all the damping holes.

[0081] By selecting the above dimensions of the piston plate 5 in the present application, the damping ratio of the steel spring vibration isolator can be controlled between 6% and 10%; thus, a vibration isolator with the most suitable piston plate can be selected according to the requirements of the construction site to meet the construction requirements.

[0082] The above has described the present utility model in combination with preferred embodiments, but these embodiments are only exemplary and only serve an illustrative role. On this basis, various substitutions and improvements can be made to the present utility model, and these all fall within the protection scope of the present utility model.

Claims

1. A high-damping-ratio steel spring viscous vibration isolator, characterized in that, The vibration isolator includes an upper cover plate (1) and a lower cylinder (2), and a sealing strip (3) for sealed connection is arranged between the upper cover plate (1) and the lower cylinder (2); A steel spring (4), a piston plate (5) and damping liquid (6) are arranged in the lower cylinder (2), and both the steel spring (4) and the piston plate (5) are immersed in the damping liquid (6); The piston plate (5) is horizontally arranged in the lower cylinder (2), and the piston plate (5) divides the lower cylinder (2) into an upper oil chamber and a lower oil chamber; A through damping hole (51) is formed in the piston plate (5). The diameter of the piston plate (5) is slightly smaller than the inner diameter of the lower cylinder (2). A gap is left between the piston plate (5) and the inner wall of the lower cylinder (2). The damping liquid (6) can circulate between the upper oil chamber and the lower oil chamber through the damping hole and the gap.

2. The high-damping-ratio steel spring viscous vibration isolator according to claim 1, wherein The vibration isolator is installed in a floating slab track bed. When the floating slab track bed is in a static state, the liquid level height of the damping liquid (6) in the lower cylinder (2) is above the piston plate (5) and below the sealing strip (3).

3. The high-damping-ratio steel spring viscous vibration isolator according to claim 1, wherein The steel spring (4) is vertically arranged, its bottom abuts against the bottom of the lower cylinder (2), and its top abuts against the piston plate (5).

4. The high-damping-ratio steel spring viscous vibration isolator according to claim 3, wherein An annular support ring (11) extending downward is arranged on the upper cover plate (1), and the bottom of the support ring (11) abuts against the piston plate (5), so as to transmit the vertical force received in the upper cover plate (1) to the piston plate (5) and the steel spring (4) below it.

5. The high-damping-ratio steel spring viscous vibration isolator according to claim 1, wherein A threaded hole is formed in the middle of the upper cover plate (1), A limiting boss (21) protruding inward is arranged at the inner bottom of the lower cylinder (2); a bottom through hole for a bolt to pass through is formed in the limiting boss (21), A central hole (52) is formed in the middle of the piston plate (5), The vibration isolator further includes a bolt (7). The bolt (7) sequentially passes through the bottom through hole on the limiting boss (21), the central hole (52) of the piston plate (5) and the threaded hole on the upper cover plate (1) from bottom to top, and is screwed and fixed with a nut (8), so as to fix the upper cover plate (1) and the lower cylinder (2) into one body.

6. The high-damping-ratio steel spring viscous vibration isolator according to claim 5, wherein The damping holes (51) on the piston plate (5) surround and are evenly distributed around the central hole (52).

7. The high-damping-ratio steel spring viscous vibration isolator according to claim 1, wherein The inner diameter of the lower cylinder (2) is 176 mm; The radius dimension of the piston plate (5) is 168 - 172 mm; The thickness of the piston plate (5) is 10 - 16 mm; The total area of the damping holes (51) on the piston plate (5) is 1000 - 1600 mm 2 .

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