A saddle for a numerical control machine tool

Abstract

This utility model belongs to the field of CNC machine tool technology, and particularly relates to a saddle for a CNC machine tool, comprising: a base with a guide rail on the base; a saddle with its bottom slidingly engaged with the guide rail and driven by a drive unit to move along the length of the guide rail; a chip cleaning mechanism disposed on the front and rear sides of the saddle for cleaning chips from the guide rail surface in advance when the saddle moves; and a saddle balancing and stabilizing mechanism disposed on the left and right sides of the saddle, comprising a follower part and a stabilizing part; wherein the follower part is connected to the saddle and moves with the saddle, and the stabilizing part is connected to the base, and stabilizes the balance of the saddle during movement by cooperating with the follower part. Compared with the prior art, this utility model can effectively improve the moving stability of the saddle.

Description

Technical Field

[0001] This utility model belongs to the field of CNC machine tool technology, and in particular relates to a saddle for CNC machine tools. Background Technology

[0002] The saddle of a CNC machine tool is a crucial component, typically used to support and move slides, worktables, and other parts. It plays a key role in the machine tool's structure, ensuring stability and precision during machining. However, existing CNC machine tool saddles, when moving forward, are prone to tilting at the rear end due to the weight of the front machining head structure, leading to machining errors. Traditional methods using counterweights or angle compensation have several drawbacks: counterweights increase load and affect movement efficiency; angle compensation is highly susceptible to environmental influences, requiring frequent calibration and resulting in slow machining speeds; and the saddles are structurally complex and costly. Furthermore, existing CNC machine tool saddles are easily affected by debris on the guide rails during movement, hindering their motion. Therefore, improvements are necessary. Utility Model Content

[0003] The purpose of this invention is to address the aforementioned technical problems by providing a saddle for CNC machine tools, thereby effectively improving the moving stability of the saddle.

[0004] In view of this, the present invention provides a saddle for a CNC machine tool, comprising: A base, on which a guide rail is provided; Also includes: The saddle, the bottom of which is slidably engaged with the guide rail, and the saddle is driven by a drive unit to move along the length of the guide rail; A debris cleaning mechanism is provided on the front and rear sides of the saddle to clean debris from the guide rail surface in advance when the saddle moves. A saddle balancing and stabilizing mechanism is provided on the left and right sides of the saddle, and the saddle balancing and stabilizing mechanism includes a follower part and a stabilizing part; The follower is connected to the saddle and moves with the saddle. The stabilizing part is connected to the base and stabilizes the balance of the saddle during movement by cooperating with the follower.

[0005] In this technical solution, the saddle balancing and stabilizing mechanism, especially the cooperation between the stabilizing part and the follower part, can stabilize the balance of the saddle in real time during the movement process. The debris cleaning mechanism cleans the debris on the guide rail surface before the saddle moves. Compared with the prior art, this utility model can effectively improve the movement stability of the saddle.

[0006] In the above technical solution, the debris cleaning mechanism further includes: Mounting bracket, which is disposed on the front and rear sides of the saddle; A rotating disk is rotatably mounted on a mounting bracket and located directly above the guide rail via a rotating shaft; A drive motor, which is mounted on a mounting bracket; A cleaning brush, wherein the cleaning brush has a plurality of brushes and is evenly spaced along the circumference of the rotating disk on the bottom surface of the rotating disk; The drive end of the drive motor is connected to the rotating shaft to drive the rotating disk to rotate, and the brush surface of the cleaning brush is in contact with the guide rail surface.

[0007] In the above technical solution, the follower further includes: A roller frame, wherein the roller frame is disposed on the left and right sides of the saddle; The roller body is rotatably mounted on the roller frame via a roller shaft. The roller body is horizontally distributed along its axis and perpendicular to the direction of movement of the saddle.

[0008] In the above technical solution, the stabilizing unit further includes: A stabilizing frame, which is mounted on a base; The track rods are arranged on the left and right sides of the saddle, and the track rods are horizontally distributed with their length direction parallel to the moving direction of the saddle. A support unit, which is mounted on the track rod to adjust the height of the track rod and provide elastic support; One end of the track rod is hinged to the stabilizer, the support unit is located at the end of the track rod away from the stabilizer, and the roller body is in contact with the lower surface of the track rod.

[0009] In the above technical solution, the supporting unit further includes: The groove is provided on the upper end face of the track rod away from the stabilizer, and a through hole is provided in the groove that extends vertically downward through the end of the track rod; The lower pad is disposed in the groove, and the upper surface of the lower pad has a spherical groove; A pad, wherein the pad is disposed above the lower pad, and the bottom surface of the pad has a spherical protrusion that mates with a spherical groove; A disc spring assembly is disposed above the pad block, and an upper pad is provided at the top of the disc spring assembly; The lower nut, located below the end of the track shaft, is used for initial support and fixing the track height; The upper nut is positioned above the upper washer to pre-tighten the disc spring assembly and adjust the magnitude of the elastic reaction force; The outer cover is a cylindrical cover with an opening at the top and an open bottom, and the outer cover is placed on the outside of the upper nut, upper washer, disc spring assembly and pad block; A support screw, the bottom end of which is threadedly connected to the base; The upper end of the support screw passes through the lower nut, through hole, lower washer, pad, disc spring assembly, upper washer, upper nut and the top of the outer cover in sequence, and then the lower nut, through hole, lower washer, pad, disc spring assembly, upper washer, upper nut and outer cover are connected in series and fastened by the top nut. The spherical protrusion and the spherical groove form a sliding bearing interface to allow the track rod to rotate freely and move up and down freely when under force.

[0010] The beneficial effects of this utility model are: 1. Through the saddle balancing and stabilizing mechanism, especially the cooperation between the stabilizing part and the follower part, the balance of the saddle can be stabilized in real time during its movement. Even if the saddle becomes unbalanced due to factors such as the weight of the front machining head, causing the roller body to tilt and the track rod to be pressed against by the roller body, the support unit can adjust the support force on the saddle through the elastic deformation of the disc spring assembly and the slight rotation and vertical movement of the track rod itself. This ensures the saddle remains relatively stable, effectively reducing machining errors caused by saddle imbalance and improving machining accuracy. Compared to traditional counterweight methods, it does not add extra load affecting movement efficiency; compared to angle compensation, it is unaffected by the environment, requires no frequent calibration, increases machining speed, simplifies the structure, and reduces costs.

[0011] 2. The debris cleaning mechanism cleans debris from the guide rail surface before the saddle moves. The drive motor rotates the rotating disk, causing the cleaning brush to sweep the guide rail surface, removing debris and preventing it from getting stuck between the saddle and the guide rail. This prevents the saddle from being obstructed, extends the service life of the guide rail and saddle, and also improves the smoothness of the saddle movement and the reliability of the machine tool operation.

[0012] 3. By using disc springs to provide elastic reaction force, the saddle is characterized by fatigue resistance, low elastic decay after long-term use, and the ability to withstand greater pressure, which further improves the moving stability of the saddle. Attached Figure Description

[0013] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0014] Figure 1This is a schematic diagram of the structure of a specific embodiment of the present utility model.

[0015] Figure 2 This is a schematic diagram of the debris cleaning mechanism of this utility model.

[0016] Figure 3 This is a schematic diagram of the rotating disk structure of this utility model.

[0017] Figure 4 This is a schematic diagram of the saddle balancing and stabilizing mechanism of this utility model.

[0018] Figure 5 This is a schematic diagram of the support unit structure of this utility model.

[0019] The markings in the diagram are as follows: 1. Base; 2. Guide rail; 3. Saddle; 4. Debris cleaning mechanism; 40. Mounting bracket; 41. Rotating disk; 42. Rotating shaft; 43. Drive motor; 44. Sweeping brush; 5. Follower part; 50. Roller frame; 51. Roller body; 52. Roller shaft; 6. Stabilizing part; 60. Stabilizing frame; 61. Track rod; 7. Support unit; 70. Groove; 71. Through hole; 72. Lower washer; 73. Pad; 74. Disc spring assembly; 75. Lower nut; 76. Upper nut; 77. Outer cover; 78. Support screw; 79. Top nut; 710. Upper washer. Detailed Implementation

[0020] 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.

[0021] In the description of this application, it should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. For ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0022] Saddle 3 Balance and Stabilization Mechanism The follower unit 5 and roller frame 50 are integrally formed from high-strength metal sheets. Their structural outline perfectly matches the middle and rear areas of the left and right sides of the saddle 3 (corresponding to the rear portion of the saddle 3 that is prone to tilting upwards), ensuring a fit of ≥95% with the sides of the saddle 3. The roller frame 50 is fixed to the sides of the saddle 3 using two connection methods: the main body area is welded (weld height not less than 1 / 2 of the sheet thickness), and the edge auxiliary areas are connected with high-strength bolts (bolt grade not less than 8.8), with uniform bolt spacing to ensure balanced force. The installation direction of the roller frame 50 is strictly perpendicular to the moving direction of the saddle 3, with a perpendicularity error controlled within ±0.1°, ensuring stable contact between the roller body 51 and the lower surface of the track rod 61, accurately transmitting the force generated by the tilting of the saddle 3. Roller body 51: The main body is cylindrical with a bearing mounting hole in the central axis. A high-precision deep groove ball bearing (bearing precision grade not lower than P6) is installed in the hole with an interference fit. The inner ring of the bearing forms a clearance fit with the roller shaft 52 (fit clearance 0.005-0.01mm) to reduce rotational resistance. A roller bushing is provided between the roller body 51 and the roller frame 50. The bushing is made of polyurethane elastic wear-resistant material and is ring-shaped and fitted at both ends of the journal of the roller body 51. The inner diameter of the bushing has a transition fit with the journal of the roller shaft 52, and the outer diameter has a clearance fit with the mounting hole of the roller frame 50. The elastic deformation of the bushing maintains a reasonable clearance (clearance value 0.02-0.05mm) between the roller body 51 and the roller frame 50 to prevent long-term wear from causing the clearance to become too large and affecting the accuracy of influence transmission. Roller shaft 52: Composed of a threaded bolt shaft and a matching hexagonal nut. The coaxiality error between the threaded section and the smooth section of the bolt shaft is ≤0.02mm. The bolt shaft passes sequentially through the mounting hole on one side of the roller frame 50, the inner ring of the bearing at the center of the roller body 51, and the mounting hole on the other side of the roller frame 50, and is then tightened with the hexagonal nut. After the nut is tightened, an anti-loosening washer is used to lock it, ensuring that the axial movement of the roller body 51 on the roller frame 50 is ≤0.03mm, and that it can rotate flexibly around the roller shaft 52 (rotational resistance torque ≤0.5N・m). This does not affect the normal movement of the saddle 3, and can transmit force immediately when the saddle 3 tilts upward. Overall connection: Two roller frames 50 (corresponding to the left and right sides of the saddle 3 respectively) are symmetrically distributed in the middle and rear of the saddle 3. The axis of the roller body 51 is perpendicular to the moving direction of the saddle 3, and the outer circumferential surface of the roller body 51 forms a tight line contact with the lower surface of the track rod 61 of the stabilizing part 6. The contact length is not less than 2 / 3 of the length of the roller body 51, ensuring that the force generated when the saddle 3 tilts upward can be completely transmitted to the track rod 61 without loss of force. Working process: When the drive unit moves the saddle 3 along the guide rail 2, the saddle 3, through a double fixing structure of welding and bolt connection, drives the roller frames 50 on both sides to move synchronously. Since the outer circumferential surface of the roller body 51 is in close contact with the lower surface of the track rod 61, during the normal movement of the saddle 3, the roller body 51 rotates around its own axis and rolls in a straight line along the lower surface of the track rod 61, providing stable follow-up support for the saddle 3 without adding extra movement resistance. When the rear of the saddle 3 tends to tilt upwards due to the weight of the front machining head (load ≥ 100kg) or the machining cutting force, the rear of the saddle 3 will lift upwards, causing the roller frame 50 on the same side to move upwards synchronously. At this time, because the roller body 51 is in close contact with the lower surface of the track rod 61, the track rod 61 generates a downward blocking force on the roller body 51, while the roller body 51 transmits the upward force generated by the tilting of the rear of the saddle 3 (the magnitude of the force is proportional to the tilting tendency) in the opposite direction to the track rod 61, forming a force transmission path of "saddle 3 tilting upwards - roller receiving force - force transmitted to track rod 61", providing the initial force for subsequent elastic balance. Stabilizing unit 6, stabilizing frame 60: Anchor bolt mounting holes are provided at the bottom (the hole positions correspond one-to-one with the pre-set threaded holes on the base 1). The stabilizing frame 60 is fixed to the base 1 using high-strength anchor bolts (bolt grade not lower than 10.9). After tightening the bolts, double nuts are used to prevent loosening, ensuring that the connection rigidity between the stabilizing frame 60 and the base 1 is ≥5×10. 5 The torque (N / m) is sufficient to withstand the upward force transmitted by the track rod 61 without deformation. The height of the stabilizer 60 is precisely matched with the height of the roller frame 50 on the side of the saddle 3, with an error of ≤±0.5mm, ensuring that the track rod 61 can precisely fit against the outer circumference of the roller body 51 after installation, and that the track rod 61 remains horizontal in its initial state, providing a stable foundation for force transmission. The two stabilizers 60 are symmetrically arranged on the base 1 at the left and right sides of the saddle 3, respectively, and the parallelism error between the longitudinal axis of the stabilizer 60 (along the length of the guide rail 2) and the axis of the guide rail 2 is ≤±0.05mm, preventing the track rod 61 from tilting and causing a deviation in the force transmission direction. Track rod 61: Made of high-strength alloy structural steel (material not less than 40Cr), with chrome plating (chrome plating layer thickness 0.05-0.1mm) and surface roughness Ra≤0.8μm to improve surface smoothness and wear resistance (hardness ≥HRC55), extending the service life of contact with the roller body 51. One end of track rod 61 is provided with a hinge connection hole, which is connected to the top of the stabilizer 60 through a single-ear hinge. The hinge pin and the connection hole of track rod 61 are transition fit (fit clearance 0.01-0.03mm). The two ends of the pin are axially positioned by elastic retaining rings to ensure that track rod 61 can rotate slightly within ±5° around the hinge pin (mainly upward rotation, to meet the force transmission requirements when the saddle 3 tilts upward), and the rotational resistance torque is ≤1N・m, ensuring that track rod 61 can respond instantly to the force transmitted by roller body 51. The other end of the track rod 61 extends to the end of the moving range of the saddle 3 (more than 10% beyond the maximum moving stroke of the saddle 3), and the end is pre-set with a support unit 7 mounting structure (including groove 70 and through hole 71) to ensure that the track rod 61 completely transmits the received upward force to the disc spring assembly 74 of the support unit 7. Overall Connection: The track rod 61 and the stabilizer frame 60 are rotatably connected by a hinge. The upper surface of the track rod 61 is in line contact with the lower surface of the roller body 51, and the straightness error of the contact area is ≤0.02mm / m, ensuring uniform force transmission without local stress concentration. The length of the track rod 61 covers the entire travel of the saddle 3, and the arrangement of the track rod 61 completely coincides with the movement path of the roller frame 50 of the saddle 3, ensuring that the roller body 51 can maintain contact with the track rod 61 and transmit force even if the saddle 3 tilts upward at any position, with no support blind spots. Working process: When the saddle 3 moves normally along the guide rail 2, the roller body 51 of the follower part 5 rolls on the lower surface of the track rod 61. The track rod 61 provides a stable support surface for the roller body 51 through its own rigid structure, restricting the meaningless displacement of the roller body 51 in the vertical direction, ensuring that the saddle 3 moves smoothly and does not produce additional shaking. When the rear of the saddle 3 begins to tilt upwards, the roller body 51 transmits the upward force to the track rod 61. The track rod 61 then experiences an upward thrust and rotates slightly clockwise around the hinge end of the stabilizer 60 (based on the direction of movement of the saddle 3). The end of the track rod 61 furthest from the stabilizer 60 (the rear end) then lifts upwards. Since the rear end of the track rod 61 is in direct contact with the disc spring assembly 74 of the support unit 7 through the lower pad 72 and the pad 73, the upward force of the track rod 61 directly acts on the pad 73, thereby pushing the pad 73 upwards to compress the disc spring assembly 74. This forms a force transmission chain of "track rod 61 under force - rotation around the hinge - rear end lifting - compression of disc spring assembly 74," converting the upward force of the saddle 3 into a compressive force on the disc spring assembly 74, providing the premise for the disc spring assembly 74 to generate an elastic reaction force. If the upward tilting tendency of saddle 3 weakens or disappears, the upward force on track rod 61 decreases, the compression of disc spring assembly 74 decreases accordingly, the elastic reaction force decreases synchronously, and track rod 61 rotates counterclockwise around the hinge end under the action of the elastic reaction force of disc spring assembly 74, gradually returning to the horizontal state, waiting for the force transmission and balance action when saddle 3 tilts up again, forming a dynamic response cycle.

[0023] Support unit 7 Basic load-bearing structure: end structure of track rod 61: a groove 70 is machined on the upper end face of the end of track rod 61 away from the stabilizer 60. The depth of groove 70 is 1 / 3 to 1 / 2 of the diameter of track rod 61, ensuring that the lower pad 72 can be stably embedded in groove 70 without radial displacement; a through hole 71 is machined at the center of the bottom of groove 70, which is vertically penetrating the end of track rod 61. The diameter of through hole 71 is larger than the nominal diameter of support screw 78, ensuring that support screw 78 can pass through smoothly and leaving room for movement of track rod 61. Support screw 78: Made of high-strength alloy structural steel (material not less than 35CrMo), with surface heat treated (hardness 28-32HRC). The bottom end is machined with external threads (thread accuracy grade 6g), forming a threaded connection with the pre-set internal threaded hole (thread accuracy grade 6H) on the base 1. The tightened threaded connection can withstand axial pressure ≥50kN, providing a stable foundation for the entire support unit 7 and preventing displacement of the support screw 78 due to the upward force of the saddle 3. The upper end of the support screw 78 passes sequentially through the lower nut 75, the through hole 71 of the track rod 61, the lower washer 72, the pad 73, the disc spring assembly 74, the upper washer 710, the upper nut 76, and the opening at the top of the outer cover 77, forming a series support structure to ensure that each component can transmit force and displacement along the axial direction of the support screw 78. The lower shim 72 is made of tin bronze and has a circular sheet structure. The upper surface is machined with a spherical groove 70 (the radius of the sphere R is determined according to the radius of the spherical protrusion of the shim 73, and the fitting gap is 0.005-0.01mm). The lower surface is in close contact with the bottom surface of the groove 70 of the track rod 61 (fitting degree ≥98%). The radial displacement of the lower shim 72 is limited by the positioning function of the groove 70, ensuring that the force transmitted by the track rod 61 can act perpendicularly on the lower shim 72. Spacer 73: Made of stainless steel (material 304), cylindrical in shape, with a spherical protrusion on the bottom surface that matches the spherical groove 70 of the lower spacer 72 (sphericity error ≤0.005mm), and a flat top surface (flatness error ≤0.01mm), making full contact with the bottom surface of the disc spring assembly 74. The spherical protrusion of spacer 73 and the spherical groove 70 of the lower spacer 72 form a sliding bearing interface. High-temperature grease (operating temperature range -20℃-150℃) is applied between the interfaces to reduce the coefficient of friction during relative sliding (coefficient of friction ≤0.1), ensuring that when the track rod 61 rotates around the hinge, spacer 73 can be slightly adjusted with the tilt angle of the track rod 61, so that the compressive force always acts perpendicularly on the disc spring assembly 74, avoiding damage caused by uneven force on the disc spring assembly 74. Disc spring assembly 74: Composed of multiple disc springs of the same specification (material not less than 60Si2MnA), stacked in a mating manner (concave surfaces of adjacent disc springs facing each other) to obtain a larger elastic deformation and a smoother elastic reaction force curve, adapting to the balance requirements of different degrees of upward tilting of saddle 3. The number of disc spring assemblies 74 is determined according to the designed elastic reaction force, generally 3-8 pieces. The total height of the stacked disc spring assembly 74 is 1.5-3 times the height of a single disc spring, and the inner diameter of the disc spring assembly 74 is matched with the optical axis section of the support screw 78 (gap 0.05-0.1mm) to ensure that the disc spring assembly 74 can deform uniformly along the axial direction of the support screw 78 without jamming when compressed. Upper washer 710 and lower nut 75: The upper washer 710 is made of rubber elastic material (Shore hardness 60-70HA), and is in the shape of a circular sheet. Its inner diameter is clearance-fitted with the optical axis section of the support screw 78, and its outer diameter is adapted to the outer diameter of the disc spring assembly 74. Through its own elastic deformation, it ensures full contact with the top surface of the disc spring assembly 74 and disperses the pressure of the disc spring assembly 74 on the upper structure. The lower nut 75 is a hexagonal nut (material not less than 45 steel, hardness 20-25HRC), which is connected to the threaded section below the optical axis section of the support screw 78. It is used to initially support the track rod 61 and adjust the initial height of the track rod 61 so that the track rod 61 remains horizontal when not under force. After the nut is tightened, it fits tightly with the lower end face of the track rod 61 (fitting pressure ≥5kN) to prevent the track rod 61 from moving up and down during normal movement. Fixing and Protective Structure: Upper Nut 76: A hexagonal thin nut (material not less than 45 steel, hardness 20-25HRC) is used, which connects to the threaded section above the optical axis section of the support screw 78. By adjusting the tightening degree, a preload is applied to the disc spring assembly 74 (preload range 5-20kN), thereby adjusting the initial elastic reaction force of the disc spring assembly 74 (elastic reaction force and preload are linearly related, correlation coefficient R). 2(≥0.99), the initial reaction force can be preset according to the actual weight and processing load of the saddle 3 to improve the response speed to the upward trend of the saddle 3. Outer cover 77: made of cold-rolled steel plate (thickness 1-1.5mm) stamped and formed into a cylindrical cover with an opening at the top and an open bottom. The diameter of the opening at the top is clearance-fitted with the optical axis section of the support screw 78 (clearance 0.1-0.2mm), and the inner diameter at the bottom is adapted to the outer diameter of the end of the track rod 61 (adaptation clearance 0.5-1mm). The outer cover 77 completely covers the outside of the upper nut 76, upper washer 710, disc spring assembly 74 and pad 73. The bottom is fixed to the upper end face of the end of the track rod 61 by spot welding to form a closed protective space to prevent processing debris and cutting fluid from entering the interior and affecting the force transmission efficiency and service life of the elastic component. Top nut 79: A hexagonal nut (material not less than 45 steel, hardness 20-25HRC) is tightened on the top of the support screw 78. The lower nut 75, track rod 61, lower washer 72, pad block 73, disc spring assembly 74, upper washer 710, upper nut 76 and outer cover 77 are connected in series and tightened to form a complete support unit 7, ensuring that there is no relative looseness of each component (looseness ≤0.01mm) and that the force transmission path is complete and without loss. Workflow: Force Transmission and Elastic Reaction Generation Process: When the track rod 61 is lifted upward due to the upward tilting of the rear of the saddle 3, the bottom surface of the groove 70 at the end of the track rod 61 applies upward pressure to the lower pad 72. The lower pad 72 accurately transmits the pressure to the spherical protrusion of the pad block 73 through the spherical groove 70 (pressure transmission efficiency ≥95%). Under the action of pressure, the pad block 73 moves upward, compressing the disc spring assembly 74 above. After being subjected to axial compressive force, the disc spring assembly 74 undergoes elastic deformation. The amount of deformation is proportional to the magnitude of the compressive force (the proportionality coefficient is the stiffness coefficient of the disc spring assembly 74). At the same time, according to Hooke's Law, a downward elastic reaction force is generated. The magnitude of this reaction force is proportional to the amount of compression of the disc spring assembly 74, forming a balanced force opposite to the upward tilting force of the saddle 3. Upward tilting balancing process: The downward elastic reaction force generated by the disc spring assembly 74 is transmitted in the opposite direction to the track rod 61 through the pad 73 and the lower pad 72 (reaction force transmission efficiency ≥92%). Under the action of the reaction force, the track rod 61 obtains a downward constraint force, which is transmitted to the roller body 51 through the track rod 61. The roller body 51 then applies the constraint force to the rear of the saddle 3, forming a reverse force transmission chain of "disc spring reaction force - track rod 61 transmission - roller pressure - saddle 3 balance". Since the magnitude of the elastic reaction force increases synchronously with the increase of the upward tilting force of the saddle 3, it can match the change of the upward tilting trend of the saddle 3 in real time, effectively counteract the upward tilting force at the rear of the saddle 3, and control the upward tilting amount at the rear of the saddle 3 within the range of ≤0.05mm, avoiding processing errors caused by tilting.

[0024] Adaptive adjustment mechanism: Throughout the balancing process, the sliding bearing interface formed by the spherical protrusion on the bottom surface of the pad 73 and the spherical groove 70 on the upper surface of the lower pad 72 allows the track rod 61 to rotate freely around the spherical contact point (rotation angle ≤ 1°) when under force. This ensures that the track rod 61 can adaptively adjust its posture according to the upward angle of the saddle 3, so that the elastic reaction force always acts on the rear of the saddle 3 in the vertical direction, avoiding a decrease in the balancing effect due to force direction deviation. At the same time, the track rod 61 can move up and down along the support screw 78 by ≤ 0.1 mm, ensuring that the disc spring assembly 74 can deform sufficiently to generate enough elastic reaction force, avoiding rigid collisions or stress concentration (stress concentration factor ≤ 1.2).

[0025] Debris removal mechanism 4 Mounting bracket 40, structural design: It is made of lightweight, high-strength aluminum alloy (material 6061-T6) in one piece, with an overall "L" shape. The horizontal section is used to connect the saddle 3, and the vertical section is used to install the rotating disk 41 and the drive motor 43. The horizontal section of the mounting bracket 40 has waist-shaped bolt holes (the length of the holes is consistent with the movement direction of the saddle 3). It is connected to the front and rear sides of the saddle 3 by internal hex bolts. After the bolts are tightened, they are locked with thread-locking adhesive. The waist-shaped hole design allows the mounting bracket 40 to be adjusted in height by ±5mm in the vertical direction to accommodate guide rails 2 of different heights.

[0026] The number of mounting brackets 40 corresponds one-to-one with the number of guide rails 2 on the base 1, that is, each guide rail 2 is equipped with two mounting brackets 40 (corresponding to the front and rear sides of the saddle 3 respectively). The projections of the two mounting brackets 40 corresponding to the same guide rail 2 on the front and rear sides of the saddle 3 are completely overlapped, ensuring that the rotating disk 41 can be accurately positioned directly above the guide rail 2 after installation (centering error ≤ 0.5mm). The mounting brackets 40 corresponding to adjacent guide rails 2 maintain a uniform spacing, and the spacing value is consistent with the spacing of the guide rails 2 to avoid interference between the mounting brackets 40. The rotating disk 41 and the drive assembly: The rotating disk 41 is made of low-carbon steel plate (material Q235) and is a circular flat plate structure. The bottom surface has mounting holes for cleaning brushes 44 along the circumference (the number of holes is the same as the number of cleaning brushes 44, evenly distributed, with a distribution angle error ≤1°). A mounting hole for a rotating shaft 42 is opened in the central axis of the rotating disk 41. The rotating shaft 42 is connected to the rotating disk 41 by a key (key connection accuracy level not lower than 9), ensuring that the coaxiality error between the rotating shaft 42 and the rotating disk 41 is ≤0.03mm, and that they can rotate synchronously (transmission efficiency ≥99%). Shaft 42: Made of 45 steel with heat treatment (hardness 22-25HRC), its lower end is connected to the rotating disk 41 by a key, and its upper end is installed in the preset hole of the vertical section of the mounting bracket 40 by a deep groove ball bearing (precision grade P6). The outer ring of the bearing is interference fit with the hole of the mounting bracket 40, and the inner ring is transition fit with the shaft 42, ensuring that the shaft 42 can rotate flexibly around its own axis (rotational resistance torque ≤0.3N・m). Drive motor 43: A permanent magnet synchronous motor is selected (power is determined according to cleaning requirements, generally 0.3-0.75kW, speed 1000-2000r / min). It is fixed to the outside of the vertical section of the mounting bracket 40 by a motor mount, and the motor mount and mounting bracket 40 are connected by bolts (bolt grade not lower than 6.8). The drive end (output shaft) of the motor is connected to the upper end of the rotating shaft 42 through a conventional transmission component, such as a coupling drive: a flexible coupling (made of aluminum alloy) is used to directly connect the motor output shaft and the upper end of the rotating shaft 42. The compensation of the coupling can offset the coaxiality error between the motor and the rotating shaft 42 (compensation ≤0.2mm), and there is no backlash in the transmission. Sweeping brush 44: The main body of sweeping brush 44 is made of nylon 66 or pig bristles (nylon bristle diameter 0.15-0.3mm, pig bristle bristle diameter 0.2-0.4mm). The bristle length is determined according to the flatness of the guide rail 2 surface (generally 2-5mm). The bristle roots are fixed to the brush base by a bristle implantation process (bristle implantation density ≥50 bristles / cm). 2 The brush holder is injection molded from ABS engineering plastic, and the back is equipped with threaded posts that are compatible with the mounting holes of the rotating disk 41. The cleaning brush 44 is threadedly connected to the mounting hole on the bottom surface of the rotating disk 41 via a threaded post on the back of the brush holder. After tightening, the bottom surface of the brush holder and the bottom surface of the rotating disk 41 are tightly fitted (fit ≥ 95%), ensuring that the cleaning brush 44 has no radial movement (movement ≤ 0.1 mm). The cleaning brushes 44 are evenly spaced along the circumference of the rotating disk 41, and the bristles of adjacent cleaning brushes 44 overlap by 10%-20% in the coverage area on the surface of the guide rail 2, ensuring that there are no blind spots on the surface of the guide rail 2 (blind spot rate 0%).

[0027] Contact control: After the cleaning brush 44 is assembled, the contact pressure between the brush surface and the guide rail 2 surface is precisely controlled by adjusting the height of the mounting bracket 40. It is generally controlled between 5-15N, which ensures that the bristles can make close contact with the guide rail 2 surface (contact depth 0.5-1mm) while avoiding excessive squeezing that could cause bristle deformation (deformation amount ≤10%) or accelerated wear.

[0028] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. A saddle for a CNC machine tool, comprising: A base (1) is provided with a guide rail (2); Its characteristic is that it further includes: The bottom of the saddle (3) is slidably engaged with the guide rail (2) and the saddle (3) is driven by the drive unit to move along the length direction of the guide rail (2); The debris cleaning mechanism (4) is set on the front and rear sides of the saddle (3) to clean the debris on the surface of the guide rail (2) in advance when the saddle (3) moves. The saddle (3) balance and stabilization mechanism is provided on the left and right sides of the saddle (3). The saddle (3) balance and stabilization mechanism includes a follower (5) and a stabilizing part (6). The follower (5) is connected to the saddle (3) and moves with the saddle (3). The stabilizing part (6) is connected to the base (1). The stabilizing part (6) stabilizes the balance of the saddle (3) during its movement by cooperating with the follower (5).

2. A saddle for a numerically controlled machine tool according to claim 1, characterized in that The debris cleaning mechanism (4) further includes: Mounting bracket (40) is provided on the front and rear sides of the saddle (3); A rotating disk (41) is rotatably mounted on a mounting bracket (40) and located directly above the guide rail (2) via a rotating shaft (42); A drive motor (43) is mounted on a mounting bracket (40); A cleaning brush (44) having a plurality of brushes evenly spaced along the circumference of the rotating disk (41) on the bottom surface of the rotating disk (41); The drive end of the drive motor (43) is connected to the rotating shaft (42) to drive the rotating disk (41) to rotate, and the brush surface of the cleaning brush (44) is in contact with the surface of the guide rail (2).

3. A saddle for a numerically controlled machine tool according to claim 2, characterized in that The follower (5) also includes: Roller frame (50) is provided on the left and right sides of the saddle (3); The roller body (51) is rotatably mounted on the roller frame (50) via the roller shaft (52); The roller body (51) is horizontally distributed along its axis and is perpendicular to the moving direction of the saddle (3).

4. A saddle according to claim 3, characterized in that The stabilizing part (6) further includes: A stabilizer (60) is mounted on a base (1); The track rod (61) is arranged on the left and right sides of the saddle (3). The track rod (61) is horizontally distributed and the length direction of the track rod (61) is parallel to the moving direction of the saddle (3). Support unit (7), which is mounted on track rod (61) for adjusting the height of track rod (61) and providing elastic support; One end of the track rod (61) is hinged to the stabilizer (60), the support unit (7) is located at the end of the track rod (61) away from the stabilizer (60), and the roller body (51) is in contact with the lower surface of the track rod (61).

5. A saddle for a numerically controlled machine tool according to claim 4, characterized in that The support unit (7) also includes: A groove (70) is provided on the upper end face of the track rod (61) away from the stabilizer (60), and a through hole (71) is provided in the groove (70) to penetrate vertically downward through the end of the track rod (61); The lower pad (72) is disposed in the groove (70), and the upper surface of the lower pad (72) has a spherical groove (70); A pad (73) is disposed above the lower pad (72), and the bottom surface of the pad (73) has a spherical protrusion that mates with the spherical groove (70); Disc spring assembly (74), the disc spring assembly (74) is disposed above the pad (73), and the top of the disc spring assembly (74) is provided with an upper pad (710); The lower nut (75) is located below the end of the track shaft and is used for initial support and fixing of the track height; Upper nut (76), which is positioned above the upper washer (710) for pre-tightening the disc spring assembly (74) and adjusting the magnitude of the elastic reaction force; The outer cover (77) is a columnar cover with an opening at the top and an open bottom. The outer cover (77) covers the outside of the upper nut (76), the upper washer (710), the disc spring assembly (74) and the pad (73). A support screw (78) is provided, the bottom end of which is threadedly connected to the base (1); The upper end of the support screw (78) passes through the bottom nut (75), through hole (71), bottom washer (72), pad (73), disc spring assembly (74), top washer (710), top nut (76) and outer cover (77) in sequence, and then the bottom nut (75), through hole (71), bottom washer (72), pad (73), disc spring assembly (74), top washer (710), top nut (76) and outer cover (77) are connected in series and fastened by the top nut (79). A sliding bearing interface is formed between the spherical protrusion and the spherical groove (70) to allow the track rod (61) to rotate freely and move up and down freely when under force.

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