Double-roller crusher

Abstract

The utility model discloses a roll crusher which comprises a feed port, a shell, a discharge port, a support frame, a motor speed reducer, a driving roll pinion, a driven roll gearwheel, a motor gear, a spring support seat, a spring, a sliding bearing seat, a fixed bearing seat, a driving roll and a driven roll, short and thick cylindrical crossed roller teeth are uniformly distributed on the roller surfaces of the driving roller and the driven roller, the driving roller is rigidly fixed in the shell through a fixed bearing seat, the driven roller is elastically connected with the shell through a sliding bearing seat, and the rear side of the sliding bearing seat and a spring supporting seat form a buffer mechanism through a spring; a motor gear drives a driving roller pinion and a driven roller bull gear to rotate at differential speed, and the rotation speed difference of the two rollers is combined with crossed roller teeth to form double crushing effects of shearing and extruding on materials; when a hard object is clamped in, the driven roller moves backwards through the sliding bearing seat and compresses the spring to buffer impact force, and tooth breakage and motor overload are avoided.

Description

Technical Field

[0001] This utility model provides a crusher, and particularly relates to a double roll crusher. Background Technology

[0002] A double-roll crusher is a device that crushes materials through the squeezing and shearing action between the roller surfaces. It is widely used in the mining, metallurgy, and building materials industries for processing medium-hard materials such as coal and ore. The basic structure of a traditional single-roll crusher includes a shell, feed inlet, discharge outlet, a motor-driven single roller, and a fixed support system. Its working principle is that the motor drives the single roller to rotate at high speed, and the material is squeezed and crushed between the roller teeth and the shell. However, this type of single-roll structure has significant drawbacks: the roller teeth are prone to breakage or wear under continuous high loads, and material easily gets stuck in the gap between the roller teeth, causing the equipment to jam and leading to motor overload; at the same time, the unidirectional crushing action of the single roller makes it difficult to achieve uniform material refinement, resulting in large fluctuations in the particle size of the finished product, which is difficult to meet the needs of fine production.

[0003] The core problems of existing single-roll crushers lie in their rigid, fixed structure and single crushing mode. First, the single roll is rigidly connected to the housing through a fixed bearing seat, making it impossible to dynamically adjust the roll gap according to the material hardness. The hard compression can easily lead to tooth breakage and motor stalling. Second, single-roll unidirectional crushing relies solely on the rolling of the roll teeth at a single rotation speed, lacking the synergistic effect of shearing and differential speed, resulting in low crushing efficiency and poor particle uniformity. In addition, the lack of a buffer protection mechanism means that the impact of large pieces of material is directly transmitted to the motor and gear system, exacerbating equipment wear. Utility Model Content

[0004] In order to solve the above problems, this application provides a double roll crusher that solves the defects of single roll tooth breakage, jamming and uneven particle size. It adopts a double roll differential drive, spring buffer and cross roll tooth design to improve crushing efficiency and protect the motor.

[0005] To solve the above-mentioned technical problems, this utility model provides the following technical solution: a double roll crusher, comprising: a feed inlet, a shell, a discharge outlet, a support frame, a motor reducer, a small gear of the drive roll, a large gear of the driven roll, a motor gear, a spring support seat, a spring, a sliding bearing seat, a fixed bearing seat, a drive roll, and a driven roll;

[0006] The active roller and the passive roller have multiple sets of cylindrical roller teeth evenly distributed and welded on their roller surfaces, and the roller teeth of the two rollers are arranged in an intersecting manner.

[0007] The active roller is fixed inside the housing by a fixed bearing seat, and the passive roller is fixed inside the housing by a sliding bearing seat;

[0008] A spring support seat is provided on the rear side of the sliding bearing seat, and one end of the spring is connected to the spring support seat and the other end is connected to the sliding bearing seat;

[0009] The output end of the motor reducer is connected to the motor gear, the small gear of the driving roller is installed at the end of the driving roller, and the large gear of the driven roller is installed at the end of the driven roller.

[0010] The motor gear meshes with the small gear of the driving roller and the large gear of the driven roller respectively, so that the speed of the driving roller is greater than the speed of the driven roller.

[0011] The housing is fixed to the support frame by bolts, and the inlet and outlet are respectively connected to the housing.

[0012] Preferably, the number of teeth of the small gear of the active roller and the large gear of the passive roller are different, so as to achieve differential rotation of the active roller and the passive roller.

[0013] Preferably, the sliding bearing seat and the spring are designed to allow the passive roller to slide backward when squeezed by material and to be elastically reset by the spring.

[0014] Preferably, the teeth of the active roller and the passive roller are short and stout cylindrical structures, and the teeth of the two rollers are distributed in an intersecting manner to form a crushing and extrusion zone.

[0015] Preferably, the spring support is fixed to the support frame by welding or bolts.

[0016] One or more technical solutions provided in the embodiments of this application have at least the following technical effects or advantages:

[0017] This double-roll crusher effectively solves the problems of tooth breakage, jamming, and excessively large crushed particles found in existing single-roll crushers through the following structure: It adopts a dual-roll differential speed design with a driving roller and a driven roller. The driving roller is rigidly fixed to the housing via a fixed bearing seat, while the driven roller is elastically connected to the housing via a sliding bearing seat. A spring support seat and spring are installed on the rear side of the sliding bearing seat. When material squeezes the driven roller, the sliding bearing seat can slide backward and be reset by the spring buffer, avoiding tooth breakage or motor stalling due to overload. The difference in the number of teeth between the driving roller's pinion and the driven roller's gear drives the dual-roll differential speed rotation. Combined with the short, thick, cylindrical roller teeth intersecting on the roller surfaces, this creates a high-intensity shearing and squeezing effect, improving crushing efficiency and reducing particle size. The housing is fixed to the support frame with bolts, and the feed inlet and discharge outlet are tightly connected to the housing, resulting in a stable and reliable overall structure that solves the problem of component damage caused by vibration or impact in traditional equipment.

[0018] Other advantages, objectives and features of this invention will be set forth in part in the description which follows, and in part will be apparent to those skilled in the art from the following examination or study, or may be taught from the practice of this invention. Attached Figure Description

[0019] Figure 1 This is a front view of a double-roll crusher according to the present invention;

[0020] Figure 2 This is a side view of a double-roll crusher according to the present invention;

[0021] Figure 3 This is a top view of a double-roll crusher according to the present invention.

[0022] As shown in the figure:

[0023] 1. Feed inlet; 2. Housing; 3. Discharge outlet; 4. Support frame; 5. Motor reducer; 6. Small gear of the drive roller; 7. Large gear of the driven roller; 8. Motor gear; 9. Spring support seat; 10. Spring; 11. Sliding bearing seat; 12. Fixed bearing seat; 13. Drive roller; 14. Driven roller. Detailed Implementation

[0024] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0025] It should be noted that the terms "vertical," "horizontal," "up," "down," "left," "right," and similar expressions used in this article are for illustrative purposes only and do not represent the only possible implementation.

[0026] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains; the terminology used herein in the description of this invention is for the purpose of describing particular embodiments only and is not intended to limit the invention; the term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0027] like Figure 1 and Figure 2As shown, a double-roll crusher includes: a feed inlet 1, a shell 2, a discharge outlet 3, a support frame 4, a motor reducer 5, a driving roller pinion 6, a driven roller gear 7, a motor gear 8, a spring support seat 9, a spring 10, a sliding bearing seat 11, a fixed bearing seat 12, a driving roller 13, and a driven roller 14; the driving roller 13 and the driven roller 14 have short, thick cylindrical roller teeth evenly distributed and welded on their roller surfaces, and the roller teeth of the two rollers are arranged crosswise; the driving roller 13 is fixed to the shell 2 by the fixed bearing seat 12, and the driven roller 14 is fixed to the shell 2 by the sliding bearing seat 11. Inside, a spring support seat 9 is provided on the rear side of the sliding bearing seat 11. One end of the spring 10 is connected to the spring support seat 9, and the other end is connected to the sliding bearing seat 11. The output end of the motor reducer 5 is connected to the motor gear 8. The driving roller pinion 6 is installed at the end of the driving roller 13, and the driven roller gear 7 is installed at the end of the driven roller 14. The motor gear 8 meshes with the driving roller pinion 6 and the driven roller gear 7 respectively, and drives the driving roller 13 to rotate at a higher speed than the driven roller 14 through the difference in the number of teeth. The housing 2 is fixed to the support frame 4 by bolts, and the feed port 1 and the discharge port 3 are respectively connected to the housing 2.

[0028] In this embodiment, the active roller 13 is rigidly fixed to the housing 2 by a fixed bearing seat 12 to ensure the stability of the active roller during high-speed rotation; the passive roller 14 is connected to the housing 2 by a sliding bearing seat 11, and the rear side of the sliding bearing seat 11 is elastically connected to the spring support seat 9 by a spring 10. When material enters the gap between the two rollers, the passive roller 14 can slide backward with the sliding bearing seat 11 to increase the roller gap. After being compressed, the spring 10 returns to its original position through elastic reset, avoiding roller tooth breakage or motor overload caused by hard compression; the motor reducer 5. The motor gear 8 simultaneously drives the driving roller pinion 6 and the driven roller gear 7. Taking advantage of the difference in the number of teeth of the driving roller pinion 6 compared to the driven roller gear 7, the driving roller 13 rotates at a higher speed than the driven roller 14, forming a differential rotation between the two rollers. The short, thick cylindrical roller teeth, which are distributed in a cross pattern, exert a dual effect of shearing and crushing on the material under differential speed, which greatly improves the crushing efficiency and particle uniformity. The shell 2 is fixed to the support frame 4 by bolts. The feed port 1 and the discharge port 3 are seamlessly connected to the shell 2, which enhances the overall structural rigidity and reduces component wear caused by vibration.

[0029] Based on the above embodiments, the innovation and beneficial effects of this utility model are as follows:

[0030] Differential drive and roller tooth design: The combination of differential rotation of the two rollers and the cross roller tooth layout significantly improves crushing efficiency and reduces the size of finished particles, solving the problem of uneven particle size in traditional single-roller crushing.

[0031] Spring buffer protection mechanism: The elastic connection design between the sliding bearing seat 11 and the spring 10 can dynamically adjust the roller spacing and absorb impact energy, effectively preventing tooth breakage, jamming and motor stalling.

[0032] Structural stability optimization: The bolt fixing method between the shell 2 and the support frame 4, as well as the compact meshing layout of the gear set, enhance the overall rigidity of the equipment, reduce operating vibration, and extend service life.

[0033] Energy saving and reliability: Differential drive reduces the instantaneous load on the motor, and spring buffer reduces the risk of overload. The two work together to optimize energy consumption and ensure stable equipment operation, meeting the needs of high-load continuous production.

[0034] like Figure 2 and Figure 3 As shown, the number of teeth of the active roller pinion 6 and the passive roller gear 7 are different to achieve differential rotation; the sliding bearing seat 11 cooperates with the spring 10 to allow the passive roller 14 to slide when squeezed and be reset by the spring; the roller teeth of the active roller 13 and the passive roller 14 intersect to form a crushing area; the spring support seat 9 is fixed to the support frame 4 by welding or bolts.

[0035] In this embodiment, the tooth ratio of the small gear of the active roller to the large gear of the passive roller is 1:2. This difference in tooth count allows the active roller to rotate at twice the speed of the passive roller, creating a differential shearing and crushing effect. The sliding bearing seat and spring are fitted together. The spring is made of 65Mn spring steel with a free length L = 200mm and a stiffness coefficient k = 50N / mm. When the material extrusion pressure exceeds a preset threshold, the sliding bearing seat can slide backward by a displacement Δ = 10-20mm and return to its original position through the elasticity of the spring. The roller teeth of the active and passive rollers are cylindrical with a diameter D = 20mm, a height H = 30mm, a tooth spacing S = 10mm, and a tooth intersection angle θ = 45°, forming a uniformly distributed extrusion and crushing area, effectively improving the uniformity of material crushing. The spring support seat is fixed to the support frame by welding or M12 high-strength bolts, ensuring the stability and impact resistance of the buffer system.

[0036] Detailed breakdown of key implementation points:

[0037] Gear parameters:

[0038] Drive roller pinion: module M=5, number of teeth Z1=20, material 42CrMo, surface carburized and quenched to a hardness of HRC58-62.

[0039] Passive roller gear: module M=5, number of teeth Z2=40, material and processing are the same as the driving gear, the difference in number of teeth drives the differential speed ratio of 2:1.

[0040] Spring parameters:

[0041] Material: 65Mn spring steel, tensile strength ≥980MPa.

[0042] Stiffness coefficient k = 50 N / mm, compression stroke Δ = 20 mm, maximum bearing pressure F_max = 15 kN.

[0043] Roller tooth parameters:

[0044] Diameter D = 20mm ± 0.1mm, height H = 30mm ± 0.2mm, spacing S = 10mm ± 0.1mm.

[0045] The cross angle θ = 45° ± 2°, and the roller tooth surface is overlaid with a wear-resistant layer.

[0046] Connection parameters:

[0047] Spring support seat welding: weld height ≥ 5mm, conforming to ISO 5817-B grade weld quality.

[0048] Bolted connection: M12×1.75, strength grade 8.8, preload torque T=90N·m.

[0049] Innovative implementation results:

[0050] Differential gear set: The two rollers are differentially driven by a gear ratio of 2:1. The speed difference increases the shearing force and improves the crushing efficiency by more than 30%.

[0051] Elastic buffer system: The spring stiffness and stroke are optimized to absorb peak impact force ≥15kN, reducing the tooth breakage failure rate by 80%.

[0052] Crossed roller tooth layout: The 45° cross angle causes the material to be subjected to multi-directional extrusion, increasing the proportion of finished particles with a size ≤5mm to 95%.

[0053] High-reliability connection: The spring support is fixed in both welding and bolt modes, which enhances vibration resistance and extends equipment life to more than 10,000 hours.

[0054] The operating steps of this double roll crusher are as follows: First, check the connection status of each component of the equipment to ensure that the cross angle of the roller teeth of the active roller and the passive roller is 45°, the gear set is properly meshed, and the spring is at its free length. After starting the motor and reducer, the material is evenly fed into the housing from the feed inlet. The motor gear drives the small gear of the active roller and the large gear of the passive roller to rotate at different speeds. The roller teeth of the two rollers shear and crush the material. If a large hard object gets stuck during operation, the passive roller slides backward through the sliding bearing seat to compress the spring, increasing the roller gap to buffer the impact force. After the spring returns to its original position, the roller gap automatically recovers. After the crushed material is discharged through the discharge outlet, turn off the motor and reducer and clean up any residual material. Regularly check the wear of the roller teeth, the meshing status of the gears, and the stiffness of the springs to ensure long-term stable operation of the equipment.

[0055] Although the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the present invention. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention should be determined by the claims.

Claims

1. A pair of opposed rolls for a roll crusher, characterized in that, include: Feed inlet (1), housing (2), discharge outlet (3), support frame (4), motor reducer (5), drive roller pinion (6), driven roller gear (7), motor gear (8), spring support seat (9), spring (10), sliding bearing seat (11), fixed bearing seat (12), drive roller (13) and driven roller (14); The active roller (13) and the passive roller (14) have multiple sets of cylindrical roller teeth evenly welded on their roller surfaces, and the roller teeth of the two rollers are arranged in an intersecting manner. The active roller (13) is fixed inside the housing (2) by a fixed bearing seat (12), and the passive roller (14) is fixed inside the housing (2) by a sliding bearing seat (11); The sliding bearing seat (11) is provided with a spring support seat (9) on its rear side. One end of the spring (10) is connected to the spring support seat (9), and the other end is connected to the sliding bearing seat (11). The output end of the motor reducer (5) is connected to the motor gear (8), the driving roller pinion (6) is installed at the end of the driving roller (13), and the passive roller gear (7) is installed at the end of the passive roller (14). The motor gear (8) meshes with the small gear (6) of the active roller and the large gear (7) of the passive roller respectively, so that the rotational speed of the active roller (13) is greater than that of the passive roller (14); The housing (2) is fixed to the support frame (4) by bolts, and the inlet (1) and outlet (3) are respectively connected to the housing (2).

2. A pair of crushing rolls according to claim 1, characterized in that: The number of teeth of the driving roller pinion (6) and the passive roller gear (7) are different to achieve differential rotation of the driving roller (13) and the passive roller (14).

3. A pair of crushing rolls according to claim 1, characterized in that: The cooperation structure between the sliding bearing seat (11) and the spring (10) allows the passive roller (14) to slide backward when squeezed by the material and be reset by the elasticity of the spring (10).

4. A pair of crushing rolls according to claim 1, characterized in that: The active roller (13) and passive roller (14) have short and thick cylindrical teeth, and the teeth of the two rollers are distributed in an intersecting manner to form a crushing and extrusion zone.

5. A pair of crushing rolls as claimed in claim 1 wherein: The spring support seat (9) is fixed to the support frame (4) by welding or bolting.

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