A machine for the production of a plurality of containers
By combining the three-stage vibration reduction structure, the vibration reduction problem of the traction machine under different frequency bands is solved, achieving noise reduction and vibration reduction effects across the entire frequency band, and improving the stability and service life of the equipment.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- ZHEJIANG FEIYA ELEVATOR
- Filing Date
- 2025-09-12
- Publication Date
- 2026-07-24
AI Technical Summary
Existing traction machine vibration damping pads cannot fully cover low, medium, and high frequency vibrations, resulting in excessive noise and accelerated component wear, making it difficult to meet the needs of use under all working conditions.
It adopts a three-stage vibration reduction structure, including a flange seat, a rubber sleeve body, an elastic energy storage component, and a magnetic component, which precisely suppress low, medium, and high frequency vibrations respectively. Through the combined design of a rubber layer, a medium-frequency elastic layer, and a high-frequency magnetic layer, it achieves vibration reduction and noise reduction across the entire frequency band.
It achieves full-frequency vibration reduction for the traction machine during startup, acceleration, and constant speed phases, improving the operational stability and comfort of the equipment and extending its service life.
Smart Images
Figure CN224550701U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of mechanical vibration reduction technology, and in particular to a vibration reduction device for a traction machine. Background Technology
[0002] The existing traction machine is the core power component of elevators and lifting equipment. It drives the traction sheave to rotate through a motor, and uses steel wire ropes to pull the car or heavy object to complete the lifting and lowering movement. It directly determines the operating efficiency and safety of the equipment and is widely used in residential buildings, commercial complexes, industrial plants and other scenarios. It is the key to ensuring the stable operation of vertical transportation systems, and its operating status is directly related to passenger safety, cargo transportation efficiency and the overall service life of the equipment.
[0003] As a crucial auxiliary component of traction machines, vibration damping pads primarily function to buffer the vibrations generated during operation, preventing their transmission to the equipment frame and building structure. They not only reduce vibration-induced noise, improving passenger comfort in the elevator car and minimizing noise pollution in the machine room and surrounding environment, but also reduce wear on internal components such as bearings and gears, extending equipment maintenance cycles and lowering operating costs. Furthermore, they prevent vibration-induced structural resonance, ensuring building safety and making them a key component for meeting industry standards for quiet operation and stability.
[0004] Most vibration damping pads currently on the market do not fully consider the multiple vibration conditions that traction machines experience during actual operation. Low-frequency vibrations (10-50Hz) occur during traction machine start-up, braking, and heavy-load operation; medium-frequency vibrations (50-200Hz) occur during continuous operation; and high-frequency vibrations (200-1000Hz) are generated by bearing friction and electromagnetic effects. Existing vibration damping pads are mostly single-layer structures, only adaptable to a specific frequency band. For example, ordinary rubber pads are insufficient to suppress low-frequency vibrations, and metal springs easily resonate with high-frequency vibrations. They cannot comprehensively cover low, medium, and high-frequency vibrations, resulting in some frequency bands not being suppressed, leading to problems such as excessive noise and accelerated component wear, making it difficult to meet the needs of all operating conditions.
[0005] This proposal is put forward in order to improve and optimize the above-mentioned problems or shortcomings. Utility Model Content
[0006] This utility model provides a shock absorption device for a traction machine to solve the technical problems mentioned in the background art.
[0007] The present invention adopts the following technical solution to solve the above-mentioned technical problems: A shock absorption device for a traction machine includes a flange seat; A primary shock-absorbing structure; the lower end is embedded in the upper surface of the flange seat and fixed relative to it; A secondary damping structure includes a damping sleeve and an elastic energy storage component, wherein the damping sleeve is inserted into the primary damping structure, the elastic energy storage component is embedded in the lower blind hole of the damping sleeve, and the upper and lower ends of the elastic energy storage component abut against the damping sleeve and the flange seat, respectively. The three-stage damping structure includes two magnetic components, one of which is fixed to the lower end face of the damping sleeve and the other is fixed to the flange seat. The adjacent end faces of the two magnetic components have the same magnetic pole, thereby generating a magnetic repulsion force between the two magnetic components. The flange seat is fixed to the traction load-bearing beam by anti-loosening bolts. The upper center of the damping sleeve is provided with a milled screw hole in the damping pad. The milled screw hole in the damping pad passes through the fixing hole on the traction machine and is threadedly connected to the milled screw hole in the damping pad to achieve fixation.
[0008] Preferably, the upper surface of the flange seat is provided with a countersunk hole, and the primary damping structure is embedded and fixed in the countersunk hole. The interference fit of the countersunk hole locks the axial and circumferential degrees of freedom of the primary damping structure.
[0009] Preferably, the primary shock absorption structure includes a rubber sleeve body and a metal frame, wherein the metal frame is disposed inside the rubber sleeve body as a frame and is embedded inside the rubber sleeve body by a vulcanization process.
[0010] Preferably, the metal frame is a ring structure, and its cross-section can be a circle, triangle, square, or other conventional geometric shapes. The metal frame supports the cylindrical sleeve structure of the rubber sleeve body after being embedded in the rubber sleeve body through its own rigid structure.
[0011] Preferably, the outer surface of the rubber sleeve body 11 is provided with a threaded groove structure, and the helix angle is 15°-20°.
[0012] Preferably, the elastic energy storage component includes a spring, which is a cylindrical helical spring structure. The lower end of the shock absorber sleeve is provided with a downwardly open guide countersunk hole. The spring is installed in the guide countersunk hole and is inserted into the rubber sleeve body along with the shock absorber sleeve. The spring elastically expands and contracts along the axial direction, and the lower end of the spring abuts against the upper surface of the countersunk hole of the flange seat.
[0013] Preferably, the outer wall of the shock-absorbing sleeve and the inner wall of the rubber sleeve body abut against each other, and the outer wall of the shock-absorbing sleeve and the inner wall of the rubber sleeve body form frictional damping.
[0014] Preferably, the spring has a variable diameter structure, with an upper diameter of 50-60mm and a lower diameter of 70-80mm.
[0015] Preferably, the three-stage damping structure includes two magnetic components: a lower magnetic ring and an upper magnetic ring. The lower magnetic ring is fixed in the countersunk hole of the flange seat, and the upper magnetic ring is fixed on the lower surface of the damping sleeve. The lower magnetic ring and the upper magnetic ring are coaxially arranged, and a magnetic repulsion force is generated between the lower magnetic ring and the upper magnetic ring.
[0016] The advantages and positive effects of this utility model are: Reasonable frequency band adaptation: For low, medium and high frequency vibrations during the start-up, acceleration and constant speed stages of the traction machine, the low frequency rubber layer, medium frequency elastic layer and high frequency magnetic layer are used to precisely suppress them, so as to achieve vibration reduction and noise reduction throughout the entire operation cycle.
[0017] Excellent structural performance: The spiral design of the low-frequency layer enhances compressive stress resistance, the variable diameter spring and shock-absorbing sleeve of the mid-frequency layer prevents displacement, and the magnetic vibration filtering of the high-frequency layer ensures both durability and shock absorption effect in each layer structure.
[0018] Wide range of applications: It can be adapted to various scenarios such as industrial lifting and elevators, especially meeting the needs of large-tonnage equipment. The components are easy to replace and adapt to different high-frequency vibration conditions. Attached Figure Description
[0019] The present invention will be further described below with reference to the accompanying drawings and embodiments.
[0020] Figure 1 This is a schematic diagram of the structure of this utility model after assembly; Figure 2 This is an assembly diagram of the utility model and the traction machine; Figure 3 This is an exploded structural diagram of the present invention; Figure 4 This is a cross-sectional structural diagram of the present invention; Figure 5 yes Figure 3 A partial cross-sectional structural diagram of the middle damping sleeve; Figure 6 yes Figure 3 Schematic diagram of the structure of the rubber sleeve body; Figure 7 This is a schematic diagram of the metal skeleton in this utility model; Figure 8 This is a schematic diagram of the metal skeleton in this utility model (another embodiment).
[0021] The attached diagram is labeled as follows: 0, traction load-bearing beam; 2, anti-loosening bolt; 3, traction machine; 10, flange seat; 110, metal frame; 11, rubber sleeve body; 12, shock-absorbing sleeve; 13, spring; 14, upper magnetic ring; 15, lower magnetic ring; 121, milled screw hole inside the shock-absorbing pad; 122, guide countersunk hole. Detailed Implementation
[0022] The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, illustrating only the basic structure of the present invention, and therefore only show the components relevant to the present invention.
[0023] If the embodiments of this application contain terms relating to directional indications or positional relationships (such as up, down, left, right, front, back, inside, outside, top, bottom, center, vertical, horizontal, longitudinal, transverse, length, width, counterclockwise, clockwise, axial, radial, circumferential, etc.), such terms are only used to explain the relative positional relationships and movement of the components in a specific posture (as shown in the attached figures); if the specific posture changes, the directional indications or positional relationships will also change accordingly. Furthermore, the terms "first" and "second" used in the embodiments of this application are only for descriptive convenience and should not be construed as indicating or implying relative importance. The embodiments of this utility model will be further described in detail below with reference to the accompanying drawings: Example 1: like Figure 1-8 As shown, the traction machine vibration damping device of this utility model includes a flange seat 10; A primary shock-absorbing structure; the lower end is embedded in the upper surface of the flange seat 10 and fixed thereto; A secondary damping structure includes a damping sleeve 12 and an elastic energy storage component, wherein the damping sleeve 12 is installed inside the primary damping structure, the elastic energy storage component is embedded in the lower blind hole of the damping sleeve 12, and the upper and lower ends of the elastic energy storage component abut against the damping sleeve 12 and the flange seat 10, respectively. The three-stage damping structure includes two magnetic components, one of which is fixed to the lower end face of the damping sleeve 12 and the other is fixed to the flange seat 10. The adjacent end faces of the two magnetic components have the same magnetic pole, thereby generating a magnetic repulsion force between the two magnetic components. The flange seat 10 is fixed to the traction load-bearing beam 0 by anti-loosening bolts 2. The upper center of the damping sleeve 12 is provided with a damping pad milled screw hole 121. The damping pad milled screw hole 121 passes through the fixing hole on the traction machine 3 and is threadedly connected to the damping pad milled screw hole 121 to achieve fixation.
[0024] Preferably, the upper surface of the flange seat 10 is provided with a countersunk hole, and the primary damping structure is embedded and fixed in the countersunk hole. The interference fit of the countersunk hole locks the axial and circumferential degrees of freedom of the primary damping structure.
[0025] Preferably, the primary damping structure includes a rubber sleeve body 11 and a metal frame 110, wherein the metal frame 110 is disposed inside the rubber sleeve body 11 as a frame and is embedded inside the rubber sleeve body 11 by a vulcanization process. The rubber body 111 is made of nitrile rubber, which has excellent oil resistance and aging resistance, so as to reduce low-frequency large displacement vibration (frequency 10-50Hz, displacement ≤5mm) during the start-up phase of the traction machine.
[0026] Preferred, such as Figure 7 The metal skeleton 110 is a ring structure, and its cross-section can be circular, triangular, square, or other conventional geometric shapes. After being embedded in the rubber sleeve body 11 through its own rigid structure, the metal skeleton 110 supports the cylindrical sleeve structure of the rubber sleeve body 11, providing rigid support force during the deformation of the rubber sleeve body 11 under pressure, thereby improving the deformation resistance of the rubber sleeve body 11. As an example, the metal skeleton 110 can be made of Q235 steel.
[0027] Preferably, the rubber sleeve body 11 has a threaded groove structure on the outside, and the helix angle is 15°-20°. By optimizing and adjusting the external structure, the compressive stress is enhanced by utilizing the structural mechanical properties of the arc groove surface (compressive stress is increased by 40%-50%, which is obtained through finite element analysis and solid structure experiments).
[0028] Preferably, the elastic energy storage component includes a spring 13, which is a cylindrical helical spring structure. The lower end of the shock-absorbing sleeve 12 is provided with a downwardly open guide countersunk hole 122. The spring 13 is installed in the guide countersunk hole 122 and is installed in the rubber sleeve body 11 along with the shock-absorbing sleeve 12. The spring 13 elastically expands and contracts along the axial direction. The lower end of the spring 13 abuts against the upper surface of the countersunk hole of the flange seat 10. When the axial vibration force acts on the shock-absorbing sleeve 12, the spring 13 undergoes elastic deformation. Specifically, the spring 13 is made of 60Si2Mn spring steel, which has high elastic limit and fatigue strength.
[0029] Preferably, the outer wall of the shock-absorbing sleeve 12 abuts against the inner wall of the rubber sleeve body 11. When the axial vibration force acts on the shock-absorbing sleeve 12, the rubber sleeve body 11 and the spring 13 provide joint support, and the outer wall of the shock-absorbing sleeve 12 and the inner wall of the rubber sleeve body 11 form frictional damping to prevent the shock-absorbing sleeve 12 from bouncing up and down.
[0030] Preferably, the spring 13 has a variable diameter structure with an upper diameter of 50-60mm and a lower diameter of 70-80mm, which is suitable for the medium-frequency vibration (frequency 50-200Hz) during the acceleration phase of the traction machine. It can absorb vibration energy through elastic deformation, further unload the load, achieve a smooth transition of vibration energy, and avoid sudden changes in impact load.
[0031] Preferably, the three-stage damping structure includes two magnetic components: a lower magnetic ring 15 and an upper magnetic ring 14. The lower magnetic ring 15 is fixed in the countersunk hole of the flange seat 10, and the upper magnetic ring 14 is fixed on the lower surface of the damping sleeve 12. The lower magnetic ring 15 and the upper magnetic ring 14 are coaxially arranged, and a magnetic repulsive force is generated between the lower magnetic ring 15 and the upper magnetic ring 14 (specifically, the lower surface of the upper magnetic ring 14 and the upper surface of the lower magnetic ring 15 have the same magnetic poles). The magnetic field force filters out the high-frequency vibration (frequency 200-1000Hz) during the uniform speed stage of the traction machine.
[0032] Example 2: Different from the previous example, such as Figure 8 The metal skeleton 110 has a continuous spiral structure. The spiral structure not only provides anti-deformation support for the rubber sleeve body 11 in the circumferential direction, but also provides auxiliary support in the axial direction through the spiral elasticity. This prevents the rubber sleeve body 11 from undergoing excessive deformation in the axial direction at the moment of vibration pressure, thereby improving the overall stability and service life of the rubber sleeve body 11.
[0033] It should be emphasized that the embodiments described in this utility model are illustrative rather than limiting. Therefore, this utility model is not limited to the embodiments described in the specific implementation. Any other implementation methods derived by those skilled in the art based on the technical solutions of this utility model are also within the scope of protection of this utility model.
Claims
1. A traction machine vibration damping device, comprising a flange seat (10); characterized in that: Also includes A primary shock-absorbing structure; the lower end is embedded in the upper surface of the flange seat (10) and fixed relative to it; A secondary damping structure includes a damping sleeve (12) and an elastic energy storage component, wherein the damping sleeve (12) is installed inside the primary damping structure, the elastic energy storage component is embedded in the lower blind hole of the damping sleeve (12), and the upper and lower ends of the elastic energy storage component abut against the damping sleeve (12) and the flange seat (10) respectively. The three-stage shock absorption structure includes two magnetic components, one of which is fixed to the lower end face of the shock absorption sleeve (12) and the other is fixed to the flange seat (10). The adjacent end faces of the two magnetic components have the same magnetic poles, and there is magnetic repulsion between the two magnetic components. The flange seat (10) is fixed to the traction load-bearing beam (0) by bolts. The upper center of the damping sleeve (12) is provided with a damping pad milled screw hole (121). The damping pad milled screw hole (121) passes through the fixing hole on the traction machine (3) and is threadedly connected to the damping pad milled screw hole (121) to achieve fixation.
2. The traction machine vibration damping device according to claim 1, characterized in that: The upper surface of the flange seat (10) is provided with a countersunk hole, and the primary damping structure is embedded and fixed in the countersunk hole. The axial and circumferential degrees of freedom of the primary damping structure are locked by the interference fit of the countersunk hole.
3. The traction machine vibration damping device according to claim 1, characterized in that: The primary shock absorption structure includes a rubber sleeve body (11) and a metal frame (110), wherein the metal frame (110) is set inside the rubber sleeve body (11) as a frame and is embedded inside the rubber sleeve body (11) by a vulcanization process.
4. A traction machine vibration damping device according to claim 3, characterized in that: The metal frame (110) is a ring structure, and its cross-section can be circular, triangular or square. The metal frame (110) supports the cylindrical sleeve structure of the rubber sleeve body (11) after being embedded in the rubber sleeve body (11) through its own rigid structure.
5. A traction machine vibration damping device according to claim 3, characterized in that: The metal skeleton (110) has a continuous spiral structure.
6. A traction machine vibration damping device according to any one of claims 3-5, characterized in that: The rubber sleeve body (11) has a threaded groove structure on the outside, and the helix angle is 15°-20°.
7. A traction machine vibration damping device according to claim 3, characterized in that: The elastic energy storage component includes a spring (13), which is a cylindrical helical spring. The lower end of the shock-absorbing sleeve (12) is provided with a downward-opening guide countersunk hole (122). The spring (13) is installed in the guide countersunk hole (122) and is installed in the rubber sleeve body (11) along with the shock-absorbing sleeve (12). The spring (13) elastically expands and contracts along the axial direction. The lower end of the spring (13) abuts against the upper surface of the countersunk hole of the flange seat (10).
8. A traction machine vibration damping device according to claim 3, characterized in that: The outer wall of the shock-absorbing sleeve (12) abuts against the inner wall of the rubber sleeve body (11), and the outer wall of the shock-absorbing sleeve (12) and the inner wall of the rubber sleeve body (11) form frictional damping.
9. A traction machine vibration damping device according to claim 7, characterized in that: The spring (13) has a variable diameter structure, with an upper diameter of 50-60mm and a lower diameter of 70-80mm.
10. A traction machine vibration damping device according to claim 1, characterized in that: The three-stage damping structure includes two magnetic components: a lower magnetic ring (15) and an upper magnetic ring (14). The lower magnetic ring (15) is fixed in the countersunk hole of the flange seat (10), and the upper magnetic ring (14) is fixed on the lower surface of the damping sleeve (12). The lower magnetic ring (15) and the upper magnetic ring (14) are coaxially arranged, and a magnetic repulsion force is generated between the lower magnetic ring (15) and the upper magnetic ring (14).