Double-geared roller crusher with retaining function

Abstract

The utility model belongs to the technical field of crushers, and particularly relates to a double-geared roller crusher with a retaining function, which comprises a frame, an upper casing arranged above the frame, a fixed bearing seat and a movable bearing seat, the fixed bearing seat and the movable bearing seat are positioned between the frame and the upper casing, and a first hydraulic cylinder is arranged between the fixed bearing seat and the movable bearing seat. A piston rod of the first hydraulic cylinder is in contact with the movable bearing seat and is used for driving the movable bearing seat to move; a second hydraulic cylinder is arranged on the side, away from the fixed bearing seat, of the movable bearing seat, and a piston rod of the second hydraulic cylinder is indirectly connected with the movable bearing seat through an elastic assembly. Through a dual-control structure that the first hydraulic cylinder drives the movable bearing seat to move and the second hydraulic cylinder provides continuous reverse thrust through the elastic assembly, when hard materials cause the movable crushing roller to retreat, the elastic assembly can quickly push the movable bearing seat to reset to maintain a crushing gap, meanwhile, it can be guaranteed that the hard materials or ironware can smoothly fall off, and the service life of the movable crushing roller is prolonged. And material blockage is avoided, and the two crushing rollers are protected from being damaged.

Description

Technical Field

[0001] The utility model belongs to the technical field of crushers, in particular to a double-toothed roller crusher with a back-stop function. Background Art

[0002] Double-toothed roller crushers are widely used in mining, metallurgy, building materials, and other fields for medium and fine crushing. Their core crushing function relies on the shearing and squeezing action of two counter-rotating toothed rollers. Traditional double-toothed roller crushers typically rely on mechanical adjustment mechanisms (such as adding or removing gaskets or shifting bolts). This method suffers from cumbersome operation, low adjustment accuracy, and an inability to dynamically adapt to changing material properties. Especially when processing materials of varying hardness or particle size, a fixed center distance can lead to reduced crushing efficiency, increased roller tooth wear, and even equipment overload failure.

[0003] The prior art also has a structural form that uses a fixed bearing seat and a movable bearing seat, and adjusts the distance between the two crushing rollers through a hydraulic cylinder to adapt to the requirements of different material particle sizes, but there are still the following defects: when the double-toothed roller crusher is crushing medium and high hardness materials, the equipment often malfunctions due to the mixing of hard impurities (such as iron, super-hard ores) that are difficult to crush in the materials or instantaneous overload. Although limited retreat can be achieved by driving the movable roller by a single hydraulic cylinder, when hard materials or foreign matter enter the crushing chamber, the movable roller can retreat briefly, but lacks an effective anti-retreat function, resulting in the inability to quickly reset after retreat, causing fluctuations in crushing efficiency and inability to adapt to the crushing of the current material; in addition, the sliding fit structure between the movable bearing seat and the frame often becomes stuck due to dust intrusion or unbalanced load, which makes the movement accuracy of the movable roller low, affecting the stability of equipment operation.

[0004] Therefore, there is an urgent need to develop a double-toothed roller crusher with both reliable anti-retraction function and high stability adjustment to solve the key technical bottlenecks in the existing technology. Utility Model Content

[0005] In order to solve the problems in the above-mentioned background technology, the utility model provides a double-toothed roller crusher with a back-stop function, which takes into account both active adjustment and passive protection functions through the division of labor and cooperation of dual hydraulic cylinders, thereby improving the adaptability of the equipment to different working conditions.

[0006] The utility model adopts the following technical solutions:

[0007] A double-toothed roller crusher with a back-stop function comprises a frame, an upper casing arranged above the frame, and a fixed bearing seat and a movable bearing seat located between the frame and the upper casing. Fixed crushing rollers are mounted on two oppositely arranged fixed bearing seats, and movable crushing rollers are mounted on two oppositely arranged movable bearing seats, wherein:

[0008] A first hydraulic cylinder is provided between the fixed bearing seat and the movable bearing seat, and a piston rod of the first hydraulic cylinder is provided in contact with the movable bearing seat for driving the movable bearing seat to move;

[0009] A second hydraulic cylinder is provided on a side of the movable bearing seat facing away from the fixed bearing seat, and a piston rod of the second hydraulic cylinder is indirectly connected to the movable bearing seat through an elastic component.

[0010] Furthermore, the elastic component includes a spring mounting plate and at least two springs. The piston rod of the second hydraulic cylinder is arranged in contact with the spring mounting plate. One end of the spring is fixedly connected to the spring mounting plate, and the other end of the spring abuts against the movable bearing seat. The thrust of the spring on the movable bearing seat is greater than the crushing force required for the material.

[0011] Furthermore, at least two springs are evenly arranged on one side of the movable bearing seat.

[0012] Furthermore, the movable bearing seat is a rectangular structure, and the upper surface and lower surface of the movable bearing seat are both provided with slide grooves, and the lower surface of the upper shell and the upper surface of the frame are both fixed with rails that are compatible with the slide grooves.

[0013] Furthermore, a first hydraulic cylinder bracket is fixed between the fixed bearing seat and the movable bearing seat, and the first hydraulic cylinder is installed on the first hydraulic cylinder bracket; a second hydraulic cylinder bracket is fixed on the side of the movable bearing seat away from the fixed bearing seat, and the second hydraulic cylinder is installed on the second hydraulic cylinder bracket.

[0014] Furthermore, a fixed bracket is fixed to the outer side of the fixed bearing seat, and the first hydraulic cylinder bracket and the fixed bracket clamp and fix the crushing roller.

[0015] Furthermore, a circular hole for installing a fixed crushing roller is formed between the fixed bracket and the first hydraulic cylinder bracket, and a long strip hole for installing a movable crushing roller is formed between the first hydraulic cylinder bracket and the second hydraulic cylinder bracket. The movable crushing roller moves along the long strip hole under the action of the first hydraulic cylinder and the second hydraulic cylinder.

[0016] Furthermore, the upper casing and the frame are connected to the first hydraulic cylinder bracket, the second hydraulic cylinder bracket and the fixed bracket through a bolt group.

[0017] Furthermore, it also includes a first drive assembly for driving the fixed crushing roller to rotate, and a second drive assembly for driving the movable crushing roller to rotate;

[0018] The first drive assembly and the second drive assembly both include a motor, a hydraulic coupling and a reducer which are sequentially connected in transmission. The reducer of the first drive assembly is connected to the fixed crushing roller through a coupling, and the reducer of the second drive assembly is connected to the mobile crushing roller through a universal coupling.

[0019] Furthermore, the mobile crushing roller moves toward or away from the fixed crushing roller, which can drive the universal coupling to deviate relative to the second driving assembly.

[0020] Compared with the prior art, the beneficial effects of the present invention are:

[0021] The present application provides a double-toothed roller crusher with an anti-retraction function. By setting a dual control structure in which a first hydraulic cylinder drives the movable bearing seat to move and a second hydraulic cylinder provides continuous reverse thrust through an elastic component, when hard materials cause the movable crushing roller to retreat, the elastic component can quickly push the movable bearing seat to reset and maintain the crushing gap. At the same time, combined with the precise guidance of the chute and the track and the adaptive offset of the universal coupling, it has the advantages of preventing the crushing roller from being unable to reset after abnormal retreat and improving the operating stability of the equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0023] Figure 1 A front view of a double-toothed roller crusher provided in one embodiment of the present application;

[0024] Figure 2 A top view of a double-toothed roller crusher provided in one embodiment of the present application;

[0025] Figure 3 This is a left side view of a double-toothed roller crusher provided in one embodiment of the present application;

[0026] Figure 4 for Figure 2 AA view in;

[0027] Figure 5 An angled view of a universal coupling provided in one embodiment of the present application;

[0028] Figure 6 for Figure 2 BB view in;

[0029] Figure 7 A structural diagram of a movable bearing seat provided in one embodiment of the present application;

[0030] Among them: 1-frame, 2-upper casing, 201-track, 3-fixed bearing seat, 4-movable bearing seat, 401-chute, 5-fixed crushing roller, 6-movable crushing roller, 7-first hydraulic cylinder, 8-second hydraulic cylinder, 9-elastic component, 901-spring mounting plate, 902-spring, 10-first hydraulic cylinder bracket, 11-second hydraulic cylinder bracket, 12-fixed bracket, 13-round hole, 14-long hole, 15-motor, 16-hydraulic coupling, 17-reducer, 18-coupling, 19-universal coupling. DETAILED DESCRIPTION

[0031] The following is a clear and complete description of the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0032] The following is combined with Figure 1 To the attached Figure 7 And specific embodiments discuss the present invention in detail.

[0033] like Figures 1 to 7 As shown, the utility model provides a double-toothed roller crusher with a back-stop function, comprising a frame 1, an upper casing 2 arranged above the frame 1, and a fixed bearing seat 3 and a movable bearing seat 4 located between the frame 1 and the upper casing 2, two oppositely arranged fixed bearing seats 3 are equipped with fixed crushing rollers 5, and two oppositely arranged movable bearing seats 4 are equipped with movable crushing rollers 6, wherein: a first hydraulic cylinder 7 is arranged between the fixed bearing seat 3 and the movable bearing seat 4, the piston rod of the first hydraulic cylinder 7 is arranged in contact with the movable bearing seat 4, and is used to drive the movable bearing seat 4 to move; a second hydraulic cylinder 8 is arranged on the side of the movable bearing seat 4 away from the fixed bearing seat 3, and the piston rod of the second hydraulic cylinder 8 is indirectly connected to the movable bearing seat 4 through an elastic component 9. In the above technical solution, the first hydraulic cylinder 7 is a linear drive device arranged between the fixed bearing seat 3 and the movable bearing seat 4. It can be implemented by a single-acting or double-acting hydraulic cylinder and is used to actively adjust the distance between the two crushing rollers to adapt to material requirements. The second hydraulic cylinder 8 is an auxiliary drive device arranged outside the movable bearing seat 4. It can be implemented by a double-acting hydraulic cylinder in combination with an elastic component and is used to provide a reverse buffering force under abnormal loads. The elastic component 9 is an energy storage structure that absorbs energy through spring deformation and releases deformation recovery force after the load disappears. It should be noted that the piston rod of the first hydraulic cylinder 7 in this application is in contact with the movable bearing seat 4 but is not fixedly connected. The piston rod of the second hydraulic cylinder 8 is indirectly connected to the movable bearing seat 4, that is, the indirect connection between the two is achieved through the elastic component 9 located in the middle.

[0034] The first hydraulic cylinder 7 directly pushes the movable bearing seat 4 through the extension and contraction of the piston rod, so that the mobile crushing roller 6 moves closer to or away from the fixed crushing roller 5, realizing the roller spacing adjustment under normal working conditions. When hard foreign matter enters the crushing chamber and causes a sudden increase in load, the abnormal crushing force is transmitted to the movable bearing seat 4 through the mobile crushing roller 6. At this time, the elastic component 9 of the second hydraulic cylinder 8 is compressed and contracted, allowing the movable bearing seat 4 to retreat outward to avoid the foreign matter. When the foreign matter is discharged, the elastic component 9 releases the stored elastic potential energy and pushes the movable bearing seat 4 in the opposite direction to return to its original working position; to put it more bluntly, once hard material or iron enters the crushing chamber, the spring 902 will continue to be compressed to increase the center distance between the fixed crushing roller 5 and the mobile crushing roller 6, ensuring that the hard material or iron can fall smoothly, without blocking the material and protecting the two crushing rollers from damage. Compared with the traditional single hydraulic cylinder solution that can only rely on system pressure for passive reset after retreat, with slow response speed and low reset accuracy, the present application forms an active reset mechanism through the second hydraulic cylinder 8 and the elastic component 9, which immediately triggers the elastic force to drive the reset after retreat, shortening the recovery time and avoiding equipment shutdown caused by foreign object obstruction; through the division of labor and cooperation of the two hydraulic cylinders, active adjustment and passive protection functions are taken into account, thereby improving the adaptability of the equipment to different working conditions.

[0035] Specifically, the elastic assembly 9 includes a spring mounting plate 901 and at least two springs 902. The piston rod of the second hydraulic cylinder 8 is connected to the spring mounting plate 901. One end of the spring 902 is fixedly connected to the spring mounting plate 901, and the other end of the spring 902 is connected to the movable bearing seat 4. The thrust exerted by the spring 902 on the movable bearing seat 4 is greater than the required crushing force of the material. In the above technical solution, the spring mounting plate 901 serves as an intermediate carrier connecting the second hydraulic cylinder 8 and the springs 902, capable of converting the hydraulic driving force into a uniformly distributed elastic thrust. The at least two springs 902 are arranged in parallel to form a redundant structure. If one spring fails, the remaining springs can still maintain system functionality, preventing a sudden drop in thrust from causing an abnormal resetting of the movable bearing seat 4. Preferably, the springs 902 in this application can be coil springs or disc springs, but are not limited thereto. Specifically, when the piston rod of the second hydraulic cylinder 8 extends, it pushes the spring mounting plate 901 toward the movable bearing seat 4. At this time, the springs 902 are in a compressed state and accumulate elastic potential energy. When a hard foreign object is encountered during the crushing process, causing the movable bearing seat 4 to retreat, the compression of spring 902 increases, generating a corresponding increase in the reverse thrust. Because the total thrust of spring 902 is always greater than the material's crushing force, the movable bearing seat 4 immediately returns to its initial position due to the spring's rebound force after the foreign object passes through the gap between the crushing rollers. Multiple springs 902 are evenly distributed along the sides of the movable bearing seat 4, ensuring unbiased thrust transmission and preventing tilting and jamming of the movable bearing seat 4 during movement.

[0036] This application achieves instantaneous automatic repositioning of the movable bearing seat 4 after yielding, eliminating the fluctuations in crushing efficiency caused by pressure regulation delays in traditional hydraulic drives. The multi-spring structure of the elastic assembly 9 ensures uniform and continuous thrust distribution. Even in the event of partial failure of spring 902, effective thrust is maintained, preventing the movable bearing seat 4 from shifting due to insufficient thrust. The matching design of spring thrust and crushing force enables the device to adapt to instantaneous overload yielding while quickly restoring the set crushing gap, ensuring the stability of the crushing process.

[0037] Specifically, at least two springs 902 are evenly arranged on one side of the movable bearing seat 4. In other words, the uniform arrangement of the springs 902 can be achieved by adopting a layout method of symmetrical installation along the axial center line of the movable bearing seat 4. For example, two springs 902 are respectively arranged at the two end positions of the side of the movable bearing seat 4, or four springs 902 are distributed on the side of the movable bearing seat 4 in a rectangular array. Through the symmetrical arrangement of the springs 902, the thrust vectors generated by each spring 902 form a balanced force system, avoiding the generation of torque by the movable bearing seat 4 during the movement. When the movable bearing seat 4 is subjected to the thrust of the second hydraulic cylinder 8, the evenly distributed springs 902 simultaneously generate a reverse force, and the compression deformation of each spring 902 remains synchronized. When encountering a hard foreign object that causes the movable bearing seat 4 to move backward, the symmetrically arranged springs 902 transmit the reaction force to the piston rod of the second hydraulic cylinder 8 by being evenly compressed, so that the movable bearing seat 4 always moves in parallel.

[0038] Specifically, in this embodiment, the movable bearing seat 4 is a rectangular structure, with slide grooves 401 provided on both its upper and lower surfaces. A track 201, compatible with the slide grooves 401, is fixed to the lower surface of the upper housing 2 and the upper surface of the frame 1. The slide groove 401 is a groove structure formed on the surface of the movable bearing seat 4 along the direction of movement. Specifically, it can be implemented as a T-slot or dovetail groove. The inner wall of the groove is finely machined to reduce the coefficient of sliding friction. The track 201 is a raised structure with a complementary shape to the slide groove 401. Specifically, it can be fixed to the frame 1 and the upper housing 2 by welding or countersunk screws. The extension direction of the track 201 coincides with the direction of movement of the movable crushing roller 6. The surface of the track 201 can be provided with a self-lubricating coating to reduce sliding resistance.

[0039] Specifically, the movable bearing seat 4 forms a dual guide pair with the frame 1 and the rail 201 on the upper housing 2, respectively, through the slide grooves 401 provided on its upper and lower surfaces. The symmetry of the rectangular structure ensures uniform stress distribution when the movable bearing seat 4 is subjected to crushing loads, preventing uneven wear on the sliding surface caused by unilateral deformation. The contact between the slide grooves 401 and the rail 201 ensures free linear movement while preventing external dust from entering the sliding gap through the sealing effect of the bilateral contact surfaces.

[0040] Specifically, a first hydraulic cylinder bracket 10 is fixed between the fixed bearing seat 3 and the movable bearing seat 4, and the first hydraulic cylinder 7 is installed on the first hydraulic cylinder bracket 10; a second hydraulic cylinder bracket 11 is fixed on the side of the movable bearing seat 4 away from the fixed bearing seat 3, and the second hydraulic cylinder 8 is installed on the second hydraulic cylinder bracket 11.

[0041] Specifically, the first hydraulic cylinder support 10 is fixed in the gap between the fixed bearing seat 3 and the movable bearing seat 4, forming a rigid constraint on the first hydraulic cylinder 7. When the first hydraulic cylinder 7 drives the movable bearing seat 4 to move, the reaction force is dispersed to the fixed bearing seat 3 and the frame 1 through the first hydraulic cylinder support 10, avoiding local stress deformation of the movable bearing seat 4. The second hydraulic cylinder support 11 is independently arranged on the outside of the movable bearing seat 4 and has no direct connection with the movable bearing seat 4, ensuring that the installation position of the second hydraulic cylinder 8 is not affected by the displacement of the movable parts. When the second hydraulic cylinder 8 pushes the movable bearing seat 4 through the elastic component 9, the second hydraulic cylinder support 11 acts as a fixed fulcrum, so that the hydraulic thrust is evenly transmitted to the movable bearing seat 4 through the spring 902.

[0042] Specifically, a fixed bracket 12 is fixed to the outside of the fixed bearing seat 3. The first hydraulic cylinder bracket 10 and the fixed bracket 12 clamp the fixed crushing roller 5. The first hydraulic cylinder bracket 10 and the fixed bracket 12 form a bidirectional constraint on the axial end of the fixed crushing roller 5. Specifically, this can be achieved by using a clamping plate with a semicircular groove to cooperate with the shaft neck of the fixed crushing roller 5. Specifically, the fixed bracket 12 is welded to the outside of the fixed bearing seat 3, so that it and the first hydraulic cylinder bracket 10 form a support structure symmetrically distributed on both sides of the fixed crushing roller 5, ensuring that the fixed crushing roller 5 does not move during operation.

[0043] Specifically, a circular hole 13 for mounting the fixed crushing roller 5 is formed between the fixed bracket 12 and the first hydraulic cylinder bracket 10. A strip hole 14 for mounting the movable crushing roller 6 is formed between the first hydraulic cylinder bracket 10 and the second hydraulic cylinder bracket 11. The movable crushing roller 6 moves along the strip hole 14 under the action of the first hydraulic cylinder 7 and the second hydraulic cylinder 8. The circular hole 13 serves as the mounting hole for the fixed crushing roller 5, and its inner wall forms an interference fit with the shaft neck of the fixed crushing roller 5. The strip hole 14 serves as a guide hole for the movable crushing roller 6, and its length is parallel to the movement path of the movable bearing seat 4. Specifically, the roller shaft of the fixed crushing roller 5 is constrained in the circular hole 13 formed by the fixed bracket 12 and the first hydraulic cylinder bracket 10. The interference fit between the inner diameter of the circular hole 13 and the shaft neck of the fixed crushing roller 5 creates a radially rigid constraint, eliminating radial movement caused by shear force fluctuations during the crushing operation. The roller shaft of the mobile crushing roller 6 is placed in the elongated hole 14 formed by the first hydraulic cylinder bracket 10 and the second hydraulic cylinder bracket 11, so that the roller shaft of the mobile crushing roller 6 can only move linearly along the length of the elongated hole 14. The piston rod ends of the first hydraulic cylinder 7 and the second hydraulic cylinder 8 are respectively connected to the two sides of the movable bearing seat 4. The extension and contraction of the first hydraulic cylinder 7 and the second hydraulic cylinder 8 are synchronously controlled by the hydraulic station, driving the mobile crushing roller 6 to move within the movement path defined by the elongated hole 14.

[0044] Specifically, the upper housing 2 and frame 1 are connected to the first hydraulic cylinder support 10, the second hydraulic cylinder support 11, and the fixed support 12 via a bolt group. A bolt group refers to a connection unit composed of multiple bolts, specifically high-strength alloy steel bolts and lock washers. Its function is to achieve rigid fixation and sealing between multiple components. The upper housing 2 and frame 1 of the present application are rigidly connected to the first hydraulic cylinder support 10, the second hydraulic cylinder support 11, and the fixed support 12 via bolt groups, forming a frame structure that connects the entire device into a whole and ensures the stability of the device.

[0045] Specifically, it also includes a first drive assembly for driving the fixed crushing roller 5 to rotate, and a second drive assembly for driving the mobile crushing roller 6 to rotate; the first drive assembly and the second drive assembly both include a motor 15, a hydraulic coupling 16 and a reducer 17 that are sequentially connected in transmission. The reducer 17 of the first drive assembly is connected to the fixed crushing roller 5 through a coupling 18. The coupling 18 can be a pin coupling or a drum gear coupling, but is not limited to this. The reducer 17 of the second drive assembly is connected to the mobile crushing roller 6 through a universal coupling 19.

[0046] Specifically, the fixed crushing roller 5 is driven by the first drive assembly. The power output of the motor 15 is transmitted to the reducer 17 via the hydraulic coupling 16. This power is then fixedly connected to the fixed crushing roller 5 via the coupling 18, achieving a stable output speed. The mobile crushing roller 6 is independently controlled by the second drive assembly. The output end of the reducer 17 is connected to the mobile crushing roller 6 via the universal coupling 19. When the mobile crushing roller 6 is displaced by the hydraulic cylinder, the articulated structure of the universal coupling 19 adapts to axis deviation, eliminating the need to adjust the position of the second drive assembly separately during the roller gap adjustment process. The independent operation of the first and second drive assemblies allows the speed and torque of the fixed crushing roller 5 and the mobile crushing roller 6 to be adjusted separately based on the material characteristics.

[0047] Furthermore, when the mobile crushing roller 6 moves toward or away from the fixed crushing roller 5, it can drive the universal coupling 19 to deflect relative to the second drive assembly. It can be seen that the universal coupling 19 refers to a transmission connection component with a multi-directional angle compensation function, which can be implemented by a cross-axis or ball cage structure, allowing angular offset and axial displacement between the input shaft and the output shaft through the hinge node. This feature compensates for the deviation of the transmission axis during the movement of the mobile crushing roller 6 and avoids stress concentration caused by rigid connection. Specifically, when the mobile crushing roller 6 is driven by the first hydraulic cylinder 7 to make a linear displacement along the track 201, its rotating shaft is connected to the output end of the reducer 17 of the second drive assembly through the universal coupling 19. When the mobile crushing roller 6 approaches or moves away from the fixed crushing roller 5, the cross-axis or ball joint structure of the universal coupling 19 undergoes angular deflection to absorb the axis offset caused by the movement of the mobile crushing roller 6. The transmission torque is transmitted to the mobile crushing roller 6 through the hinged parts of the universal coupling 19. At the same time, the movable parts inside the universal coupling 19 adaptively adjust the angle under the elastic elements or clearance fit. This feature enables the transmission system to maintain the continuity of power transmission during dynamic adjustment and eliminates the rigid constraints of position changes on the second drive component.

[0048] This application addresses the problem of transmission instability caused by the rigid connection of the second drive assembly during dynamic adjustment of the mobile crushing roller 6. By utilizing the angular offset function of the universal joint 19, flexible adaptation of the transmission system and the moving components is achieved. During the continuous adjustment of the position of the mobile crushing roller 6, this structure automatically compensates for axis deviation, ensuring efficient transmission of drive torque while eliminating the vibration and stress concentration caused by traditional rigid connection methods. This significantly improves the operational reliability of the equipment under dynamic adjustment conditions.

[0049] The above further describes the present invention with the help of specific embodiments, but it should be understood that the specific description here should not be construed as limiting the essence and scope of the present invention. Various modifications made to the above embodiments by ordinary technicians in this field after reading this specification are all within the scope of protection of the present invention.

Claims

1. A double-toothed roller crusher with a back-stop function, characterized in that: The crushing machine comprises a frame, an upper casing arranged above the frame, and a fixed bearing seat and a movable bearing seat located between the frame and the upper casing, wherein fixed crushing rollers are installed on two oppositely arranged fixed bearing seats, and movable crushing rollers are installed on two oppositely arranged movable bearing seats, wherein: A first hydraulic cylinder is provided between the fixed bearing seat and the movable bearing seat, and a piston rod of the first hydraulic cylinder is provided in contact with the movable bearing seat for driving the movable bearing seat to move; A second hydraulic cylinder is provided on a side of the movable bearing seat facing away from the fixed bearing seat, and a piston rod of the second hydraulic cylinder is indirectly connected to the movable bearing seat through an elastic component.

2. The double-toothed roller crusher with a back-stop function according to claim 1, characterized in that: The elastic component includes a spring mounting plate and at least two springs. The piston rod of the second hydraulic cylinder is arranged in contact with the spring mounting plate. One end of the spring is fixedly connected to the spring mounting plate, and the other end of the spring abuts against the movable bearing seat. The thrust of the spring on the movable bearing seat is greater than the crushing force required for the material.

3. The double-toothed roller crusher with a back-stop function according to claim 2, characterized in that: At least two of the springs are evenly arranged on one side of the movable bearing seat.

4. The double-toothed roller crusher with a back-stop function according to claim 1, characterized in that: The movable bearing seat is a rectangular structure, and the upper surface and the lower surface of the movable bearing seat are both provided with slide grooves, and the lower surface of the upper shell and the upper surface of the frame are both fixed with rails adapted to the slide grooves.

5. The double-toothed roller crusher with a back-stop function according to claim 1, characterized in that: A first hydraulic cylinder bracket is fixed between the fixed bearing seat and the movable bearing seat, and the first hydraulic cylinder is installed on the first hydraulic cylinder bracket; a second hydraulic cylinder bracket is fixed on the side of the movable bearing seat away from the fixed bearing seat, and the second hydraulic cylinder is installed on the second hydraulic cylinder bracket.

6. The double-toothed roller crusher with a back-stop function according to claim 5, characterized in that: A fixed bracket is fixed to the outer side of the fixed bearing seat, and the first hydraulic cylinder bracket and the fixed bracket clamp the fixed crushing roller.

7. The double-toothed roller crusher with a back-stop function according to claim 6, characterized in that: A circular hole for installing the fixed crushing roller is formed between the fixed bracket and the first hydraulic cylinder bracket, and a long hole for installing the movable crushing roller is formed between the first hydraulic cylinder bracket and the second hydraulic cylinder bracket. The movable crushing roller moves along the long hole under the action of the first hydraulic cylinder and the second hydraulic cylinder.

8. The double-toothed roller crusher with a back-stop function according to claim 6, characterized in that: The upper casing and the frame are connected to the first hydraulic cylinder support, the second hydraulic cylinder support and the fixed support through a bolt group.

9. The double-toothed roller crusher with a back-stop function according to claim 1, characterized in that: Also included is a first drive assembly for driving the fixed crushing roller to rotate, and a second drive assembly for driving the movable crushing roller to rotate; The first drive assembly and the second drive assembly both include a motor, a hydraulic coupling and a reducer that are sequentially connected in transmission. The reducer of the first drive assembly is connected to the fixed crushing roller through a coupling, and the reducer of the second drive assembly is connected to the movable crushing roller through a universal coupling.

10. The double-toothed roller crusher with a back-stop function according to claim 9, characterized in that: The movable crushing roller moves toward or away from the fixed crushing roller, thereby driving the universal coupling to deviate relative to the second driving assembly.

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