Anti-backlash device, anti-backlash control method and rolling equipment

Abstract

The invention relates to the field of rolling, and discloses an anti-backlash device, an anti-backlash control method and rolling equipment, the anti-backlash device comprises two bearing seats, a bearing set, a jacking structure and a hydraulic driving part, the two bearing seats are provided with mounting cavities in a penetrating mode in the first direction, one side face of each bearing seat is provided with a containing cavity, and the containing cavities communicate with the mounting cavities; the two ends, in the first direction, of the roller are each provided with a rotating shaft, the rotating shafts are located in the corresponding installation cavities, each installation cavity is internally provided with a bearing set, each bearing set comprises a third bearing, the jacking structure abuts against the third bearing, the hydraulic driving part is in transmission connection with the jacking structure, and the hydraulic driving part drives the jacking structure to abut against the third bearing. The hydraulic driving part drives the jacking structure to continuously and stably apply the pre-tightening force to the third bearing, a thread jackscrew structure which is prone to loosening and losing efficacy is replaced, the problem that the pre-tightening force is attenuated or lost due to vibration and loads is effectively solved, and therefore the anti-backlash effect can be reliably maintained for a long time.

Description

Cross-reference to related applications

[0001] This application claims priority to Chinese Patent Application No. 2025120339524, filed on December 30, 2025, entitled "A Gap Elimination Device, Gap Elimination Control Method and Roller Press Equipment", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of roller pressing, and more particularly to a gap elimination device, gap elimination control method and roller pressing equipment. Background Technology

[0003] In the field of precision mechanical transmission, especially in high-load, high-precision backlash elimination control methods, the presence of bearing clearance directly affects the spindle's rotational accuracy, transmission stiffness, and operational stability. Currently, common backlash elimination structures often employ a single-support main bearing coupled with an auxiliary backlash-eliminating bearing, using a threaded setter to apply preload to eliminate backlash. However, this structure reveals significant reliability issues in long-term operation: the threaded setter is prone to plastic deformation or thread loosening under continuous vibration and load, leading to a gradual attenuation or even loss of preload, making it difficult to maintain the backlash elimination effect. Furthermore, the single-support structure lacks sufficient rigidity under large or variable loads, further impacting the long-term operational accuracy and lifespan of the equipment. Summary of the Invention

[0004] In view of this, the purpose of this application is to overcome the shortcomings of the prior art and provide a gap elimination device, a gap elimination control method and a roller pressing equipment.

[0005] To achieve the above objectives, the technical solution adopted in this application is as follows: This application provides: A gap-eliminating device, having two perpendicular directions—a first direction, a second direction, and a third direction—comprising: The bearing housing has two mounting cavities extending through it along the first direction. One side of the bearing housing has a receiving cavity that communicates with the mounting cavity. A roller is disposed between the two bearing housings, and a rotating shaft is disposed at both ends of the roller along the first direction. The rotating shaft is located in the corresponding mounting cavity. Each of the mounting cavities is provided with a bearing assembly, which includes a first bearing, a second bearing, and a third bearing arranged sequentially in the mounting cavity along the first direction. The first bearing and the second bearing are offset relative to the first bearing, and the first bearing, the second bearing, and the third bearing are all sleeved on the rotating shaft. A top-pressure structure is provided in each of the accommodating cavities, and the top-pressure structure abuts against the third bearing; A hydraulic drive unit is connected to the top pressure structure for transmission, and the hydraulic drive unit drives the top pressure structure to abut against the third bearing.

[0006] Furthermore, the top-pressing structure includes a top-pressing member and a cover plate. The top-pressing member is slidably disposed in the accommodating cavity along the second direction. The top-pressing member is sealed to the side wall of the accommodating cavity. The end of the accommodating cavity away from the mounting cavity along the second direction is provided with a cover plate. The cover plate covers the accommodating cavity. The top-pressing member and the cover plate define an oil cavity.

[0007] Furthermore, the inner and outer radii of the first and second bearings are the same, and the offsets of the first and second bearings relative to the shaft are the same. The oil pressure output by the hydraulic drive component satisfies the following:

[0008] Where: Fz is the rolling force acting on the roll, θ is the rolling force angle, T is the torque when the roll is working, Rr is the radius of the roll, a is the offset of the first and second bearings relative to the rotating shaft, P is the oil pressure output by the hydraulic drive, R is the outer ring radius of the first and third bearings, and r is the inner ring radius of the first and second bearings.

[0009] Furthermore, a pressure monitor is provided on the hydraulic drive component, which is used to monitor the oil pressure delivered to the oil chamber.

[0010] Furthermore, the cover plate has an oil inlet hole extending through it along the second direction. The oil inlet hole is connected to the oil cavity, and the end of the oil inlet hole facing away from the top pressure member is connected to the hydraulic drive member.

[0011] Furthermore, the pressing member includes a driven part and a pressing part connected to each other, the driven part being sealed to the inner wall of the accommodating cavity, and the pressing part abutting against the third bearing.

[0012] Furthermore, the end of the top pressing portion that is away from the driven portion is an arc surface adapted to the circumferential surface of the third bearing.

[0013] Furthermore, the cross-sectional shape of the accommodating cavity and the top pressure member is circular or rectangular.

[0014] This application also provides a gap elimination control method for the gap elimination device described in any one of the above-mentioned methods, comprising: Obtain the radius Rr of the roll, the rolling force Fz, the rolling force angle θ, and the torque during operation; Obtain the offset a of the first bearing and the second bearing relative to the shaft, the outer ring radius R and the inner ring radius r, and the cross-sectional area A of the accommodating cavity; Substitute the above parameters into: The minimum oil pressure P delivered to the hydraulic oil in the top pressure structure is obtained; The oil pressure P1 delivered to the top pressure structure satisfies: P1≥P.

[0015] This application also provides a roller pressing device, comprising: The gap elimination device described in any one of the above statements; A rotary drive component, wherein the rotary drive component is connected to the rotating shaft via a transmission.

[0016] This application uses a hydraulically driven pressing structure to continuously and stably apply preload to the third bearing, replacing the easily loosened and failed threaded set screw structure. This effectively overcomes the problem of preload attenuation or loss caused by vibration and load, thus maintaining the backlash elimination effect reliably for a long time. At the same time, the triangular support structure formed by the first, second, and third bearings on the rotating shaft significantly enhances the rigidity and stability of the bearing housing and rolls when subjected to large or variable loads, thereby improving the long-term operating accuracy and service life of the rolling equipment.

[0017] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This paper shows a schematic diagram of the bearing housing, roll, pressing structure, and hydraulic drive components in their mating state. Figure 2 The diagram shows the bearing housing, first bearing, second bearing, third bearing, and top pressure structure under explosive conditions. Figure 3 A schematic diagram of the top pressure component structure of this application is shown; Figure 4 A side view of the bearing housing of this application is shown; Figure 5 A simplified schematic diagram of the first bearing, second bearing, third bearing, roll, and shaft in their mating state is shown in this application. Figure 6 A second simplified schematic diagram is shown showing the first bearing, second bearing, third bearing, roll, and rotating shaft in their mating state according to this application; Figure 7 The diagram shows the bearing housing, roll, shaft, and rotary drive component of this application in their assembled state. Figure 8 A schematic diagram of the gap elimination control method of this application is shown.

[0020] Explanation of key component symbols: 100-Bearing housing; 101-Mounting cavity; 102-Accommodation cavity; 200-Bearing assembly; 210-First bearing; 220-Second bearing; 230-Third bearing; 300-Top pressure structure; 301-Oil cavity; 310-Top pressure component; 311-Driven part; 312-Top pressure part; 3101-Arc surface; 320-Cover plate; 321-Oil inlet; 400-Roller; 410-Shaft; 500-Hydraulic drive component; 510-Pressure monitor; 600-Rotation drive component; Z-First direction; Y-Second direction; X-Third direction. Detailed Implementation

[0021] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0022] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0023] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0024] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0025] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0026] This application provides a backlash elimination device having a first direction Z, a second direction Y and a third direction X that are perpendicular to each other, specifically including a bearing housing 100, a bearing assembly 200, a top pressure structure 300 and a hydraulic drive component 500.

[0027] In some embodiments, the bearing housing 100 has two mounting cavities 101 extending through it along a first direction. A receiving cavity 102 is formed on one side of the bearing housing 100, communicating with the mounting cavity 101. A roller 400 is disposed between the two bearing housings 100, and a rotating shaft 410 is provided at both ends of the roller 400 along the first direction. The rotating shaft 410 is located within its corresponding mounting cavity 101. Each mounting cavity 101 contains a bearing assembly 200, which includes bearings sequentially arranged within the mounting cavity 101 along the first direction. The first bearing 210, the second bearing 220, and the third bearing 230 are provided. The first bearing 210 and the second bearing 220 are offset relative to the first bearing 210. The first bearing 210, the second bearing 220, and the third bearing 230 are all sleeved on the rotating shaft 410. Each accommodating cavity 102 is provided with a top pressing structure 300, which abuts against the third bearing 230. The hydraulic drive component 500 is connected to the top pressing structure 300 and drives the top pressing structure 300 to abut against the third bearing 230.

[0028] In this embodiment, the first direction mentioned above is the axial direction of the roll 400 and the shaft 410, the second direction is the transverse direction of the bearing housing 100, and the third direction is the longitudinal direction of the bearing housing 100.

[0029] Bearings mainly consist of an inner ring, an outer ring, and a shaft between the inner and outer rings. Due to the gap between the inner and outer rings and the shaft during assembly and manufacturing, the material rolling thickness of two adjacent rollers 400 is inconsistent, which in turn affects the final quality of the product.

[0030] Please see Figure 1 and Figure 4 As shown, in this embodiment, the present application is connected to 300 via transmission, so that 500 provides 300 with a contact force acting on 230 in real time. Compared with the existing method of using a threaded set screw, the present application can provide 300 with a contact force acting on 230 in real time via 500 as needed, preventing the existing set screw from undergoing plastic deformation and loosening due to vibration and load, which would cause the force acting on 230 to decrease or be lost. This ensures that 300 is always in contact with 230, preventing the force acting on 230 from decreasing or disappearing.

[0031] Please see Figure 2 , Figure 5 as well as Figure 6 As shown, the inner rings of the first bearing 210, the second bearing 220, and the third bearing 230 are all fitted onto the rotating shaft 410 and are concentric with the rotating shaft 410. The first bearing 210 and the second bearing 220 are offset relative to each other along a third direction, meaning that the outer ring centers of the first bearing 210 and the second bearing 220 are not concentric with the rotating shaft 410, and the first bearing 210 and the second bearing 220 are positioned opposite each other about the center line of the rotating shaft 410. Similarly, the outer ring of the third bearing 230 is offset relative to the rotating shaft 410 along a second direction and is not concentric with the rotating shaft 410, and the offset amounts of the first bearing 210, the second bearing 220, and the third bearing 230 relative to the rotating shaft 410 are all the same. At this time, the rotating shaft 410 is subjected to abutment from the first bearing 210, the second bearing 220, and the third bearing 230 from three directions. Please refer to [link to relevant documentation]. Figure 5 As shown, when viewed along the first direction, the contact points of the first bearing 210, the second bearing 220, and the third bearing 230 with the rotating shaft 410 are points u, v, and w, respectively, thus forming a stable triangular support structure for the rotating shaft 410. This allows the rotating shaft 410 to rotate within the triangular support area, eliminating the gaps between the inner rings, shafts, and outer rings of each bearing, and enabling the rotating shaft 410 and the roll 400 to rotate stably.

[0032] Please continue reading. Figure 5 As shown, eliminating clearance here means that at the contact point, the inner ring, shaft, and outer ring of the bearing are in contact with each other, that is, there is no clearance between the inner ring, shaft, and outer ring at this time, so as to achieve the clearance elimination function.

[0033] In some embodiments, the top pressure structure 300 includes a top pressure member 310 and a cover plate 320. The top pressure member 310 is slidably disposed in the accommodating cavity 102 along the second direction. The top pressure member 310 is sealed to the side wall of the accommodating cavity 102. The end of the accommodating cavity 102 away from the mounting cavity 101 along the second direction is provided with a cover plate 320. The cover plate 320 covers the accommodating cavity 102. The top pressure member 310 and the cover plate 320 define an oil cavity 301.

[0034] Please see Figure 2 As shown, in this embodiment, the top pressure structure 300 is disposed on the side of the bearing housing 100. That is, the contact point between the third bearing 230 and the rotating shaft 410 is the upper vertex of the rotating shaft 410. In order to continuously apply pressure to the third bearing 230, the accommodating cavity 102 is opened on the side of the bearing housing 100 and communicates with the mounting cavity 101. The top pressure member 310 is slidably disposed in the accommodating cavity 102. The upper opening of the accommodating cavity 102 is closed by the cover plate 320. At this time, an oil cavity 301 is formed between the top pressure member 310 and the cover plate 320, which can easily accommodate the hydraulic oil from the hydraulic drive member 500.

[0035] Furthermore, when it is necessary to drive the top pressure component 310 to apply pressure to the third bearing 230, the hydraulic drive component 500 needs to be activated to deliver hydraulic oil to the oil chamber 301. As the amount of hydraulic oil in the oil chamber 301 increases, it will drive the top pressure component 310 to move toward the third bearing 230 to apply pressure to it, thereby realizing pressure transmission.

[0036] Understandably, in order to prevent hydraulic oil from leaking from the gap between the top pressure member 310 and the inner wall of the accommodating cavity 102, it is necessary to make a sealing fit between the top pressure member 310 and the accommodating cavity 102. Specifically, a sealing ring can be provided on the top pressure member 310 to achieve a sealing fit between the top pressure member 310 and the accommodating cavity 102.

[0037] In some embodiments, the inner and outer ring radii of the first bearing 210 and the second bearing 220 are the same, and the offsets of the first bearing 210 and the second bearing 220 relative to the rotating shaft 410 are the same. The oil pressure output by the hydraulic drive 500 satisfies the following:

[0038] Where: Fz is the rolling force acting on roll 400, θ is the rolling force angle, T is the torque of roll 400 during operation, Rr is the radius of roll 400, a is the offset of the first bearing 210 and the second bearing 220 relative to the rotating shaft 410, P is the oil pressure output by the hydraulic drive 500, R is the outer ring radius of the first bearing 210 and the third bearing 230, r is the inner ring radius of the first bearing 210 and the second bearing 220; A is the end face area of ​​the pressing member 310 away from 230.

[0039] Please see Figure 5 As shown, the contact points between the rotating shaft 410 and the first bearing 210 and the second bearing 220 are support points u and v, respectively. The support reaction forces of the first bearing 210 and the second bearing 220 on the rotating shaft 410 are bearing support reaction forces F1 and F2, respectively. In addition, the roll is also subjected to its own gravity G, the reaction force of the film material (i.e., the rolling force Fz), the frictional force of the film material on the roll Ff, the hydraulic pressure Fd applied to the third bearing 230, and the torque T applied by the rotating drive component 600 to drive rotation; and the vector angles of each force are already shown in the diagram. Figure 5 The bid is marked.

[0040] During actual operation, sensors on the equipment can detect the torque T and rolling force Fz when the roll 400 rotates. The weight G of the roll 400 and the shaft 410 is also known and can be calculated through load-bearing capacity or bulk density. In stable operation, the force on the roll 400 is balanced, so the torque T generated by the frictional force Ff on the shaft is balanced. The radius of the roll 400 on the pressing surface is Rr, and the torque T = Ff. Rr. Based on the above known conditions, the support reactions F1 and F2 of the first bearing 210 and the second bearing 220 on the roll 400 can be calculated. The specific calculation steps are as follows: Decompose each force along the negative x-axis to obtain the component forces of each force: The rolling force is Fz cosθ The reaction force of the second bearing 220 is 2. F2 sinα The frictional force is Ff sinθ Decompose each force along the positive x-axis to obtain the component forces of each force: The reaction force of one main bearing is 2. F1 sinα Decompose each force along the negative y-axis to obtain the component forces of each force: The gravity is G; The rolling force is Fz sinθ The hydraulic set screw force is 2 Fd Decompose each force along the positive y-axis to obtain the component forces of each force: First bearing 210 support reaction force: 2 F1 cosα; Second bearing 220 support reaction force: 2 F2 cosα; Friction: Ff cosθ; When the roll 400 is running stably, it is in a state of equilibrium, that is, the resultant force in the x and y directions is zero. Therefore, the following equation is obtained: Fz cosθ+2 F2 sinα+Ff sinθ=2 F1 sinα; G+Fz sinθ+2 Fd=2 F1 cosα+2 F2 cosα+Ff cosθ; Where Ff=T / Rr, and by combining the above equations, the bearing support reaction force can be calculated.

[0041] ; ; The rolling force angle θ is related to the design of each roll position, generally 0-10°, while the support reaction angle α is related to the mechanical structure design. For example... Figure 6 The dimensional diagram shown indicates that 'a' represents the offset of the main bearing, 'r' is the radius of the inner ring of the first bearing 210 and the second bearing 220, and 'R' is the radius of the outer ring of the first bearing 210 and the second bearing 220.

[0042] See Figure 6 As shown in the figure, point A is the center of the rotating shaft 410, point B is the center of the first bearing 210, and point C is the center of the second bearing 220.

[0043] We can obtain the following from geometric relationships: Line segment AB = Rr.

[0044] Line segment OB = a.

[0045] but .

[0046] angle =arcsin(a / (Rr)).

[0047] Substituting into the above formula for solving support reactions, we get:

[0048] .

[0049] To ensure stable backlash elimination, the pressing component 310 must press the rotating shaft 410 tightly onto the two support points u and v of the first bearing 210 and the second bearing 220, i.e., ensuring F1 > 0 and F2 > 0. From the analytical expression, it is known that as long as the rolling force Fz exists, F1 > F2. Therefore, it is sufficient to ensure F2 > 0. Substituting this into the analytical expression for F2, we get:

[0050] The minimum gap-eliminating top pressure is defined as follows:

[0051] Therefore, in actual stable operation, depending on the different operating conditions, the monitoring data from the equipment sensors should be adjusted accordingly. , and the original design of the equipment , , , , By obtaining these parameters, the minimum hydraulic jacking force Fx required for stable backlash elimination under various operating conditions can be calculated, ensuring... This achieves the gap-eliminating effect. However, to ensure sufficient margin in the jacking pressure while preventing excessive hydraulic jacking pressure that could lead to large deformation of the shaft 410, a certain setting is typically implemented. =1.5 (The coefficient can be adjusted according to the actual equipment fluctuations). Furthermore, at the initial design stage, the optimal bias 'a' can be designed using the above formula to minimize... This will meet the requirements for eliminating gaps.

[0052] Given the minimum force exerted by the pressure member 310 on the third bearing 230, the minimum oil pressure delivered from the hydraulic drive member 500 to the oil chamber can be determined. According to existing knowledge, the relationship between the oil pressure P, the cross-sectional area of ​​the pressure member 310, and the pressure exerted by the pressure member on the third bearing 230 is: F = P A, where F = minimum clearance-eliminating top pressure Fx, therefore the oil pressure P satisfies: .

[0053] In some embodiments, a pressure monitor 510 is provided on the hydraulic drive 500, the pressure monitor 510 being used to monitor the oil pressure delivered to the oil chamber 301.

[0054] In order to accurately detect and control the pressure of the hydraulic oil output by the hydraulic drive unit 500, a pressure monitor 510 is installed on the hydraulic drive unit 500 to accurately monitor the oil pressure delivered to the oil chamber 301.

[0055] For example, the hydraulic drive 500 can be a hydraulic oil pump, the pressure monitor 510 can be a hydraulic sensor, or it can be other components or devices that can realize hydraulic oil delivery and hydraulic oil pressure monitoring, which are not specifically limited here.

[0056] In some embodiments, the cover plate 320 is provided with an oil inlet hole 321 through the second direction. The oil inlet hole 321 is connected to the oil cavity 301, and the end of the oil inlet hole 321 away from the top pressure member 310 is connected to the hydraulic drive member 500.

[0057] Please see Figure 1 , Figure 2 as well as Figure 4 As shown, in order to deliver hydraulic pressure from the hydraulic drive unit 500 to the oil chamber 301, an oil inlet hole 321 is provided on the cover plate 320, so that the hydraulic oil from the hydraulic drive unit 500 can enter the oil chamber 301 to drive the top pressure member 310 to move.

[0058] In some embodiments, the accommodating cavity 102 and the pressing member 310 may have a circular or rectangular cross-sectional shape as needed.

[0059] In this embodiment, the shape and size of the top pressure member 310 are the same as those of the receiving cavity 102, thereby reducing the gap between the top pressure member 310 and the inner wall of the receiving cavity 102 and preventing the hydraulic oil in the oil cavity 301 from leaking.

[0060] In this embodiment, the cross-section of the pressing member 310 is circular, and the following description will assume that the cross-section of the pressing member 310 is circular.

[0061] In some embodiments, the pressing member 310 includes a driven part 311 and a pressing part 312 connected to each other. The driven part 311 is sealed to the inner wall of the accommodating cavity 102, and the pressing part 312 abuts against the third bearing 230.

[0062] Please continue reading. Figure 2 and Figure 3 As shown, the driven part 311 and the pressing part 312 are integrally connected, and the diameter of the pressing part 312 can be smaller than the diameter of the driven part 311. That is, the area A of the pressing member 310 mentioned above is the cross-sectional area of ​​the driven part 311. Therefore, the area A can be calculated when the radius of the driven part 311 is known.

[0063] In some embodiments, the end of the pressing portion 312 that is away from the driven portion 311 is an arc surface 3101 adapted to the circumferential surface of the third bearing 230.

[0064] Please see Figure 2 and Figure 3As shown, the arc surface 3101 is perfectly matched with the curvature of the third bearing 230, thereby making the contact area between the top pressing part 312 and the outer ring of the third bearing 230 more sufficient, preventing the deformation of the outer ring of the third bearing 230 due to the small contact area between the top pressing part 312 and the third bearing 230.

[0065] See Figure 8 As shown, this application embodiment also provides a gap elimination control method for use with the gap elimination device in any of the above embodiments, comprising: S100: Obtain the radius Rr of roll 400, the rolling force Fz, the rolling force angle θ, and the torque during operation; S200: Obtain the offset a, outer ring radius R, and inner ring radius r of the first bearing 210 and the second bearing 220 relative to the rotating shaft 410, as well as the cross-sectional area A of the receiving cavity 102; S300: Substitute the above parameters into: The minimum oil pressure P of the hydraulic oil delivered to the top pressure structure 300 is obtained; S400: The oil pressure P1 delivered to the top pressure structure 300 satisfies: P1≥P.

[0066] This application also provides a roller pressing device, which includes a backlash elimination device and a rotary drive 600 as described in any of the above embodiments, and the rotary drive 600 is connected to the rotating shaft 410 for transmission.

[0067] See Figure 7 As shown, in this embodiment, the rolling equipment includes multiple horizontally arranged bearing seats 100. The rotating shaft 410 connected to it is driven to rotate by the rotating drive 600, which in turn drives the roller 400 to rotate. Under the extrusion and rolling of two adjacent rollers 400, the powder is rolled into a film. The rotating drive 600 is a motor, specifically a servo motor.

[0068] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0069] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A backlash elimination device having a first direction, a second direction, and a third direction perpendicular to each other two by two, characterized by, The utility model relates to a bearing seat (100) and bearing group (200) and top pressure structure (300) and hydraulic drive piece (500) are provided, the bearing seat (100) has two and is equipped with the installation cavity (101) through the first direction, one side of bearing seat (100) is equipped with the accommodation cavity (102) and is opened, the accommodation cavity (102) is communicated with installation cavity (101), and the roll (400) is arranged between two bearing seat (100), and the roll (400) is equipped with the rotating shaft (410) along two ends of the first direction, and the rotating shaft (410) is located in the installation cavity (101) corresponding, bearing group (200) is equipped in each installation cavity (101), bearing group (200) includes first bearing (210), second bearing (220) and third bearing (230) that are arranged in installation cavity (101) in sequence along the first direction, first bearing (210) and second bearing (220) are compared with first bearing (210) and are arranged offset, and first bearing (210), second bearing (220) and third bearing (230) are all set on the rotating shaft (410), top pressure structure (300) is equipped in each accommodation cavity (102), and top pressure structure (300) is abutted to third bearing (230), hydraulic drive piece (500) is transmission connection with top pressure structure (300), and hydraulic drive piece (500) drives top pressure structure (300) and is abutted to third bearing (230). The utility model relates to a bearing seat (100) and bearing group (200) and top pressure structure (300) and hydraulic drive piece (500) are provided, the bearing seat (100) has two and is equipped with the installation cavity (101) through the first direction, one side of bearing seat (100) is equipped with the accommodation cavity (102) and is opened, the accommodation cavity (102) is communicated with installation cavity (101), and the roll (400) is arranged between two bearing seat (100), and the roll (400) is equipped with the rotating shaft (410) along two ends of the first direction, and the rotating shaft (410) is located in the installation cavity (101) corresponding, bearing group (200) is equipped in each installation cavity (101), bearing group (200) includes first bearing (210), second bearing (220) and third bearing (230) that are arranged in installation cavity (101) in sequence along the first direction, first bearing (210) and second bearing (220) are compared with first bearing (210) and are arranged offset, and first bearing (210), second bearing (220) and third bearing (230) are all set on the rotating shaft (410), top pressure structure (300) is equipped in each accommodation cavity (102), and top pressure structure (300) is abutted to third bearing (230), hydraulic drive piece (500) is transmission connection with top pressure structure (300), and hydraulic drive piece (500) drives top pressure structure (300) and is abutted to third bearing (230). The top pressure structure (300) includes top pressure piece (310) and cover plate (320), the top pressure piece (310) is slidably arranged in the accommodation cavity (102) along the second direction, the top pressure piece (310) is sealed with the side wall of the accommodation cavity (102), the end of the accommodation cavity (102) away from the installation cavity (101) is provided with the cover plate (320) along the second direction, the cover plate (320) covers the accommodation cavity (102), and the top pressure piece (310) and the cover plate (320) define the oil cavity (301). The inner ring radius of (210) and (220) and the outer ring radius are same, and the first bearing (210) and the second bearing (220) are same to the rotating shaft (410) and are arranged offset, and the oil pressure that the hydraulic drive piece (500) outputs satisfies, satisfies: Wherein: Fz is the rolling force acting on the roll (400), theta is the rolling force angle, T is the torque when the roll (400) works, Rr is the radius of the roll (400), a is the offset amount of the first bearing (210) and the second bearing (220) relative to the rotating shaft (410), P is the oil pressure output by the hydraulic drive piece (500), R is the outer ring radius of the first bearing (210) and the third bearing (230), r is the inner ring radius of the first bearing (210) and the second bearing (220), and A is the end face area of the top pressure piece (310) away from (230).

2. The backlash elimination device according to claim 1, characterized in that ​ 3. The backlash elimination device according to claim 2, characterized in that ​ ​ 4. The backlash elimination device according to claim 2, characterized by The hydraulic drive unit (500) is provided with a pressure monitor (510), which is used to monitor the oil pressure delivered to the oil chamber (301).

5. The backlash elimination device of claim 2, wherein The cover plate (320) has an oil inlet hole (321) extending through it along the second direction. The oil inlet hole (321) is connected to the oil cavity (301). The end of the oil inlet hole (321) away from the top pressure member (310) is connected to the hydraulic drive member (500).

6. The backlash elimination device of claim 2, wherein The pressing member (310) includes a driven part (311) and a pressing part (312) connected to each other. The driven part (311) is sealed to the inner wall of the accommodating cavity (102), and the pressing part (312) abuts against the third bearing (230).

7. A backlash elimination device according to claim 6, characterized in that The end of the top pressing part (312) that is away from the driven part (311) is an arc surface (3101) that is adapted to the circumferential surface of the third bearing (230).

8. The backlash elimination device of claim 2, wherein The cross-sectional shape of the accommodating cavity (102) and the top pressing member (310) is circular or rectangular.

9. A lash control method for the lash control device of any one of claims 1 to 8, characterized by, include: Obtain the radius Rr of the roll (400), the rolling force Fz, the rolling force angle θ, and the torque during operation; Obtain the offset a of the first bearing (210) and the second bearing (220) relative to the shaft (410), the outer ring radius R and the inner ring radius r, and the cross-sectional area A of the accommodating cavity (102); The above parameters are brought into the following equation: to obtain the minimum oil pressure P of the hydraulic oil delivered into the top pressure structure (300). The oil pressure P1 delivered to the accommodating cavity (102) satisfies: P1≥P.

10. A calendering apparatus characterized by, include: The gap-eliminating device according to any one of claims 1 to 8; A rotary drive (600) is connected to the rotating shaft (410) in a transmission manner.

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