A battery pole production with a heart machine

Abstract

The application relates to the technical field of battery production and discloses a battery pole production centering machine, which comprises a base, a rack assembly and a main shaft, the rack assembly is provided with two transmission tooth surfaces arranged in a back-to-back mode on both sides along the length direction of the rack assembly, the length direction of the rack assembly is parallel to the sliding direction of the main shaft, a driving gear and an anti-backlash gear are arranged on the main shaft, and an elastic pre-tightening piece and a rigid limiting piece are arranged between the main shaft and the anti-backlash gear. According to the application, the position of the rigid limiting piece is actively adjusted by a linear driving component to change the compression amount of the elastic pre-tightening piece, and the timing synchronization of the pre-tightening force state change and the main shaft reversing is realized by combining sensor closed-loop feedback, high pre-tightening force is provided in the feeding cutting stage to resist impact and prevent disengagement, and the pre-tightening force is switched to low pre-tightening force in the back-off positioning stage to avoid stick-slip sliding and response lag.

Description

Technical Field

[0001] This invention relates to the field of battery manufacturing technology, specifically to a Swiss-type lathe for producing battery terminals. Background Technology

[0002] As the core component connecting the battery cell to the external circuit, the critical dimensional accuracy of the battery terminals, such as the height of the sealing step, the overall length, and the positional accuracy, directly determines the sealing reliability and assembly consistency of the battery. The machining of these parts is a typical short-stroke, high-frequency cyclic operation involving "feeding, retraction, and shifting," requiring extremely high production cycle time and continuous operation for extended periods. To adapt to this machining characteristic, existing Swiss-type lathes often employ a servo motor-driven ball screw structure for the Z-axis feed. However, under these conditions, the screw pair generates accumulated heat due to high-frequency commutation friction, causing Z-axis thermal elongation and resulting in drift of critical workpiece dimensions. Furthermore, when facing the continuous feeding requirements of long terminals or long bars, traditional long screws are limited by critical speed and self-weight sag effects, making it difficult to balance long strokes and high-cycle production. To overcome these bottlenecks, some equipment has begun to adopt a gear and rack structure to replace the ball screw as the Z-axis feed solution. While this structure fundamentally eliminates the accumulation of thermal elongation and critical speed limitations, it also introduces new technical challenges in the high-frequency reciprocating precision machining of battery terminals.

[0003] The inherent meshing backlash of rack and pinion drives is fundamentally in conflict with the high-frequency reciprocating motion of battery terminals. Each change in direction requires traversing the dead zone of backlash between the gear and rack. During the feed phase, the cutting force can still press the drive gear against the working tooth surface to maintain meshing; however, during the retraction phase, due to the lack of auxiliary clamping force from the cutting force, the engagement between the gear and the tooth surface relies entirely on the preload of the backlash elimination mechanism. If the backlash is not effectively eliminated, random offsets will occur during retraction positioning, directly causing a drift in the absolute starting point of the next feed. This cumulative error caused by the commutation backlash will lead to batch deviations in critical dimensions such as the position, coaxiality, and sealing step height of the terminals. In other words, while the rack and pinion structure eliminates the thermal error of the lead screw, it introduces new positioning uncertainties at the high-frequency commutation node, severely restricting the stability of machining accuracy.

[0004] However, the preload applied to eliminate this backlash is itself caught in a dilemma where the requirements of the feed and retraction stages conflict. A single constant preload cannot simultaneously adapt to two completely different mechanical boundary conditions. During the feed cutting stage, the peak impact load generated by intermittent cutting can be several times the average cutting force. At this time, the backlash-eliminating gear is subjected to a strong reverse separation force, and a sufficiently large preload must be applied to resist the external impact and prevent vibration and tool deflection caused by transient disengagement. However, when the working condition switches to the retraction positioning stage, the system is only subjected to weak friction and inertial forces. The large preload previously set to ensure feed rigidity will instead be converted into additional static friction of the sliding pair, causing the servo system to exhibit a viscous sliding effect during reversal. This not only prolongs the setting time and reduces the production cycle, but also induces new thermal balance problems due to continuous high frictional heat, offsetting the original thermal advantages of gear and rack transmission. Conversely, if the preload setting is reduced to take into account the return response, the impact margin during the feed stage will be insufficient, and the backlash-free gear will easily detach from the tooth surface under the action of the reverse component of the cutting force, resulting in rigid impact and tooth surface damage. Summary of the Invention

[0005] In view of this, the purpose of the present invention is to provide a sliding headstock machine for producing battery terminals, so as to solve the problems existing in the background art.

[0006] To solve the above-mentioned technical problems, the technical solution of the present invention is a sliding headstock machine for producing battery terminals, comprising a base, a rack assembly, and a main shaft. The rack assembly is fixedly mounted on the base, and has two back-to-back transmission tooth surfaces on both sides along its length direction. The length direction of the rack assembly is parallel to the sliding direction of the main shaft. The main shaft is slidably mounted on the base, and is provided with a drive gear and a backlash-eliminating gear. The drive gear is rotatably mounted on the main shaft and meshes with one of the transmission tooth surfaces. The backlash-eliminating gear... The rack assembly is slidably mounted on the main shaft along a direction perpendicular to its length and meshes with another transmission tooth surface. An elastic preload and a rigid stop are provided between the main shaft and the backlash-eliminating gear, with the rigid stop slidably mounted on the main shaft. The elastic preload applies an elastic preload force to the backlash-eliminating gear, pointing towards the corresponding transmission tooth surface, to eliminate meshing backlash. Adjusting the position of the rigid stop on the main shaft changes the compression of the elastic preload, thereby adjusting the magnitude of the elastic preload force to adapt to the mechanical requirements of the feed and retraction phases, respectively.

[0007] Preferably, the rack assembly is a single rack, with the two transmission tooth surfaces integrally formed on opposite side walls along its length.

[0008] Preferably, the rack assembly includes two independent racks, which are fixedly arranged side by side on the base along a direction perpendicular to the length of the rack assembly, and the opposite sides of the two independent racks respectively form two transmission tooth surfaces.

[0009] Preferably, the spindle is further provided with a linear drive component, and the rigid limiting component is installed on the moving end of the linear drive component; the linear drive component drives the rigid limiting component to slide on the spindle to adjust the compression amount of the elastic preload.

[0010] Furthermore, a drive motor is also provided on the spindle, and the output end of the drive motor is connected to the drive gear. The linear drive component moves the rigid limit member to a preset feed position during the feed phase and moves the rigid limit member to a preset retraction position during the retraction phase. Sensors are provided at both the feed position and the retraction position. The sensors detect the positioning status of the rigid limit member and feed back signals to control the forward and reverse switching of the drive motor, thereby realizing the coordinated linkage between preload adjustment and spindle feed reversal.

[0011] Preferably, the base is provided with a guide rail for sliding guidance of the spindle, and a compression wedge and a release wedge are provided on the guide rail along the axial direction of the spindle; the compression wedge has a first wedge-shaped surface facing the spindle retraction direction, and the release wedge has a second wedge-shaped surface facing the spindle feed direction, the first wedge-shaped surface and the second wedge-shaped surface are arranged opposite to each other; the rigid limiting member is provided with a first working surface that slides with the first wedge-shaped surface and a second working surface that slides with the second wedge-shaped surface.

[0012] Furthermore, a slotted engagement structure is provided between the rigid limiting member and the main shaft; when the compression wedge or the release wedge drives the rigid limiting member to move axially to a preset position, the slotted engagement structure engages with each other to limit the rigid limiting member.

[0013] Furthermore, an adjustment groove is provided on the guide rail along the axial direction, and the compression wedge and / or release wedge are installed in the adjustment groove by fasteners; the locking position of the fasteners in the adjustment groove is adjusted to change the axial installation position of the compression wedge and / or release wedge on the guide rail.

[0014] The main technical effects of this invention are reflected in the following aspects: This invention designs the backlash-free gear to slide on the spindle along a direction perpendicular to the length of the rack, ensuring that the direction of the elastic preload is strictly orthogonal to the spindle's z-axis feed direction. The key significance of this mechanical arrangement is that, regardless of how the preload is adjusted to meet the different needs of the feed and retraction phases, its vector of action remains perpendicular to the spindle's axis of motion, preventing the generation of any additional component force or frictional resistance torque in the feed direction.

[0015] This invention actively adjusts the position of the rigid limiter through a linear drive component to change the compression of the elastic preload, and combines sensor closed-loop feedback to achieve timing synchronization between preload state changes and spindle reversal. It provides high preload during the feed cutting stage to resist impact and prevent disengagement, and switches to low preload during the retraction positioning stage to avoid sticking, slippage and response lag. At the same time, it integrates a purely mechanical passive separation double wedge switching mechanism as a redundancy backup, which uses the spindle's own reciprocating motion to trigger the establishment and release of preload. The two functions are executed by independent wedges, the rates can be optimized separately, and the timing is naturally synchronized, completely eliminating the risk of electronic control delay. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the structure of the present invention; Figure 2 for Figure 1 Schematic diagram of the mating structure between the rack and pinion assembly and the spindle; Figure 3 for Figure 1 Schematic diagram of the mating structure between the guide rail and the spindle; In the figure: 1. Base; 2. Rack assembly; 3. Main shaft; 4. Drive gear; 5. Backlash-free gear; 51. Elastic preload; 52. Rigid limiting component; 6. Guide rail; 61. Compression wedge; 62. Release wedge; 63. First wedge surface; 64. Second wedge surface; 65. First working surface; 66. Second working surface. Detailed Implementation

[0017] The specific embodiments of the present invention will be further described in detail below with reference to the accompanying drawings, so as to make the technical solution of the present invention easier to understand and master. In the embodiments, it should be understood that the terms "middle," "upper," "lower," "top," "right side," "left end," "above," "back," "center," etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention, 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 the present invention. In addition, unless otherwise specified in this specific embodiment, the connection or fixing method between components can be achieved by bolt fixing, pin fixing, or pin connection commonly used in the prior art, etc., and therefore will not be described in detail in this embodiment.

[0018] The Swiss-type lathe for producing battery terminals provided in this embodiment aims to solve the fundamental contradiction in the prior art where the elimination of backlash in gear and rack transmission under high-frequency reciprocating conditions is difficult to match with bidirectional mechanical requirements.

[0019] Specifically, see Figure 1 , Figure 2 The Swiss-type lathe includes a base 1, a rack assembly 2, and a spindle 3. The rack assembly 2 is fixedly mounted on the base 1, and its length direction is parallel to the sliding direction of the spindle 3, providing a rigid transmission reference for the Z-axis feed. The rack assembly 2 has two back-to-back transmission tooth surfaces on both sides along its length direction. This double-tooth-surface layout is a key innovation of this embodiment, distinguishing it from traditional single-sided meshing gear racks. It spatially separates the driving function and backlash elimination function into two independent meshing interfaces, allowing the driving gear 4 to only transmit cutting power, while the backlash elimination gear 5 is dedicated to eliminating backlash. The two do not interfere with each other, fundamentally avoiding the load coupling and uneven wear problems caused by sharing the same tooth surface in traditional double-gear backlash elimination structures. The main shaft 3 is slidably mounted on the base 1, and a drive gear 4 and a backlash-eliminating gear 5 are mounted on the main shaft 3. The drive gear 4 is rotatably mounted on the main shaft 3 and meshes with one of the transmission tooth surfaces, undertaking the main power transmission during the feed cutting stage. The backlash-eliminating gear 5 is slidably mounted on the main shaft 3 along a direction perpendicular to the length of the rack assembly 2 and meshes with the other transmission tooth surface. Its sliding freedom ensures that the backlash-eliminating gear 5 can always be in contact with the tooth surface to maintain a backlash-free meshing state. This orthogonal sliding guide design makes the preload of the backlash-eliminating gear 5 perpendicular to the feed direction of the main shaft 3. The adjustment of the preload will not introduce additional axial force to interfere with the positioning accuracy of the main shaft 3, effectively ensuring the stability of key dimensions such as the height and position of the battery terminal sealing step.

[0020] Regarding the preload adjustment mechanism, see [link / reference]. Figure 2An elastic preload element 51 (such as a disc spring assembly, wave spring, or polyurethane elastomer) and a rigid limiting element 52 are provided between the main shaft 3 and the backlash-eliminating gear 5. The rigid limiting element 52 is slidably mounted on the main shaft 3, forming a mechanical setting reference for the magnitude of the preload force. The elastic preload element 51 is constrained between the backlash-eliminating gear 5 and the rigid limiting element 52, and its natural elastic force applies an elastic preload force pointing towards the corresponding transmission tooth surface to the backlash-eliminating gear 5 to continuously eliminate meshing backlash. The core improvement of this embodiment is that the compression amount of the elastic preload element 51 is changed by adjusting the position of the rigid limiting element 52 on the main shaft 3, thereby achieving continuous adjustment of the magnitude of the preload force. This design addresses the technical dilemma in the background technology that "a single constant preload cannot simultaneously meet the mechanical requirements of both the feed and retraction stages": during the feed cutting stage, the rigid limiter 52 can be adjusted to place the elastic preloader 51 in a high compression position, providing a large preload sufficient to resist intermittent cutting impact loads and preventing vibration and tooth surface damage caused by transient disengagement of the backlash-free gear 5; while during the retraction positioning stage, the rigid limiter 52 is switched to a low compression position, reducing the preload to a level that only needs to overcome weak friction and inertial forces, avoiding the sticky sliding effect and extended reversing settling time caused by the large preload being converted into additional static friction of the sliding pair.

[0021] It is worth noting that this embodiment specifically uses a backlash-eliminating gear 5 instead of a roller as the backlash elimination actuator, based on multiple technical considerations under the high-frequency reciprocating precision machining conditions of battery terminals. First, the roller and rack are a rolling friction pair with point or line contact, and their normal load-bearing capacity is limited by the Hertzian contact stress threshold. Under the transient impact load generated by intermittent cutting, they are prone to surface crushing, spalling, or plastic deformation, leading to rapid failure of the backlash elimination function. On the other hand, the backlash-eliminating gear 5 and the rack have involute tooth surface meshing, which is a surface contact transmission with multiple teeth participating simultaneously. The load distribution is uniform, and the impact resistance margin is much higher than that of the roller. It can withstand the peak cutting force during the feed stage for a long time without damage. Secondly, rollers can only provide unidirectional normal preload and cannot constrain the tangential degree of freedom within the rack tooth groove. At the moment of reversal, the sudden change in the direction of inertial force and friction can easily cause slight slippage or jumping, introducing uncontrollable positioning lag. The backlash-free gear 5, on the other hand, simultaneously restricts normal and tangential displacement through tooth profile geometric constraints, forming a true bidirectional backlash-free meshing, fundamentally eliminating the problem of excessive reversal clearance. Thirdly, rollers are extremely sensitive to the surface roughness, waviness, and installation straightness of the rack. Any microscopic morphological defects will directly translate into periodic vibration excitation, deteriorating the surface quality. The backlash-free gear 5, through the synergistic effect of tooth profile modification and elastic preload, can effectively filter out high-frequency disturbance components, improving motion stability and the surface finish of the sealing step. Finally, the internal clearance of the roller bearing increases with usage time, and the preload exhibits a non-linear decay trend, requiring frequent shutdowns for inspection and adjustment. The preload of the backlash-free gear 5, however, is independently set by an external elastic element, decoupled from the wear state of the gear body. As long as the tooth thickness does not reach its limit, the preload can be maintained stably for a long period, significantly reducing maintenance frequency and overall lifecycle operating costs. In summary, in specific application scenarios such as battery terminals where precision, cycle time, and reliability are all critically demanding, the backlash-free gear 5 outperforms the roller in terms of load-bearing capacity, motion constraint integrity, anti-interference capability, and maintenance economy. It is an indispensable key component for achieving high-performance adaptive preload control in this embodiment.

[0022] In a preferred embodiment, the spindle 3 is also equipped with a linear drive component (such as a micro servo cylinder, a stepper screw module, or a voice coil motor). The rigid limiter 52 is directly mounted on the moving end of the linear drive component, and the linear drive component drives the rigid limiter 52 to slide precisely on the spindle 3. According to the machining program instructions, the control system moves the rigid limiter 52 to the preset "feed position" during the feed cutting stage. At this time, the elastic preload 51 is in a high compression state, providing a large preload force sufficient to resist intermittent cutting impact loads, preventing vibration, noise, and pitting damage to the tooth surface caused by the transient disengagement of the backlash-free gear 5. During the retraction positioning stage, the rigid limiter 52 is quickly switched to the preset "retraction position". At this time, the compression of the elastic preload 51 decreases, and the preload force drops to a low level that only needs to overcome weak friction and inertial forces, avoiding the sticky sliding effect, extended reversing settling time, and excessive backlash caused by the large preload force being converted into additional static friction of the sliding pair. To ensure a strict timing match between changes in preload and the movement of spindle 3, high-response position sensors (such as photoelectric switches, Hall effect sensors, or inductive proximity switches) are installed at both the feed and retraction positions. These sensors detect the position of the rigid limiter 52 in real time and feed the signal back to the central controller. The controller then triggers the forward / reverse switching of the drive motor or updates the speed curve accordingly. This closed-loop coordinated linkage mechanism ensures that the preload adjustment is completed before or simultaneously with the reversing action of spindle 3, eliminating the risk of transient disengagement caused by starting cutting before the preload is in place. It also prevents motion lag caused by maintaining high preload during the retraction phase, accurately addressing the core pain point of dynamic mismatch between preload and motion state under high-frequency reversing cycles.

[0023] It is worth noting that, in order to further balance high reliability and low control complexity, this embodiment innovatively integrates a purely mechanical passive double wedge switching mechanism on the basis of the above-mentioned active linear drive adjustment scheme, as a redundant backup or an alternative execution path that can be operated independently.

[0024] See details below: Figure 3The base 1 is provided with a guide rail 6 for sliding guidance of the main shaft 3. A compression wedge 61 and a release wedge 62 are arranged on the guide rail 6 along the axial direction of the main shaft 3, and both are fixed at preset positions on the guide rail 6 as independent functional modules. The compression wedge 61 has a first wedge-shaped surface 63 facing the retraction direction of the main shaft 3, and the release wedge 62 has a second wedge-shaped surface 64 facing the feed direction of the main shaft 3. The two wedge-shaped surfaces are arranged opposite to each other, forming a symmetrical but functionally separated mechanical conversion interface. The rigid limiting member 52 has a first working surface 65 that slides with the first wedge-shaped surface 63, and a second working surface 66 that slides with the second wedge-shaped surface 64, correspondingly arranged on its outer periphery. This separate double-wedge block layout is another key innovation that distinguishes this embodiment from traditional single-unit asymmetric wedge blocks or spring-reset mechanisms: it completely decouples the two functions of "establishing high preload" and "releasing to low preload" into independent geometric entities, so that the preload establishment rate during the feeding stage (determined by the inclination angle of the first wedge surface 63) and the preload release rate during the retraction stage (determined by the inclination angle of the second wedge surface 64) can be independently optimized by replacing wedges with different angles. This completely eliminates the adjustment interlock defect in traditional structures where adjusting one end inevitably moves the other end, giving the process debugging a great degree of freedom. During the forward feed of the spindle 3, the first action surface 65 climbs along the compression wedge 61, converting the axial movement of the spindle 3 into the controlled radial displacement of the rigid limiting member 52, compressing the elastic preload member 51 to a high preload state. During the reverse retraction of the spindle 3, the second action surface 66 slides along the release wedge 62, causing the rigid limiting member 52 to reset under the residual elastic force of the elastic preload member 51 or the action of the auxiliary reset spring, and the preload smoothly decreases to a low value. The entire switching process is driven entirely by the reciprocating motion of the spindle 3 itself, without the need for external sensors, motors, or hydraulic sources. The change in preload state and the reversing action are naturally synchronized in timing, completely eliminating the millisecond-level communication delay or actuator response lag that may exist in the electronic control scheme, ensuring a high degree of consistency in the positioning accuracy of each reversing node. When the linear drive component temporarily fails due to fault, maintenance, or electromagnetic interference, this purely mechanical mechanism can seamlessly take over the preload switching function, ensuring continuous and uninterrupted operation of the equipment, reflecting the system-level safety design thinking of electromechanical complementarity and multiple redundancy.

[0025] To ensure the stability, repeatability, and process flexibility of the aforementioned dual-mode preload adjustment mechanism under long-term, high-frequency, and high-impact operating conditions, this embodiment also introduces a slot self-locking limiting structure and a modular adjustable installation design. A precision slot mating structure is provided between the rigid limiting member 52 and the main shaft 3. When the compression wedge 61 or the release wedge 62 drives the rigid limiting member 52 to move axially to the preset feed position or retraction position, the slot mating structure automatically engages to provide axial rigid limiting for the rigid limiting member 52. The slot adopts a detachable design of elastic positioning pin (or steel ball) and annular groove. The end of the positioning pin is precision ground into a conical or spherical shape. When the rigid limit member 52 is subjected to an axial thrust exceeding the preset disengagement threshold by the next wedge trigger, the positioning pin is forced to retract and automatically disengage from the groove. This effectively prevents the preload drift caused by the unexpected axial movement of the rigid limit member 52 under vibration and impact environments, and ensures that the limiting function does not hinder the subsequent normal preload switching cycle, significantly improving the repeatability and long-term reliability of preload switching. In addition, a precision adjustment groove (such as a T-slot or waist-shaped hole) is provided on the guide rail 6 along the axial direction. The compression wedge 61 and / or release wedge 62 are installed in the adjustment groove by high-strength fasteners. By loosening the fasteners and adjusting their locking position in the adjustment groove, the axial installation position of the wedge on the guide rail 6 can be steplessly changed. This modular and adjustable design gives the equipment significant process flexibility: when the production line switches to battery terminal products of different specifications and lengths, the operator can quickly and finely adjust the axial distance between the two wedges according to the process requirements of the new workpiece and the position of the reversing point, and accurately match the timing and range of the preload switching without replacing the entire set of guide rails, reprocessing the base or modifying the control program, which greatly reduces the downtime for model changeover, spare parts inventory costs and dependence on the skill level of the operators.

[0026] Finally, regarding the specific structure of the rack assembly 2, this embodiment provides two interchangeable implementation forms to adapt to different production scenarios.

[0027] In the first form, the rack assembly 2 is a single rack, with two transmission tooth surfaces integrally formed on the two opposite side walls along its own length. This integrated structure has extremely high overall rigidity and geometric consistency. The parallelism and symmetry of the two tooth surfaces are guaranteed by a single precision grinding process, eliminating the need for assembly and adjustment. It is particularly suitable for batch production lines with strict requirements for long-term precision maintenance and relatively fixed product specifications, and can effectively reduce meshing bias and local wear caused by the accumulation of errors in separate assembly.

[0028] In the second configuration, the rack assembly 2 adopts a split structure comprising two independent racks. These two racks are fixed side-by-side on the base 1 along a direction perpendicular to the length of the rack assembly 2, with their opposite sides forming two transmission tooth surfaces. This split structure allows for independent machining, heat treatment, and installation of the two racks. When one tooth surface wears or is damaged due to long-term unidirectional heavy-load cutting, only the corresponding rack needs to be replaced without scrapping the entire assembly, significantly reducing maintenance costs and spare parts inventory pressure. Furthermore, the tooth surface distance can be finely adjusted by adjusting the thickness of the shims between the two independent racks, providing an additional process window for assembly tolerance compensation and initial preload setting. This is particularly suitable for frequent model changes or trial production verification stages involving multiple product types and small batches. Both rack structures are seamlessly compatible with subsequent preload adjustment mechanisms, allowing users to flexibly choose based on their production line's precision level, maintenance strategy, and cost budget. However, compared to a single rack, it has the following significant drawbacks: First, the installation references of the two independent racks are separate, requiring separate alignment and positioning during assembly. Accumulated errors can easily lead to excessive parallelism and symmetry of the two tooth surfaces, causing meshing imbalance, local stress concentration, and accelerated wear. Its long-term accuracy retention is significantly weaker than that of a single rack. Second, the split splicing interface is prone to slight relative displacement or loosening under high-frequency impact loads. Even with high-strength fasteners and positioning pins, it is still difficult to completely eliminate the flexible links in the vibration transmission path, resulting in a decrease in the overall dynamic rigidity of the system and affecting the positioning stability and surface finish quality during high-speed reversal. Third, although the shim thickness adjustment between the two racks provides a process window, it also introduces additional human adjustment variables, which are highly dependent on the operator's skills, have a long debugging cycle, and are difficult to control in batch production. The initial setting of the preload is prone to dispersion due to assembly differences between batches, increasing the risk of quality fluctuations. Fourth, the split structure occupies more lateral space, which places higher demands on the width of the mounting surface of the base 1 and the layout of the guide rail 6, limiting its adaptability in compact equipment design. Therefore, the second type is more suitable for trial production and verification, small-batch multi-variety model changeover, or scenarios that are extremely sensitive to maintenance costs. However, in large-scale battery terminal production lines that pursue ultimate precision, high-speed stable operation, and long lifespan, the first type of single-cell rack and pinion should be given priority.

[0029] Of course, the above are just typical examples of the present invention. In addition, the present invention may have many other specific embodiments. All technical solutions formed by equivalent substitution or equivalent transformation fall within the scope of protection claimed by the present invention.

Claims

1. A Swiss-type machine for producing battery terminals, characterized in that, The device includes a base, a rack assembly, and a main shaft. The rack assembly is fixedly mounted on the base and has two back-to-back transmission tooth surfaces on both sides along its length direction. The length direction of the rack assembly is parallel to the sliding direction of the main shaft. The main shaft is slidably mounted on the base and has a drive gear and a backlash-eliminating gear. The drive gear is rotatably mounted on the main shaft and meshes with one of the transmission tooth surfaces. The backlash-eliminating gear is slidably mounted on the main shaft along a direction perpendicular to the length direction of the rack assembly and meshes with the other transmission tooth surface. An elastic preload and a rigid limiting member are provided between the main shaft and the backlash-eliminating gear. The rigid limiting member is slidably disposed on the main shaft. An elastic preload force is applied to the backlash-eliminating gear pointing towards the corresponding transmission tooth surface by the elastic preload to eliminate meshing backlash. Adjusting the position of the rigid limiting member on the spindle changes the compression of the elastic preload member, thereby adjusting the magnitude of the elastic preload force to adapt to the mechanical requirements of the feed and retraction stages respectively.

2. The Swiss-type lathe for producing battery terminals as described in claim 1, characterized in that, The rack assembly is a single rack, and the two transmission tooth surfaces are integrally formed on the two opposite side walls of the single rack along its own length direction.

3. The Swiss-type lathe for producing battery terminals as described in claim 1, characterized in that, The rack assembly includes two independent racks, which are fixedly arranged side by side on the base along a direction perpendicular to the length of the rack assembly, and the opposite sides of the two independent racks respectively form two transmission tooth surfaces.

4. The Swiss-type lathe for producing battery terminals as described in any one of claims 1 to 3, characterized in that, The main shaft is also provided with a linear drive component, and the rigid limiting component is installed on the moving end of the linear drive component; The rigid limiting component is driven by a linear drive component to slide on the main shaft to adjust the compression of the elastic preload component.

5. The Swiss-type lathe for producing battery terminals as described in claim 4, characterized in that, The main shaft is also equipped with a drive motor, and the output end of the drive motor is connected to the drive gear. The linear drive component moves the rigid limiter to a preset feed position during the feed phase and moves it to a preset retraction position during the retraction phase. Sensors are provided at both the feed position and the retraction position to detect the positioning status of the rigid limiter and provide feedback signals to control the forward and reverse switching of the drive motor, thereby achieving coordinated linkage between preload adjustment and spindle feed reversal.

6. The Swiss-type machine for producing battery terminals as described in any one of claims 1 to 3, characterized in that, The base is provided with a guide rail for sliding guidance of the spindle. A compression wedge and a release wedge are provided on the guide rail along the axial direction of the spindle. The compression wedge has a first wedge-shaped surface facing the spindle retraction direction, and the release wedge has a second wedge-shaped surface facing the spindle feed direction. The first wedge-shaped surface and the second wedge-shaped surface are arranged opposite to each other. The rigid limiting member is provided with a first working surface that slides with the first wedge-shaped surface and a second working surface that slides with the second wedge-shaped surface.

7. The Swiss-type machine for producing battery terminals as described in claim 6, characterized in that, A slotted engagement structure is provided between the rigid limiting component and the main shaft; When the compression wedge or the release wedge drives the rigid limiting member to move axially to a preset position, the slot mating structures engage with each other to limit the rigid limiting member.

8. The Swiss-type lathe for producing battery terminals as described in claim 6, characterized in that, An adjustment groove is provided on the guide rail along the axial direction. The compression wedge and / or release wedge are installed in the adjustment groove by fasteners. The locking position of the fasteners in the adjustment groove is adjusted to change the axial installation position of the compression wedge and / or release wedge on the guide rail.

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