CN111778781A - A Rigidly Connected Broadband Composite Rail Dynamic Vibration Absorber - Google Patents

Abstract

The invention relates to a rigidly-connected broadband composite type steel rail dynamic vibration absorber which comprises a steel rail (1), a vibration absorber body (2) and a rigid fixing frame (3), wherein the vibration absorber body (2) comprises a central long shaft (201), end clamping blocks positioned at two ends of the central long shaft, a plurality of middle elastic units (204) and middle mass blocks (205) which are positioned in the middle of the central long shaft and distributed at intervals in a staggered mode, wherein a first end clamping block (203) and a second end clamping block (206) are in fit contact with the rail web of the steel rail and are fixed on the steel rail through the rigid fixing frame (3). Compared with the prior art, the rigid connection broadband composite adjustable frequency setting improves the attenuation rate of the vibration propagation of the steel rail, effectively controls the abrasion of the wheel rail and reduces the vibration noise pollution of the rail transit.

Description

A Rigidly Connected Broadband Composite Rail Dynamic Vibration Absorber

technical field

The invention relates to the technical field of rail transportation, in particular to a rigidly connected broadband composite rail dynamic vibration absorbing device, which is especially used for vibration absorbing control of the vibration and noise generated by the forced rail during the operation of the rail vehicle.

Background technique

At present, while the rapid development of urban rail transit provides people with a fast and safe way to travel, the noise and vibration problems it produces also seriously affect the quality of life of surrounding residents, endanger the safety of buildings around the line, and make the rail itself. Stability, safety and longevity are also affected. Studies have shown that when the train speed is lower than 100km/h, the rolling noise formed between the wheel and rail is the main component of the rail traffic noise and vibration. contribution is particularly evident. The most effective way to control vibration and noise is to take measures from the vibration source or block the transmission of vibration and noise. Therefore, the control of rail vibration and noise is of great significance to the vibration and noise reduction of urban rail transit.

In order to control the vibration and noise of the rail, engineers have developed various types of vibration reduction and noise reduction products. Among them, the tuned shock absorber is more common, which uses a tuning device composed of a mass-spring to generate a reaction force when the rail vibrates as a power consumption energy. To reduce the vibration of the rail, for example, the rail damper disclosed in the patent CN202530345U, such products have a certain effect of damping and reducing noise. However, in engineering applications, it is found that such product mass blocks are covered with elastomers, and the elastomers are exposed to the damp environment of tunnels or elevated exposure, and the elastomers are seriously affected by environmental aging; at the same time, the installation method of rail shock absorbers is The buckle is directly in contact with the upper surface of the elastomer. With the periodic wheel-rail impact, the contact surface of the elastomer in contact with the buckle will experience environmental corrosion and contact wear, resulting in serious cracks and falling off blocks, and the metal buckle will also experience periodic fatigue. Shortcomings such as insufficient clamping force directly affect the effect of vibration reduction and noise reduction.

SUMMARY OF THE INVENTION

The purpose of the present invention is to provide a broadband composite rail dynamic vibration absorbing device with rigid connection with long service life and good sound absorption and noise reduction effect in order to overcome the above-mentioned defects of the prior art.

The purpose of the present invention can be achieved by the following technical solutions: a rigidly connected broadband composite type steel rail dynamic vibration absorption device, comprising a steel rail (1), a vibration absorber body (2) and a rigid fixing frame (3), through the rigid fixing frame Arrange the vibration absorber body symmetrically on both sides of the rail waist.

The vibration absorber body (2) includes a central long axis (201), end clamping blocks located at both ends of the central long axis, a plurality of intermediate elastic units (204) located in the middle of the central long axis and arranged at intervals and staggered. The middle mass block (205), wherein the first end clamping block (203) and the second end clamping block (206) are in consistent contact with the rail waist of the rail, and are fixed on the rail by a rigid fixing frame (3).

The intermediate elastic unit (204) and the intermediate mass (205) are not in contact with the rail.

The center long axis of the vibration absorber body and the end clamping block and the intermediate mass block are in contact and matched with an intermediate elastic material, and the shape, size, quantity and mutual positional relationship between the intermediate elastic unit (204) and the intermediate mass block (205) are adjusted by adjusting , forming multiple groups of extrusion and shearing elastic mass resonance systems, at least two or more vibration frequencies can be controlled, and a broadband composite dynamic vibration absorption device is formed.

An elastic shaft sleeve (209) is sleeved on the central long axis (201), and a plurality of intermediate elastic units (204) and the intermediate mass block (205) are sequentially dislocated and passed through the elastic shaft sleeve (209) of the central long axis (201) external surface.

The middle mass block (205) and the elastic bushing (209) constitute a first spring-mass resonance system, and the resonance mode of the first spring-mass resonance system is vertical or lateral (perpendicular to the rail waist direction);

The middle elastic unit (204) and the middle mass block (205) constitute a second spring-mass resonance system, and the vibrator direction of the second spring-mass resonance system is vertical, lateral or longitudinal along the length of the rail, and has a long axis (201) along the center. ) radial extrusion and longitudinal shear composite effect along the length of the rail. By changing the shape, size or quantity of the intermediate elastic unit (204) and the intermediate mass (205), a wide frequency band can be adjusted to the natural frequency of the system. The shape of the intermediate elastic unit (204) and the intermediate mass (205) is circular, square or rhombus.

The end clamping block of the vibration absorber body (2) is passed through the central long axis (201), and an embedded elastic body (208) is arranged between the end clamping block and the central long axis (201) in sequence. ) and an embedded metal block (207), wherein a concave-convex matching structure is formed between the embedded elastic body (208) and the inner cavity of the end clamping block, and the inner cavity of the embedded elastic body (208) and the embedded metal block are (207) a concave-convex matching structure is formed between them;

The elastic body (208) is embedded between the central long axis (201) and the end clamping block to form a spring-mass resonance system of the central long axis, and the direction of the vibrator is vertical, lateral or longitudinal along the length of the rail;

The embedded metal block (207) and the embedded elastic body (208) form an auxiliary spring mass system, and the resonance direction is lateral or vertical.

The ends of the central long axis (201) of the vibration absorber body (2) are respectively provided with threads, and the length of the external thread can not only ensure the clamping of the vibration absorber body (2), but also ensure that the intermediate elastic unit (204) has a compression amount , the external thread and the nut (202) are matched and locked; the cross-sectional shape of the central long axis (201) is a circle, a square, a stepped shape or other shapes.

The rigid fixing frame (3) is composed of a connecting bottom plate (301), a body pressing plate (302) and bolts, the connecting bottom plate (301) passes through and contacts the bottom of the rail, and one end of the body pressing plate (302) and the end clamping block The other end is rigidly connected with the under-rail connecting bottom plate (301), and the vibration absorbing device is rigidly fixed on the steel rail (1). The number of rigid fixing frames required for the body of the vibration absorbing device is determined by the number of the intermediate mass block and the intermediate elastic unit.

The end clamping block includes a boss column provided thereon, and the body pressing plate (302) is provided with a through hole (303) that is rigidly matched with the boss column of the end clamping block.

Due to the different working conditions of the track structure and running vehicles, the vibration of the track system and its noise have the characteristics of wide frequency band and multi frequency band. The present invention adopts the broadband composite type steel rail vibration absorber with rigid connection to solve the problem from the source from the track/ One of the ways to reduce the vibration and noise problem of the rail system. The use of dynamic vibration absorber can greatly reduce the vibration amplitude of the rail and reduce the noise and vibration radiation caused by vibration.

Compared with the prior art, the present invention starts from the source of the problem, so as to control or reduce the vibration and noise of the rail system. The present invention provides a rigidly connected broadband composite type rail dynamic vibration absorbing device. The shaft connects multiple independent spring mass systems to form a multi-order resonance assembly, and the resonance mass blocks are arranged along the length of the rail to form a wave dynamic damping vibration absorber. The biggest advantage of the present invention that distinguishes the existing patents: the intermediate resonance mass and the elastic block are not in contact with the rail, and the surface of the central axis is covered with an elastic layer, so that the mass-spring unit forms a multi-degree-of-freedom extrusion and shearing along the rail system. type spring mass system, the frequency involved is a wide frequency range; the vibration absorber body is connected to the rail through a rigid fixing frame, which avoids the elastic connection attenuation of the existing vibration absorber and the problem of the vibration absorber falling off. At the same time of vertical vibration, by raising the center of the vibration absorber body, the consumption of lateral vibration energy of the rail is further improved, and the transmission of vibration energy along the rail direction is suppressed at the same time.

Description of drawings

Fig. 1 is the overall view of implementation case 1 of the present invention;

Fig. 2 is the left side view of embodiment 1 of the present invention;

Fig. 3 is the front view of the vibration absorber body of the embodiment 1 of the present invention;

4 is a cross-sectional view of the vibration absorber body of Embodiment 1 of the present invention;

FIG. 5 is a schematic diagram of the end clamping block of Embodiment 1 of the present invention;

FIG. 6 is a schematic diagram of the structure of an elastomer embedded in the inner cavity of the end clamping block according to Embodiment 1 of the present invention;

7 is a schematic diagram of the metal embedded structure in the inner cavity of the end clamping block according to Embodiment 1 of the present invention;

Fig. 8 is the schematic diagram of the middle elastic unit of the implementation case 1 of the present invention;

Fig. 9 is the schematic diagram of the intermediate mass block of the implementation case 1 of the present invention;

Fig. 10 is the schematic diagram of the center long axis of the implementation case 1 of the present invention;

FIG. 11 is a schematic diagram of the rigid fixing frame of Embodiment 1 of the present invention;

The numbers in the figure show: steel rail 1, vibration absorber body 2, central long axis 201, nut 202, first end clamping block 203, middle elastic unit 204, middle mass block 205, second end clamping block 206, Embedded metal block 207 , embedded elastic body 208 , elastic bushing 209 , rigid fixing frame 3 , connecting bottom plate 301 , body pressing plate 302 , pressing plate through hole 303 .

Detailed ways

The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

Example 1

As shown in Figure 1-2, a rigidly connected broadband composite type steel rail dynamic vibration absorbing device includes a steel rail 1, a vibration absorber body 2 and a rigid fixing frame 3, the end clamp block 203 of the vibration absorber body 2 and the rail waist of the steel rail 1 contact, and the vibration absorber body 2 is symmetrically arranged on both sides of the rail waist through the rigid fixing frame 3 . The vibration absorber device body 2 consists of a central long axis 201, an end nut 202 passing through the central long axis in sequence, a first end clamping block 203, an intermediate elastic unit 204 and an intermediate mass block 205, which are staggered and arranged. The second end clamping block 206, etc.; the end clamping block of the vibration absorber body is in contact with the rail waist, while the middle mass block 205 and the middle elastic unit 204 are not in contact with the steel rail; the vibration absorber body 2 The center long axis 201 and the end clamping block and the middle mass block are in contact and matched with an intermediate elastic material. A group of elastic mass resonance systems such as extrusion and shearing can control at least two or more vibration frequencies to form a broadband composite dynamic vibration absorption device; the rigid fixing frame and the vibration absorber body are rigidly connected, and are fixed by bolts. The vibration absorber body is rigidly fixed on the rail.

As shown in Figures 3, 4, 8, 9, and 5, the middle elastic unit 204 of the vibration absorber body 2 and the middle mass block 205 are sequentially dislocated and worn on the outer surface of the elastic sleeve 209 of the central long axis 201 by bonding, and the two No contact with the rail after installation; the middle mass block 205 and the central elastic bushing 209 form a vertical and lateral (perpendicular to the rail waist direction) spring mass resonance system; the middle mass block 205 and the middle elastic unit 204 also form a second spring mass In the resonance system, the direction of the vibrator can be vertical, lateral or longitudinal along the length of the rail, and has compound effects such as radial extrusion along the central long axis 201 and longitudinal shear along the length of the rail. By changing the shape, size or quantity of the intermediate elastic unit 204 and the intermediate mass 205, a wide frequency band can be adjusted to the natural frequency of the system. The shape of the intermediate mass 205 and the intermediate elastic unit 204 may be circular, or may be square or rhombus.

As shown in Figures 5-7, the inner cavity of the first end clamping block 203 of the vibration absorber body 2 is matched with the boss of the embedded elastic body 208, and the inner cavity matching surface of the first end clamping block 203 can also be concave groove; the inner cavity of the embedded elastic body 208 is matched with the concave-convex structure of the embedded metal block 207, and the mating surface of the inner cavity of the elastic body can also be a groove or a boss; the embedded metal block 207 and the embedded elastic body 208 form another auxiliary For spring-mass systems, the resonance direction can be lateral or vertical.

As shown in FIG. 10 , the ends of the central long axis 201 of the vibration absorber body 2 are respectively provided with threads, which are matched with the nut 202 and clamped; the shape of the central long axis 201 can be round, square, stepped or other cross-sections Shape; the central long axis 201 of the vibration absorber body 2 and the first end clamping block 203 and the second end clamping block 206 also form a spring mass resonance system with the central long axis through the elastic body 208, and the direction of the vibrator can be vertical. longitudinally, transversely or longitudinally along the length of the rail.

As shown in Figures 2 and 11, the rigid fixing frame 3 is composed of a connecting bottom plate 301, a body pressing plate 302 and bolts. The connecting bottom plate 301 passes through the rail bottom and contacts the rail, and one end of the body pressing plate 302 has a through hole 303 and an end clamping block 203. , 206 The boss column is rigidly matched, and the other end of the body pressing plate 302 is rigidly connected and tightened with the lower rail connecting base plate 301 through bolts and nuts, and the vibration absorption device is rigidly fixed on the rail 1 . The number of rigid fixing frames 3 required for the body 2 of the vibration absorbing device is determined by the number of the intermediate mass blocks 205 and the intermediate elastic units 204 .

Example 2

The second embodiment is basically the same as the first embodiment in terms of structure and requirements. The difference is that the second embodiment increases the center height of the central long axis 201, and at the same time increases the position of the center of gravity of the vibration absorbing equipment. The main purpose of designing the rail vibration absorbing device is to reduce the vibration of the rail itself. Since the rail transit line has straight sections and curved sections, the implementation case 1 works well in the straight section, and the embodiment 2 mainly considers the lateral vibration of the rail when the train passes through the curved section. It is larger than the vertical direction, and the vibration of the rail head is also significantly larger than the vibration of the rail angle. In order to have a better vibration absorption effect, the invented device must be attached to the rail head as much as possible to reduce the vibration of the rail head. Therefore, Example 2 In the design, the center of gravity of the central long axis 201 is raised, and the position of the mass spring system is raised, which can further reduce the lateral and torsional vibration of the rail head and improve the torsional stiffness of the rail.

Example 3

Embodiment 3 is basically the same as Embodiment 1 and 2 in terms of structure and requirements. The difference is that Embodiment 3 changes the support structure of the rigid fixing frame 3. The rigid fixing frame 3 is divided into the upper structure 302 of the body platen to improve the position of the vibration absorber body. And as close as possible to the position of the rail head and fix it, the lower structure of the body pressing plate 302 of the rigid fixing frame 3 is fixed at the corner of the rail. The main purpose of the design is still to reduce the vibration of the rail head by increasing the position of the vibration absorbing device when the train passes through the curved section.

Compared with the existing damping body, the above structure of the present invention has the following advantages:

1. The elastic body of the existing vibration absorber is completely exposed to humidity or exposure to the sun, and the elastic body is seriously affected by environmental aging; and the central elastic sleeve 209 with the largest area of the present invention is wrapped inside, not affected by the environment, and the only The middle elastic unit 204 exposed to the outside and the middle mass block 205 are arranged in dislocation, and its width is only (1-2)/10 of the width of the adjacent middle mass block, and it is easy to replace even if it ages;

2. The installation method of the existing rail shock absorber is that the elastic buckle directly contacts the upper surface of the elastic body. With the periodic wheel-rail impact and vibration, the contact surface of the elastic body appears environmental corrosion and contact wear, resulting in cracks, which will fall off in severe cases. At the same time, the metal elastic buckle has shortcomings such as insufficient clamping force due to periodic fatigue, which directly affects the effect of vibration reduction and noise reduction; and the fixing structure of the present invention is that the fixing frame 3 is connected to the boss of the metal block on the end clamping block. , The end clamps are in complete contact with the rail, and the connection process is rigid, so there will be no environmental corrosion that causes serious cracks and falls off the block. The vibration absorbing body is connected to the rail through a rigid fixing frame, which avoids problems such as the vibration absorber falling off due to the attenuation of the elastic connection of the existing vibration absorber.

可知，由于本发明的质量块相对现 有减振器大，吸振器本体整体质量放大，在控制频率方面将延伸到中低频，同时与 质量振子组合的弹性单元变薄(中间弹性块单元及长轴上弹性轴套)使得其刚度也 在增加，因此复合型吸振器设计可使得本发明的控制频率范围在200-1500Hz(横 向及垂向)，预期钢轨的振动水平降低15-25dB，相应轮轨耦合引起的噪声辐射水 平降低5-10dB(A)。3. The vibration absorbing device of the present invention only has the end clamping block in contact with the rail, and the middle mass block 205 as the vibrator not only forms a compressibility with the elastic block 204, but also forms a shearing type with the middle long axis elastic sleeve 209 and other compound vibration-absorbing functions. from a single free vibration system

It can be seen that since the mass block of the present invention is larger than the existing shock absorber, the overall mass of the shock absorber body is enlarged, and the control frequency will be extended to the middle and low frequencies, and the elastic unit combined with the mass oscillator will become thinner (the middle elastic block unit and the long Therefore, the design of the composite vibration absorber can make the control frequency range of the present invention in the range of 200-1500Hz (horizontal and vertical), and the vibration level of the rail is expected to be reduced by 15-25dB. Noise radiation levels due to rail coupling are reduced by 5-10dB(A).

The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit the present invention. Changes, substitutions, modifications and simplifications made by those of ordinary skill in the art within the essential scope of the present invention are all equivalent transformations. It does not deviate from the spirit of the present invention, and should also belong to the protection scope of the claims of the present invention.

Claims (10)

1. The utility model provides a broadband compound rail power vibration absorber of rigid connection, includes rail (1), bump leveller body (2) and rigidity mount (3), its characterized in that, bump leveller body (2) including central major axis (201), and be located the tip grip block at the both ends of central major axis, be located central major axis middle interval stagger a plurality of middle elastic element (204) and middle quality piece (205) of arranging, wherein first tip grip block (203) and second tip grip block (206) coincide with the rail web of rail and contact to be fixed in on the rail through rigidity mount (3).

2. The rigidly connected broadband composite rail dynamic vibration absorber according to claim 1, wherein the intermediate elastic unit (204) and the intermediate mass (205) are not in contact with the rail.

3. The rigidly connected broadband composite type rail dynamic vibration absorber of claim 1, wherein a plurality of groups of compression-shear elastic mass resonance systems are formed by adjusting the shape, size, number and mutual position relationship of the intermediate elastic unit (204) and the intermediate mass block (205), at least two or more vibration frequencies can be controlled, and a broadband composite type rail dynamic vibration absorber is formed.

4. The rigidly connected broadband composite type steel rail dynamic vibration absorber device as claimed in claim 1, wherein the central long shaft (201) is sleeved with an elastic shaft sleeve (209), and a plurality of intermediate elastic units (204) and intermediate mass blocks (205) are sequentially staggered and penetrate through the outer surface of the elastic shaft sleeve (209) of the central long shaft (201).

5. The rigidly connected broadband composite type steel rail dynamic vibration absorber device as claimed in claim 4, wherein the intermediate mass (205) and the elastic shaft sleeve (209) form a first spring-mass resonance system, and the first spring-mass resonance system is in a mode of vertical extrusion or transverse shear;

the middle elastic unit (204) and the middle mass block (205) form a second spring mass resonance system, the vibrator direction of the second spring mass resonance system is vertical, horizontal or longitudinal along the length of the steel rail, and meanwhile, the second spring mass resonance system has radial extrusion along a central long axis (201) and longitudinal shearing composite effect along the length direction of the steel rail.

6. The rigidly connected broadband composite type steel rail dynamic-vibration absorbing device of claim 1, 2, 3 or 4, wherein the external shapes of the middle elastic unit (204) and the middle mass block (205) are circular, square or diamond.

7. The rigidly-connected broadband composite type steel rail dynamic vibration absorber device as claimed in claim 1, wherein the end clamping block of the vibration absorber body (2) is inserted into the central long shaft (201), and an embedded elastic body (208) and an embedded metal block (207) are sequentially arranged between the end clamping block and the central long shaft (201), wherein a concave-convex matching structure is formed between the embedded elastic body (208) and an inner cavity of the end clamping block, and a concave-convex matching structure is formed between the inner cavity of the embedded elastic body (208) and the embedded metal block (207);

a spring mass resonance system of the central long shaft is formed between the central long shaft (201) and the end clamping block through an embedded elastic body (208), and the vibrator direction is vertical, horizontal or longitudinal along the length of the steel rail;

the embedded metal block (207) and the embedded elastic body (208) form an auxiliary spring mass system, and the resonance direction is transverse or vertical.

8. The rigidly connected broadband composite type steel rail dynamic vibration absorber device as claimed in claim 1, wherein the end of the central long axis (201) of the vibration absorber body (2) is provided with an external thread, the length of the external thread ensures that the vibration absorber body (2) is clamped and the intermediate elastic unit (204) has a compression capacity, and the external thread is matched and locked with the nut (202); the cross-sectional shape of the central long axis (201) is circular, square, stepped or other shape.

9. The rigidly-connected broadband composite type steel rail dynamic vibration absorber of claim 1, wherein the rigid fixing frame (3) comprises a connecting bottom plate (301), a body pressing plate (302) and bolts, the connecting bottom plate (301) penetrates through the rail bottom of the steel rail and contacts with the rail bottom, one end of the body pressing plate (302) is connected with the end clamping block in a matching manner, and the other end of the body pressing plate is rigidly connected with the under-rail connecting bottom plate (301) to rigidly fix the vibration absorber on the steel rail (1).

10. The rigidly connected broadband composite type steel rail dynamic vibration absorber device according to claim 1, wherein the end clamping block comprises a boss pillar, and the body pressing plate (302) is provided with a through hole (303) rigidly matched with the boss pillar of the end clamping block.

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