High-precision and high-stability punch press

Abstract

The application relates to the field of mechanical pressure processing equipment, and provides a high-precision and high-stability punch. The punch comprises a machine body, a crankshaft, two sliders, a counterweight, a sliding block, an upper connecting rod, a lower connecting rod and a driving connecting rod. The crankshaft is arranged on the machine body; the sliders are arranged on the two sides of a transmission mechanism and horizontally slide with the machine body; the counterweight vertically slides with a top base above the transmission mechanism; the sliding block is arranged below the transmission mechanism and is used for mounting an upper die. The upper connecting rod connects the counterweight and the slider, the lower connecting rod connects the sliding block and the slider, and the driving connecting rod connects the crankshaft and the slider. The second ends of the three connecting rods are coaxially hinged with the slider through the same rotating shaft. The scheme effectively reduces vibration and friction, and improves the precision and stability of the punch.

Description

Technical Field

[0001] This application relates to the field of mechanical pressure processing equipment technology, and more specifically, to a high-precision and high-stability punch press. Background Technology

[0002] As a core pressure processing equipment in the field of mechanical manufacturing, the performance of a punch press directly determines the precision, production efficiency, and die life of stamped parts. In high-speed, high-precision stamping operations, the dynamic characteristics, thermal stability, guiding accuracy, lubrication and cooling effect, vibration reduction capability, and sealing performance of various moving parts of the punch press jointly affect the overall performance of the equipment. However, existing punch presses still have significant technical defects in many of these aspects, which urgently require systematic improvement.

[0003] In the transmission mechanism of a punch press, the slide block, as a key sliding component connecting the crankshaft and the connecting rod assembly, and the connecting rod, as the core component for transmitting power, are traditionally mostly made of a single piece of copper alloy. While copper alloys possess good self-lubricating and wear-resistant properties, their coefficient of thermal expansion is relatively high (approximately 17~20×10⁻⁶). -6 During prolonged high-speed operation of a punch press, the combined effects of frictional heat and ambient temperature changes cause significant thermal deformation of the slide and connecting rod, leading to drastic fluctuations in the clearance between the sliding mating surface and the guide seat, measured to be over 0.1 mm. This instability directly weakens the accuracy of the motion trajectory and severely interferes with the reliability of the lubrication system. The large clearance reserved at room temperature to avoid high-temperature seizure makes it difficult to establish a lubricating oil film at low temperatures or during startup, causing the slide and guide seat to be in a state of boundary lubrication or even dry friction for extended periods, exacerbating wear and potentially leading to severe failures such as sintering and scoring. For connecting rods, especially split or ball-joint structures, thermal deformation can easily cause out-of-roundness of the shaft hole or abnormal fit between the ball joint and the ball seat, affecting transmission accuracy.

[0004] The performance of the punch press slide guide structure has a decisive impact on stamping accuracy. Existing technologies mainly employ sliding bearings or ball bearings in conjunction with guide posts and bushings. Sliding bearings generate significant heat accumulation due to continuous sliding friction, leading to rapid material wear and even thermal deformation and jamming. While ordinary ball bearings introduce rolling friction, their point contact mechanism results in highly concentrated contact stress, making them prone to localized crushing or spalling under heavy impact, thus limiting their load-bearing capacity. Furthermore, the assembly clearance between the balls is difficult to precisely control, and asynchronous movement causes radial runout or wobbling of the guide post, failing to meet micron-level control requirements. In addition, in existing rolling guide designs, the cage of the rolling element must move synchronously with the guide post, its range of motion entirely limited by the guide bushing length. This prevents the effective stroke of the guide post from exceeding the guide bushing size, requiring the replacement of the entire guide bushing assembly when multiple stroke specifications are needed, a cumbersome process that severely restricts process adaptability. Some solutions attempt to improve friction through the rolling contact between the balls and the guide post / sleeve, but these have failed to solve the problems of limited stroke and insufficient load-bearing capacity.

[0005] In terms of slider thermal management, during continuous high-speed stamping operations, a large amount of heat generated by the friction between the die and the workpiece is conducted to the bottom of the slider through the mounting surface, causing a sharp rise in local temperature. Since sliders are generally made of cast iron or steel, which have a high coefficient of thermal expansion, uneven temperature distribution leads to significant thermal stress, resulting in overall or local deformation of the slider. This alters the fit clearance between the slider and the guide rail, affecting positioning accuracy to the point of jamming or accelerated wear. While existing technologies attempt to incorporate cooling chambers within the slider, such as storing coolant in a single chamber and using a top-in, bottom-out circulation method, there are significant limitations: the single chamber results in a simple coolant flow path, easily creating dead zones in corners and leading to uneven cooling; the actual heat distribution is not adequately considered, making it impossible to accurately guide the cooling medium to the bottom of the slider and high heat flux density areas such as the main ribs, resulting in low cooling efficiency; and the large through-holes for installing baffles weaken the slider's structural strength and increase the risk of leakage during long-term operation.

[0006] The lubrication system design of traditional punch presses suffers from fundamental flaws. Existing solutions rely on external pipelines to directly supply oil to surface friction points. This dispersed pipeline layout occupies valuable installation space and fails to adequately cover concealed structural areas such as the internal rotating shaft of the slide, the interface between the common hinge shaft and connecting rod sleeve, and the mating surfaces of guide posts and sleeves. This results in these critical friction pairs being chronically under-lubricated, easily leading to dry friction, accelerated component wear, and the induction of jamming failures. Simultaneously, the oil return path design is inefficient, causing oil to accumulate above the stamping area, increasing the risk of leakage and hindering heat dissipation. The entire system lacks dynamic monitoring and closed-loop control mechanisms for oil temperature, and temperature fluctuations directly weaken the lubricating film. For models equipped with counterweights, lubrication of the sliding surfaces between the counterweight and the machine body, as well as the dynamic balancing guide posts, is severely lacking. Furthermore, there is no systematic solution for coordinated lubrication with the crank mechanism, resulting in unstable counterweight movement and exacerbating overall machine vibration and noise.

[0007] In terms of vibration reduction and leveling, high-speed precision stamping presses inevitably generate strong impact vibrations during stamping operations. Existing anti-vibration foot devices mostly adopt a combination structure of springs and damping cavities, but their damping force cannot be adjusted after leaving the factory. This results in the vibration reduction performance being unable to adapt to changes in load, stamping frequency fluctuations, or vibration amplitude differences—excessive damping under light loads causes sluggish response, while insufficient damping under heavy loads intensifies vibration transmission. Leveling relies entirely on manual intervention, requiring the machine to be stopped and each screw to be tightened individually, a cumbersome and time-consuming process. Furthermore, it cannot dynamically maintain a level state during operation, and long-term use can easily lead to press tilting due to ground subsidence or mold changes, affecting processing consistency. The entire system lacks real-time sensing and active control capabilities, making it difficult to meet the stringent dynamic stability requirements of high-speed stamping processes.

[0008] Furthermore, regarding the sealing of the guide structure, to prevent external dust from entering the mating gap between the guide post and the guide sleeve, the conventional practice is to install a rubber oil seal at the end of the guide structure. The rubber oil seal forms a seal through the interference contact between its lip and the guide post surface. However, during high-speed reciprocating motion, frequent friction between the lip and the guide post generates a large amount of heat, accelerating the aging and hardening of the rubber material, gradually causing it to lose elasticity and significantly weakening its sealing performance. When the lubrication system provides insufficient oil or the quality of the lubricating oil deteriorates, there is a lack of sufficient lubrication film between the lip and the guide post, leading to a sharp increase in frictional resistance, causing high-frequency, harsh noises, interfering with the operating environment, and exacerbating equipment vibration. After long-term operation, the rubber oil seal experiences continuous wear, resulting in a widening sealing gap, severely degrading its dustproof capability. External dust then enters the guide sleeve, contaminating the lubricating medium and accelerating the wear of rolling elements, ultimately leading to decreased guiding accuracy and an increased equipment failure rate.

[0009] In summary, existing punch presses suffer from significant deficiencies in areas such as the thermal stability of the transmission mechanism, the accuracy and stroke adaptability of the guide structure, the thermal management of the slide block, the integration and cooling of the lubrication system, the proactiveness of vibration damping and leveling, and the durability of the sealing structure. These shortcomings are intertwined and collectively restrict the overall performance of punch presses under high-speed, high-precision, and high-load conditions. Therefore, a comprehensive technical solution that can systematically address these problems is urgently needed. Summary of the Invention

[0010] The purpose of this application is to provide a high-precision and high-stability punch press, which has the advantages of effectively reducing the vibration and friction of the transmission mechanism and improving the running accuracy and stability of the punch press.

[0011] This application provides a high-precision, high-stability punch press, the technical solution of which is as follows: include: body; The crankshaft is mounted on the machine body; Two sliders are respectively located on the left and right sides of the transmission mechanism and slide in cooperation with the machine body in the horizontal direction; The counterweight is positioned above the transmission mechanism and slides vertically with the top seat of the punch press. The slider, located below the transmission mechanism, is used to mount the punch die; The upper connecting rod has its first end hinged to the counterweight and its second end hinged to the slider. The lower connecting rod has its first end hinged to the slider and its second end hinged to the slide. The drive connecting rod has its first end connected to the crankshaft drive and its second end hinged to the slider; The second end of the upper connecting rod, the second end of the lower connecting rod, and the second end of the drive connecting rod are coaxially hinged to the shaft hole of the slide via the same rotating shaft.

[0012] Furthermore, this application also proposes that the slider includes: The slide body is made of alloy steel with a low coefficient of thermal expansion. The sliding mating surface is located on the outer side of the slider body; The shaft hole is formed on the slide body; The sliding mating surface and the inner wall of the shaft hole are provided with a sliding layer material with a low coefficient of friction.

[0013] Furthermore, this application also proposes that the sliding layer material and the slide body are a composite structure integrally cast, or that the sliding layer material is fixed to the slide body in a separate connection manner; the average linear expansion coefficient of the low thermal expansion coefficient alloy steel in the range of 20~60℃ is not greater than 2×10 -6 / K.

[0014] Furthermore, this application also proposes that at least one of the upper connecting rod, lower connecting rod, and drive connecting rod has a connecting rod body made of alloy steel with a low coefficient of thermal expansion, and the inner wall of the connecting rod shaft hole of the connecting rod body is provided with a sliding layer material with a low coefficient of friction; the average linear expansion coefficient of the low coefficient of thermal expansion alloy steel in the range of 20~60℃ is not greater than 2×10 -6 / K.

[0015] Furthermore, this application proposes that the connecting rod is a double-hole connecting rod with shaft holes at both ends, or a ball-end connecting rod with a connecting rod shaft hole at one end and a ball head at the other end; the second end of the double-hole connecting rod adopts a split structure or a clamping structure; the split structure includes a connecting rod body end and a detachably connected end cap, which is fixedly connected by fasteners; the clamping structure has an axially penetrating opening in the circumferential direction of the shaft hole, and connecting holes are provided on both sides of the opening, and the radial clamping force of the shaft hole is adjusted by applying torque through the connecting holes with fasteners.

[0016] Furthermore, this application also proposes a guide structure disposed between the punch press frame and the slide block, the guide structure comprising: The guide post has multiple axially extending cross-sections on its outer wall; Guide sleeve, fitted over the outside of the guide post; A rolling component is disposed within the guide sleeve and makes rolling contact with the guide post; The guide seat is fixedly installed at the end of the guide sleeve and is used to limit the axial movement stroke of the guide post.

[0017] Preferably, the cut surface is a plane and is evenly or unevenly distributed along the circumference of the guide post; the guide post has an upper section with a larger diameter and a lower section with a smaller diameter, and an annular step surface is formed between the upper section and the lower section; the cut surface is disposed on the outer peripheral wall of the lower section; the guide sleeve is fitted onto the outside of the lower section.

[0018] Preferably, a guide seat is fixedly provided at the end of the guide sleeve. The guide seat has an inner cavity for accommodating the upper section of the guide post and allowing the guide post to move axially up and down within the inner cavity. A limiting structure is provided on the guide seat, which cooperates with the annular stepped surface to limit the maximum downward stroke of the guide post. The limiting structure is an annular retaining ring, which is fixedly installed on the inner wall of the annular opening at the lower end of the guide seat.

[0019] Furthermore, this application also proposes that the guide structure is a high-precision guide structure, and the rolling assembly includes a bearing cage and multiple rollers. The bearing cage is axially movable and disposed within the guide sleeve. The multiple rollers are mounted on the bearing cage, and each roller corresponds to a tangential surface of the guide post and makes rolling contact. The rollers are cylindrical, and their axial direction is perpendicular to the axial direction of the guide post.

[0020] Furthermore, this application also proposes that the guide structure is an adjustable stroke guide structure, the rolling assembly includes a base, the base is fixedly disposed in the guide sleeve, the base is provided with a circulating raceway, multiple rollers are installed in the circulating raceway and can circulate along the circulating raceway; the base is elongated, and multiple mounting slots are arranged at intervals along the axial direction on it, each mounting slot is provided with a circulating raceway body, each circulating raceway body and the rollers therein form a rolling support unit, and multiple rolling support units are distributed at intervals along the axial direction and jointly roll in contact with the corresponding tangential surface.

[0021] Furthermore, this application also proposes that the guide structure is a combined guide structure, which further includes a copper sleeve fixedly disposed within the guide sleeve, the copper sleeve slidingly engaging with the guide post; the rolling assembly includes a guide sleeve body, a retainer and multiple balls, the guide sleeve body is fixed within the guide sleeve and located below the copper sleeve, an annular gap is formed between the guide sleeve body and the guide post, the retainer is slidably disposed within the annular gap along the axial direction, and multiple balls are mounted on the retainer, with the outer circumferential surface of each ball making rolling contact with the inner wall of the guide sleeve body and the outer wall of the guide post respectively.

[0022] Furthermore, the upper end of the copper sleeve has a flange extending radially outward, the flange being mounted on the cavity end face of the guide sleeve; a cap is fixedly provided at the end of the guide sleeve, the cap pressing against the upper surface of the flange to restrict the axial displacement of the copper sleeve and the rolling assembly; sealing rings are provided between the upper end of the copper sleeve and the inner wall of the cavity of the guide sleeve, and between the upper end of the copper sleeve and the guide post, the cap pressing the sealing rings into the sealing cavity opened at the upper end of the copper sleeve; a retaining ring is provided at the lower end of the mounting cavity of the guide sleeve, the lower end of the guide sleeve body abuts against the retaining ring, the retainer and its balls are located between the retaining ring and the lower end face of the copper sleeve, and can slide axially.

[0023] Furthermore, the copper sleeve has an oil hole that connects its inner and outer walls, and the guide sleeve has an oil inlet hole and an oil return hole. The oil inlet hole and the oil return hole are respectively connected to the oil hole of the copper sleeve, and the oil inlet hole and the oil return hole are located at different positions in the axial direction of the copper sleeve to form a lubricating oil circulation path.

[0024] Furthermore, this application also proposes that the slider is an integrally formed silicon carbide particle-reinforced aluminum matrix composite slider, and the punch press also includes an oil cooling channel disposed inside the slider. The oil cooling channel includes at least one oil passage channel opened inside the slider and located directly below the main rib of the slider. The two ends of the oil passage channel extend to the side of the slider and respectively form an oil inlet and an oil outlet.

[0025] Furthermore, this application also proposes that the slider includes an upper plate, a lower plate, and multiple slider main ribs connecting the upper plate and the lower plate, the lower plate being used to install the punch die; the oil cooling channel is located above the lower plate and directly below each slider main rib, and is arranged along the length direction of the slider main rib; the oil cooling channel is a unidirectional oil passage or a detour oil passage.

[0026] Furthermore, this application also proposes a lubrication and temperature control oil circuit system integrated into the fuselage, the lubrication and temperature control oil circuit system comprising: The oil storage chamber located in the fuselage and the oil passage inside the longitudinal support beam connected to the oil storage chamber; Oil pump, distributor, and multiple oil supply branches; The oil pump is used to pump oil from the oil reservoir to the distributor; The distributor delivers oil to the following locations via oil supply branches: (i) The moving parts of the crank mechanism, used for spray lubrication; (ii) The connection between the crankshaft and the drive connecting rod; (iii) The sliding surface of the slide, the common hinge axis, and the connection point between the common hinge axis and the second end of each link; (iv) Between the guide post and the guide sleeve; After the oil collects above the stamping area, it flows back to the oil storage chamber through the oil passage inside the longitudinal support beam.

[0027] Furthermore, this application also proposes that the constant temperature lubrication oil circuit system further includes an oil cooler, which is circulatedly connected to the oil storage chamber; the first oil supply branch of the distributor is connected to the top of the dynamic balance guide column, and the oil is sprayed onto the crankshaft, upper connecting rod, lower connecting rod and drive connecting rod of the crank mechanism through the internal oil passage of the dynamic balance guide column; the second oil supply branch of the distributor is connected to the crankshaft, and the oil is transported to the sleeve joint between the crankshaft and the drive connecting rod through the internal oil passage of the crankshaft to form pressure lubrication; the third oil supply branch of the distributor is connected to the sliding surface of the slide, and the oil is transported to the common hinge shaft through the internal oil passage of the slide, the common hinge shaft is provided with an oil passage for transporting the oil to the respective sleeve joints between the common hinge shaft and the upper connecting rod, lower connecting rod and the second end of the drive connecting rod; the fourth oil supply branch of the distributor is connected between the guide column and the guide sleeve to form a sliding bearing lubrication interface.

[0028] Furthermore, this application also proposes a vibration damping system located at the bottom of the punch press body, comprising four air cushion anti-vibration feet, respectively located at the four corners of the punch press body; each air cushion anti-vibration foot includes: Base plate and top plate; A gas spring is installed between the bottom plate and the top plate, with its upper and lower ends connected to the bottom plate and the top plate respectively. Multiple damping devices are distributed between the bottom plate and the top plate. Each damping device includes: Damping cylinder, mounted on the lower end face of the top plate; A pair of damping mating plates are fixed to the upper end face of the base plate, and the damping cylinder is located between the two pairs of damping mating plates; The damping cylinder is a bidirectional output cylinder, with clamping components at its two output ends. The damping cylinder drives the clamping components to move outward and press against the corresponding damping mating plate, thereby generating damping force.

[0029] Furthermore, this application also proposes that the air cushion shock-absorbing foot further includes an automatic inflation / deflation control mechanism, which includes: Mounting bracket fixed to the lower end face of the top plate; A trigger block that is adjustable in height is mounted on a mounting frame. The trigger block has a first trigger part and a second trigger part that are arranged opposite to each other in the vertical direction. The displacement sensor is mounted on one of the damping mating plates, and the trigger end of the displacement sensor is located between the first trigger part and the second trigger part; When the bottom plate and the top plate move relative to each other, the trigger end of the displacement sensor contacts the first trigger part or the second trigger part and triggers a signal, which is used to control the inflation or deflation of the gas spring. When the punch press body tilts due to different die weights or center of gravity deviation after the punch press changes its stamping die, the automatic inflation and deflation control mechanism independently adjusts the air pressure of the air springs of each air cushion anti-vibration foot to automatically restore the punch press body to a horizontal position.

[0030] Furthermore, this application also proposes a sealing structure disposed at the end of the guide structure. The sealing structure is a glass fiber dust seal, which is a glass fiber material impregnated with grease. It is installed at the opening of the upper inner cavity of the guide seat, and the inner end of the glass fiber dust seal is in sealing sliding contact with the guide post.

[0031] Furthermore, this application also proposes that it includes a pressure ring, which is fixedly disposed on the upper end of the guide seat and presses the glass fiber dust seal tightly at the opening.

[0032] As can be seen from the above, the high-precision and high-stability punch press provided in this application includes components such as a machine body, crankshaft, slide, counterweight, slider, and connecting rod. The second ends of the upper connecting rod, lower connecting rod, and drive connecting rod are coaxially hinged to the shaft hole of the slide through the same rotating shaft. Through the above-mentioned transmission mechanism design, the friction and vibration of moving parts are effectively reduced, and the running accuracy and stability of the punch press are improved. It has the advantages of effectively reducing the vibration and friction of the transmission mechanism and improving the running accuracy and stability of the punch press. Attached Figure Description

[0033] Figure 1 This application provides a schematic diagram of the transmission structure of a high-precision and high-stability punch press.

[0034] Figure 2 This application provides a schematic diagram of the internal oil circuit of a high-precision and high-stability punch press.

[0035] Figure 3 for Figure 1 BB cross-sectional view.

[0036] Figure 4 This is a schematic diagram of the structure of a glider.

[0037] Figure 5 This is a schematic diagram of a ball-joint linkage.

[0038] Figure 6 This is a schematic diagram of the first split structure of a dual-axis bore connecting rod.

[0039] Figure 7 This is a schematic diagram of the second split structure of a dual-axis bore connecting rod.

[0040] Figure 8 This is a schematic diagram of a clamp-type structure for a dual-axis hole connecting rod.

[0041] Figure 9 This is a cross-sectional schematic diagram of a high-precision guide structure.

[0042] Figure 10 This is a schematic diagram showing the cooperation between the guide post and the rolling assembly in a high-precision guide structure.

[0043] Figure 11 This is a cross-sectional schematic diagram of an adjustable travel guide structure.

[0044] Figure 12 This is a schematic diagram showing the fit between the guide sleeve and the rolling assembly of the adjustable stroke guide structure.

[0045] Figure 13 This is a schematic diagram of the rolling component in an adjustable travel guide structure.

[0046] Figure 14 This is a cross-sectional schematic diagram of a combined guide structure.

[0047] Figure 15 This is a schematic diagram of the slider installation.

[0048] Figure 16 This is a longitudinal cross-sectional view of the slider.

[0049] Figure 17 This is a cross-sectional view of the slider.

[0050] Figure 18 This is a 3D diagram of an air cushion shock-absorbing foot.

[0051] Figure 19 This is a side view of the air cushion shockproof foot.

[0052] Figure 20 This is a cross-sectional view of the air cushion shock-absorbing foot.

[0053] Figure 21 for Figure 20 Enlarged view of part A.

[0054] Figure 22 This is a schematic diagram of a machine tool with four air cushion anti-vibration feet.

[0055] Figure 23 A comparison diagram of the slider stroke-crank angle motion curves of a general crank-connecting rod mechanism and the multi-link mechanism of this invention. Detailed Implementation

[0056] The technical solutions of this application will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are merely some embodiments of this application, and not all embodiments. The components of this application described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of this application provided in the accompanying drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without inventive effort are within the scope of protection of this application.

[0057] It should be noted that similar reference numerals and letters in the following figures indicate similar items; therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures. Furthermore, in the description of this application, terms such as "first," "second," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0058] In high-speed, high-precision stamping operations, traditional punch presses are susceptible to thermal deformation of transmission mechanism components, leading to unstable clearances and consequently affecting stamping accuracy and lubrication. Simultaneously, existing guide structures suffer from insufficient load-bearing capacity and stroke adaptability, uneven slide thermal management, incomplete lubrication system coverage, lack of adaptive vibration damping and leveling, and poor durability of sealing structures, all of which collectively restrict the overall performance of the equipment.

[0059] like Figure 1-22 As shown, this application proposes a high-precision, high-stability punch press, comprising: Fuselage 1; Crankshaft 2 is mounted on the body 1; Two sliders 3 are respectively located on the left and right sides of the transmission mechanism and slide in cooperation with the body 1 in the horizontal direction; The counterweight 12 is positioned above the transmission mechanism and slides vertically with the top seat 5 of the punch press. Slider 6, located below the transmission mechanism, is used to mount the punch die; The upper connecting rod 7 has its first end hinged to the counterweight 12 and its second end hinged to the slider 3. The lower connecting rod 8 has its first end hinged to the slider 6 and its second end hinged to the slider 3; The drive link 9 has its first end connected to the crankshaft 2 and its second end hinged to the slider 3. The second end of the upper connecting rod 7, the second end of the lower connecting rod 8, and the second end of the driving connecting rod 9 are coaxially hinged to the shaft hole 11 of the slider 3 via the same rotating shaft 10.

[0060] To facilitate understanding of the technical solution in this embodiment, some key terms involved are explained below: The machine body 1 is the main structure of the punch press, which is designed to bear and support all moving parts and transmission mechanisms, and to provide overall rigidity and stability.

[0061] The crankshaft 2 is the core component of the punch press power transmission system. Its function is to convert the externally input rotational power into periodic reciprocating motion, and then transmit the motion to the subsequent mechanism through the drive link 9.

[0062] The slider 3 is an important intermediate component in the transmission mechanism, which is configured to slide horizontally on the body 1. As the convergence point of multiple links, the slider 3 is hinged to the upper link 7, the lower link 8, and the drive link 9 through its internal shaft hole 11, thereby coordinating the movement of these links.

[0063] The counterweight 12 is positioned above the transmission mechanism and slides vertically with the top seat 5 of the punch press. Its main function is to balance the inertial forces of the moving parts of the punch press, thereby reducing the vibration and impact generated during high-speed operation of the entire machine.

[0064] The slider 6 is the component of the punch press that directly performs the stamping operation. It is located below the transmission mechanism and provides an interface for mounting the punch press die. Guided by the guide mechanism, the slider 6 performs precise vertical reciprocating motion to complete the stamping process of the workpiece.

[0065] The upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 are the key force-transmitting components of the punch press linkage mechanism. The upper connecting rod 7 connects the counterweight 12 and the slide 3, the lower connecting rod 8 connects the slider 6 and the slide 3, and the drive connecting rod 9 connects the crankshaft 2 and the slide 3. These connecting rods achieve motion transmission and conversion through hinges.

[0066] Coaxial hinge refers to the fact that the hinge points of multiple components share the same pivot 10, allowing these components to rotate relative to each other around this common axis. In this embodiment, the second end of the upper connecting rod 7, the second end of the lower connecting rod 8, and the second end of the drive connecting rod 9 are all coaxially hinged to the shaft hole 11 of the slider 3 through the same pivot 10, ensuring the compactness of the transmission mechanism and the coordination of movement.

[0067] The technical solution of this application will be described in detail below with reference to specific embodiments.

[0068] The punch press includes a frame 1, which serves as the skeleton of the equipment and is typically made of cast iron or welded steel. Its internal space is rationally planned to accommodate the transmission mechanism and other functional components. The frame 1 is designed to have sufficient rigidity and strength to withstand the enormous impact loads generated during the punching process.

[0069] The crankshaft 2 is housed inside the machine body 1 and is fixed to the machine body 1 by bearing housings. The crankshaft 2 is typically made of high-strength alloy steel and is precision-machined to ensure its rotational accuracy. The rotational motion of the crankshaft 2 is the power source for the entire stamping process.

[0070] Two slides 3 are respectively disposed on the left and right sides of the transmission mechanism and slide in cooperation with the body 1 in the horizontal direction. These slides 3 are usually made of wear-resistant materials, such as bronze alloy or surface-hardened steel. The sliding contact surface 14 between the slides 3 and the body 1 can be lubricated by conventional oil film lubrication or solid lubrication to reduce frictional resistance.

[0071] The counterweight 12 is positioned above the transmission mechanism and slides vertically against the top seat 5 of the punch press. The counterweight 12 is typically made of cast iron or steel, and its mass is precisely calculated to balance the inertial forces of the moving parts. The sliding fit between the counterweight 12 and the top seat 5 can employ a conventional structure of guide rails and sliders 6, maintaining smooth movement through periodic application of grease or lubricating oil.

[0072] The slider 6 is positioned below the transmission mechanism and is used to mount the punch die. This slider 6 is typically made of cast iron or steel, either integrally cast or welded, and has mounting holes or T-slots at its bottom for fixing the upper die. The slider 6 reciprocates vertically during the stamping process, and its motion accuracy directly affects the quality of the stamped part.

[0073] The upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 are key components connecting the aforementioned main moving parts. These connecting rods are typically forged or cast from high-strength steel, and have shaft holes 11 or ball joints 22 at both ends for hinged connection to other components. For example, the first end of the upper connecting rod 7 can be hinged to the counterweight 12 via a pin, and its second end can be hinged to the slider 3 via a pin. The first end of the lower connecting rod 8 can be hinged to the slider 6 via a pin, and its second end can be hinged to the slider 3 via a pin. The first end of the drive connecting rod 9 can be connected to the crank pin of the crankshaft 2 via a bearing drive, and its second end can be hinged to the slider 3 via a pin.

[0074] The second ends of the upper connecting rod 7, the lower connecting rod 8, and the drive connecting rod 9 are coaxially hinged to the shaft hole 11 of the slide 3 via the same rotating shaft 10. This means that the ends of these three connecting rods are connected to a common rotating shaft 10, which is then inserted into a shaft hole 11 on the slide 3. This coaxial hinge can be achieved by using a solid pin passing through the shaft holes 11 of all the connecting rods and the shaft hole 11 of the slide 3, and securing it with retaining rings or nuts at both ends. This structure ensures that multiple connecting rods rotate around a common center in the same plane, thereby achieving coordinated motion transmission.

[0075] This application optimizes the transmission mechanism of the punch press, particularly by coaxially hinged the second ends of the upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 to the shaft hole 11 of the slide 3 via the same rotating shaft 10, effectively improving the motion accuracy and stability of the punch press. This structural design makes the transmission path more compact, reducing the accumulation of motion backlash, thereby enabling more precise control of the movement trajectory of the slide 6 in high-speed stamping operations. As a result, the machining accuracy of the stamped parts is improved, while vibration and noise caused by instability in the transmission mechanism are reduced, extending the service life of the equipment.

[0076] In the above scheme, the slide 3, as a key moving component, generates a large amount of heat due to friction at its sliding mating surface 14 and shaft hole 11 during high-speed, high-load stamping processes. Simultaneously, changes in the working environment temperature of the press also cause thermal expansion of the slide 3. These thermal effects may cause slight changes in the dimensions of the slide 3, thereby affecting its fit accuracy with the machine body 1 and the linkage mechanism, leading to decreased stamping accuracy, accelerated component wear, and ultimately affecting the overall stability and service life of the press.

[0077] The beneficial effects of this scheme are explained below with reference to the motion curves in the attached diagram. Figure 23 A comparison of the slider stroke-crank angle motion curves of a general crank-connecting rod mechanism and the multi-link mechanism of this invention is shown. The horizontal axis represents the crank angle (0°~360°), and the vertical axis represents the slider 6 stroke (mm). The red line represents the motion curve of the general crank-connecting rod mechanism, and the blue line represents the motion curve of the multi-link mechanism of this invention. The curve shape comparison shows that the blue curve exhibits a smoother transition near the bottom dead center (180°)—its rate of velocity change is significantly lower than that of the red curve, forming a wider low-speed motion range. This motion characteristic effectively extends the dwell time of slider 6 in the bottom dead center region, thereby optimizing the pressure maintenance effect during the pressure holding stage. Based on kinematic principles, this smooth low-speed transition characteristic can reduce the impact of mechanism motion, reduce elastic deformation fluctuations during the molding process, and ultimately improve the dimensional accuracy of the product by improving the uniformity of pressure transmission.

[0078] like Figure 4 As shown, this application further proposes that the slide 3 includes: a slide body 13, the slide body 13 being made of alloy steel with a low coefficient of thermal expansion; a sliding mating surface 14, disposed on the outer side of the slide body 13; and a shaft hole 11, formed on the slide body 13; wherein, the sliding mating surface 14 and the inner wall of the shaft hole 11 are provided with a sliding layer material with a low coefficient of friction.

[0079] Specifically, the slide body 13 is the core component of the punch press that enables horizontal reciprocating motion. It bears the force and torque transmitted by the connecting rod and guides the slide block 6 to perform precise punching actions. The slide body 13 is typically a one-piece molded block or frame structure, and its interior can be designed with reinforcing ribs or lightweight holes to reduce its weight while ensuring strength. Its external dimensions and internal structure must precisely match those of the machine body 1, connecting rod, shaft hole 11, and other components. To address thermal expansion, the slide body 13 is made of low thermal expansion coefficient alloy steel. This type of alloy steel is a special alloy material with minimal dimensional change when the temperature changes. Its main characteristic is a low coefficient of linear expansion, enabling it to maintain dimensional stability over a wide temperature range. For example, by precisely controlling the proportions of alloying elements (such as nickel, cobalt, chromium, molybdenum, etc.) and heat treatment processes, Invar or similar high-nickel alloy steels can be obtained. Using such materials effectively suppresses dimensional expansion caused by temperature increases, thereby maintaining the geometric accuracy of the punch press.

[0080] The sliding mating surface 14 is the surface where the slide body 13 and the body 1 or other fixed components make relative sliding contact. These surfaces need to withstand high pressure and high-speed sliding, and are the main areas where friction and wear occur. The sliding mating surface 14 is usually a plane or curved surface that has been precision machined (such as grinding or lapping) to ensure uniform contact and stable sliding with the mating components. Its surface roughness, flatness, and other geometric accuracy requirements are extremely high to reduce frictional resistance and improve motion accuracy. The shaft hole 11 is a through hole opened on the slide body 13 to accommodate the rotating shaft 10 and realize the hinged connection between the slide 3 and the upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9. The accuracy of the shaft hole 11 directly affects the motion accuracy and force transmission efficiency of the linkage mechanism. The shaft hole 11 is usually machined by precision boring, honing, and other processes to ensure that its roundness, cylindricity, surface roughness, and clearance with the mating rotating shaft 10 meet high precision requirements.

[0081] To further reduce friction and wear, a low-friction coefficient sliding layer material is provided between the sliding mating surface 14 and the inner wall of the shaft hole 11. This sliding layer material is a material with excellent anti-friction properties and is typically applied to the sliding mating surface 14 and the inner wall of the shaft hole 11 in the form of a coating, bushing, or composite structure to reduce frictional resistance, reduce wear, extend component life, and suppress heat generation. For example, a bushing with low-friction properties can be pressed into or bonded into the shaft hole 11, such as a bronze alloy bushing, a polymer bushing (e.g., PA, POM, UHMW-PE, etc.), or a composite material bushing. Alternatively, the low-friction material can be integrally formed with the slider body 13 through casting, sintering, or other methods to create a composite structure, or a porous material can be used as the sliding layer and impregnated with a lubricant to form a self-lubricating structure.

[0082] Through the above technical solution, the slide body 13 is made of alloy steel with a low coefficient of thermal expansion, and a sliding layer material with a low coefficient of friction is provided on the sliding mating surface 14 and the inner wall of the shaft hole 11. This application effectively solves the problem of thermal expansion of the slide 3 caused by frictional heat generation and changes in ambient temperature during high-speed, high-load operation of the punch press. The use of alloy steel with a low coefficient of thermal expansion inherently suppresses the dimensional changes of the slide body 13 when the temperature rises, ensuring that the fit clearance between the slide 3 and the machine body 1 and the linkage mechanism always remains within the design tolerance range, thereby maintaining the motion accuracy and stamping accuracy of the punch press. At the same time, the application of the low coefficient of friction sliding layer material significantly reduces the frictional resistance at the sliding mating surface 14 and the shaft hole 11, reduces the energy loss and heat generation of the moving pair, further mitigates the thermal expansion effect, and effectively suppresses the wear of components, extending service life. This solution, which combines material property optimization and surface engineering treatment, enables the punch press to maintain excellent geometric accuracy and motion stability even under long-term continuous operation or large fluctuations in ambient temperature, significantly improving the overall performance and reliability of the punch press.

[0083] In a specific implementation, the sliding layer material and the slider body 13 are a composite structure integrally cast, or the sliding layer material is fixed to the slider body 13 in a separate connection manner; the low thermal expansion coefficient alloy steel has an average linear expansion coefficient of no more than 2×10⁻⁶ in the range of 20~60℃. -6 / K.

[0084] Regarding the composite structure where the sliding layer material and the slide body 13 are integrally cast, specifically, this means that during the manufacturing of the slide body 13, the sliding layer material and the slide body 13 material are melted and solidified into a single integral structure through a casting process. For example, during the casting of the slide body 13, a material with a low coefficient of friction can be cast together as an inner lining or surface layer to form a metallurgical bond, thereby ensuring extremely high bonding strength and stability between the sliding layer and the slide body 13, effectively avoiding interlayer peeling or detachment that may occur during use.

[0085] Alternatively, the sliding layer material can also be fixed to the slider body 13 in a separate connection manner. Specifically, this method involves pre-preparing the sliding layer material as an independent component, and then securely installing it to the slider body 13 through mechanical connections (such as bolts, rivets, clips, etc.), adhesive bonding (using high-performance structural adhesives), or thermal connections (such as brazing, diffusion welding, etc.). This separate connection method provides greater design flexibility, facilitating material selection and subsequent maintenance and replacement.

[0086] Furthermore, to further ensure the accuracy and stability of the punch press, the average linear expansion coefficient of the low thermal expansion coefficient alloy steel in the range of 20~60℃ is limited to no more than 2×10. -6 / K. This means that within the typical operating temperature range of the punch press, the dimensional changes of the material of the slide body 13 are minimal. For example, the low thermal expansion coefficient alloy steel can be an iron-nickel based low expansion alloy, such as 4J32 (Fe-32Ni-4Co-0.6Cu) or 4J50 (Fe-50Ni), etc. Among them, the average linear expansion coefficient of the 4J32 alloy can be as low as 0.6×10 in the range of 20~60℃. -6 / K, satisfying no greater than 2×10 -6 / K requirements. Precise control of the material's thermal expansion coefficient effectively suppresses minor deformations of the slider 3 caused by temperature fluctuations during operation, thus ensuring that the sliding fit clearance between the slider 3 and the machine body 1 remains within a very small tolerance range, providing a solid foundation for dimensional stability in high-precision stamping operations. Compared to conventional copper alloys (expansion coefficient approximately 17~20×10⁻⁶), ... -6 Compared to / K), the thermal deformation is reduced by about 50% to 60%, thereby effectively reducing the fluctuation of the fit clearance.

[0087] The above technical solution effectively solves the problem of weak bonding between the sliding layer material and the slide body 13 by fixing them together through integral casting or separate connection, ensuring the long-term stability and reliability of the sliding fit during stamping. Simultaneously, by precisely limiting the average linear expansion coefficient of the low thermal expansion coefficient alloy steel within a specific temperature range to no more than 2 × 10⁻⁶, the solution ensures the long-term stability and reliability of the sliding fit. -6 / K significantly reduces the dimensional deformation of the slide body 13 caused by temperature changes, thereby ensuring the geometric accuracy and motion stability of the press in high-precision stamping operations. This combination method and material selection enable the slide 3 to maintain its sliding performance and structural integrity when subjected to high-frequency, high-load impacts, significantly improving the overall accuracy and stability of the press and reducing processing errors and equipment wear caused by thermal deformation.

[0088] In a further preferred embodiment, at least one of the upper connecting rod 7, the lower connecting rod 8, and the drive connecting rod 9 has a connecting rod body made of alloy steel with a low coefficient of thermal expansion, and the inner wall of the connecting rod shaft hole 21 of the connecting rod body is provided with a sliding layer material with a low coefficient of friction; the average linear expansion coefficient of the low coefficient of thermal expansion alloy steel in the range of 20~60℃ is not greater than 2×10. -6 / K.

[0089] The connecting rod body is the core load-bearing component in the punch press transmission mechanism, and its dimensional stability is crucial to the punch press's accuracy. The connecting rod body is manufactured using alloy steel with a low coefficient of thermal expansion to minimize dimensional expansion or contraction caused by changes in operating temperature. This material typically has a special alloy composition and heat treatment process, such as nickel-based alloys or specific high-strength tool steels, whose average coefficient of linear expansion within a certain temperature range (e.g., 20~60℃) is much lower than that of ordinary steel. By selecting such materials, deformation of the connecting rod due to temperature increases during operation can be effectively suppressed, thereby ensuring the geometric accuracy and motion trajectory stability of the transmission mechanism. The connecting rod shaft hole 21 is the key part where it hinges to the rotating shaft 10 or other connecting parts. A sliding layer material with a low coefficient of friction is provided on the inner wall of this connecting rod shaft hole 21, which can significantly reduce the frictional resistance between the moving pairs. This sliding layer material can be a self-lubricating polymer (such as polytetrafluoroethylene and its composites), oil-impregnated sintered metal, or a composite coating with a special surface treatment. This sliding layer reduces energy loss during movement, lowers frictional heat generation, and effectively inhibits wear, thereby extending the service life of the connecting rod and related hinge components, and ensuring smooth operation and high-precision positioning of the transmission mechanism. The low thermal expansion coefficient alloy steel has an average linear expansion coefficient of no more than 2×10⁻⁶ within the temperature range of 20~60℃. -6 / K, this specific parameter defines the performance characteristics of the selected low thermal expansion coefficient alloy steel. 20~60℃ is the typical temperature range that a punch press may experience under normal operating conditions. The average linear expansion coefficient is limited to no more than 2×10⁻⁶. -6 / K means that within this temperature range, the change in connecting rod length is extremely small. This stringent material performance requirement is a key factor in ensuring the high precision and stability of the press during actual operation, effectively avoiding cumulative errors caused by thermal expansion. For specific material options, please refer to the description of the low thermal expansion coefficient alloy steel for slide 3 above.

[0090] By employing the aforementioned technical solution, the main body of at least one of the upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 is made of alloy steel with a low coefficient of thermal expansion, and a sliding layer material with a low coefficient of friction is applied to the inner wall of the connecting rod shaft hole 21. This significantly improves the overall performance of the punch press. Specifically, the use of alloy steel with a low coefficient of thermal expansion effectively suppresses the dimensional deformation of the connecting rod under varying operating temperatures, thereby ensuring the geometric accuracy and stability of the motion trajectory of the transmission mechanism and avoiding the accumulation of transmission errors caused by thermal expansion. Simultaneously, the low coefficient of friction sliding layer material on the inner wall of the connecting rod shaft hole 21 significantly reduces the frictional resistance between the connecting rod and the hinge, reducing energy loss and frictional heat generation, effectively suppressing wear, extending the service life of components, and ensuring the smoothness and high precision of the transmission process. Therefore, this solution, through the synergistic effect of materials and surface treatment, jointly solves the problem of decreased precision and insufficient stability of the connecting rod due to thermal expansion and frictional wear during long-term operation, thus ensuring the long-term reliability and consistency of the punch press in high-speed, high-precision stamping operations.

[0091] exist Figure 5-8 In the illustrated scheme, the connecting rod is a double-axis connecting rod with connecting rod shaft holes 21 at both ends, or a ball-end connecting rod with a connecting rod shaft hole 21 at one end and a ball head 22 at the other end; the second end of the double-axis connecting rod adopts a split structure or a clamping structure; the split structure includes a connecting rod body end 20 and a detachably connected end cap 16, which is fixedly connected by fasteners; the connecting rod shaft hole 21 of the clamping structure has an axially penetrating opening slit 18 in the circumferential direction, and connecting holes are respectively provided on both sides of the opening slit 18. The radial clamping force of the connecting rod shaft hole 21 is adjusted by applying torque through the connecting holes with fasteners.

[0092] Specifically, the structure of the connecting rod can be optimized based on its specific function and motion characteristics in the punch press transmission mechanism. For example... Figure 6-8 As shown, the first option is to use a double-hole connecting rod, with connecting rod shaft holes 21 at both ends, suitable for applications requiring a stable rotary hinge connection via a pin or rotating shaft 10. This design can effectively transmit rotational or oscillating motion and withstand large radial loads, with a relatively simple structure that is easy to manufacture and assemble. Figure 5 As shown, another option is to use a ball joint connecting rod, which has a connecting rod shaft hole 21 at one end and a ball joint 22 at the other end. The ball joint 22 connection provides greater freedom of movement, allowing rotation and oscillation in multiple directions, and can effectively compensate for assembly errors or minor misalignments generated during movement. It is suitable for complex connections that require three-dimensional movement or have a certain degree of self-alignment capability.

[0093] To further improve the assembly, maintenance convenience, and precision adjustability of the dual-axis connecting rod, its second end can adopt a split structure or a clamp-type structure. For example... Figure 5-7 As shown, when a split structure is used, the end of the connecting rod is designed as two detachable parts, specifically including a connecting rod body end 20 and a detachably connected end cap 16. The end cap 16 is reliably fixed to the connecting rod body end 20 by fasteners such as bolts or screws. This design greatly simplifies the installation and removal of bearings or bushings, and is particularly suitable for components that cannot be directly slid in from the connecting rod end, thereby shortening maintenance time and reducing maintenance costs.

[0094] like Figure 8 As shown, when a clamp-type structure is used, the connecting rod shaft hole 21 at the end of the connecting rod has an axially penetrating opening slit 18 circumferentially. Connecting holes are provided on both sides of this opening slit 18. By passing fasteners through these connecting holes and applying appropriate torque, the radial clamping force of the connecting rod shaft hole 21 can be precisely adjusted. This adjustment capability allows for fine-tuning of the fit clearance between the connecting rod shaft hole 21 and the connected shaft after wear due to long-term operation, thereby eliminating clearance, pre-tightening the connection, and maintaining the tightness of the connection and transmission accuracy.

[0095] Through the above technical solutions, this application can flexibly select either a double-hole connecting rod or a ball-end connecting rod according to the specific needs of the punch press transmission mechanism, thereby optimizing kinematic performance. In particular, the second end of the double-hole connecting rod adopts a split structure or a clamping structure, significantly improving the ease of assembly, precision adjustability, and maintainability of the connection between the connecting rod end and the rotating shaft 10. The split structure makes the installation and replacement of internal components more convenient, effectively shortening the maintenance cycle. The clamping structure allows for precise adjustment of the clamping force to compensate for wear clearances, ensuring tightness of the connection and transmission accuracy, thereby effectively suppressing vibration and noise during operation, significantly extending the service life of the punch press, and improving its overall operational stability and accuracy. These structural designs work together to provide a more reliable and efficient solution for the transmission mechanism of a high-precision, high-stability punch press.

[0096] like Figure 9-14 As shown, this application further proposes a high-precision, high-stability punch press, which also includes a guide structure disposed between the punch press frame and the slide block 6. The main function of this guide structure is to ensure that the slide block 6 can perform precise and stable reciprocating motion along a preset vertical direction during the punching process, effectively suppressing possible lateral displacement and tilting of the slide block 6, thereby ensuring punching accuracy and die life. This guide structure is typically composed of core components such as guide post 23, guide sleeve 24, rolling assembly 25, and guide seat 26.

[0097] The guide post 23 is the core guiding component in the guiding structure, and its outer wall has multiple axially extending cross-sections 27. These cross-sections 27 are not simple circular sections, but precision-machined planes designed to form a precise rolling contact interface with the rolling assembly 25. The guide post 23 is typically made of high-strength, high-hardness materials with finely ground or coated surfaces to ensure its wear resistance and dimensional stability under long-term high-speed operation. Its axially extending cross-sections 27 provide multiple flat contact surfaces for the rolling assembly 25, helping to distribute loads and improve guiding accuracy and load-bearing capacity. The guide sleeve 24 is a component fitted around the guide post 23, forming a guiding pair together with the guide post 23. An appropriate gap is left between the inner wall of the guide sleeve 24 and the outer wall of the guide post 23 to accommodate the rolling assembly 25. The guide sleeve 24 is typically fixed to the press frame or slide block 6, and its function is to provide support and limit the rolling assembly 25, and guide the rolling assembly 25 to roll precisely along the cross-sections 27 of the guide post 23. The material selection and machining precision of the guide sleeve 24 are crucial to the performance of the entire guide structure; materials with good wear resistance and dimensional stability are typically chosen. The rolling assembly 25 is disposed within the guide sleeve 24 and rolls in contact with the guide post 23. Its main function is to convert the sliding friction between the guide post 23 and the guide sleeve 24 into rolling friction, thereby significantly reducing motion resistance, reducing energy loss, and improving motion smoothness and response speed. The rolling assembly 25 can be composed of rollers 35, balls 44, or other types of rolling elements; its specific form and arrangement are designed according to the required load-bearing capacity, accuracy level, and motion characteristics. Through rolling contact, the creeping phenomenon and wear problems that may occur in traditional sliding guides under high-speed, heavy-load conditions can be effectively avoided. The guide seat 26 is fixedly disposed at the end of the guide sleeve 24. Its main function is to provide a stable mounting base for the guide sleeve 24 and precisely limit the axial travel of the guide post 23. Through the structural design of the guide seat 26, it is ensured that the guide post 23 reciprocates within a predetermined travel range, preventing overshoot or undershoot. The guide seat 26 is usually made of high rigidity material and fits tightly with the guide sleeve 24 to ensure the overall rigidity and stability of the entire guide structure.

[0098] Through the above technical solution, a guide structure is added between the press frame and the slide 6. This guide structure, consisting of guide post 23, guide sleeve 24, rolling assembly 25, and guide seat 26 working together, effectively solves the problems of lateral swaying and off-center loading that may occur in the slide 6 during high-speed stamping. Specifically, multiple axially extending facets 27 on the outer wall of guide post 23 form precise rolling contact with the rolling assembly 25 inside guide sleeve 24, converting the vertical motion of slide 6 into low-friction rolling motion, greatly reducing motion resistance and improving the smoothness and response speed of slide 6. The guide seat 26 ensures that the axial travel of guide post 23 is precisely limited, preventing over-stroke. Overall, this guide structure provides high-precision, high-rigidity vertical guidance for slide 6, significantly improving the stamping accuracy and stability of the press, effectively extending the service life of the mold and press components, thereby ensuring the quality and production efficiency of stamped products.

[0099] like Figure 9 and 10 As shown, the above-mentioned guide structure is a high-precision guide structure, wherein the rolling assembly 25 includes a bearing cage 34 and a plurality of rollers 35. The bearing cage 34 is axially movable within the guide sleeve 24, and the plurality of rollers 35 are mounted on the bearing cage 34, each roller 35 corresponding to and rollingly contacting a cross-section 27 of the guide post 23. The rollers 35 are cylindrical, and their axial direction is perpendicular to the axial direction of the guide post 23.

[0100] Specifically, the high-precision guide structure aims to ensure that the slider 6 maintains extremely high motion accuracy and position repeatability throughout the entire stroke, minimizing radial and angular runout. Its design goal is to provide low-friction, high-rigidity, and long-life guiding performance to adapt to the high-speed, heavy-load working environment of the press, thereby ensuring the dimensional accuracy and surface quality of the stamped products. The bearing cage 34 precisely spaces and guides the multiple rollers 35, preventing them from contacting and rubbing against each other, and ensuring that the rollers 35 move smoothly axially within the guide sleeve 24. The cage 34 is typically made of lightweight, wear-resistant materials, such as engineering plastics or metals, and its structural design allows the rollers 35 to roll freely while maintaining their correct alignment and spacing. The rollers 35, as the load-bearing units of the rolling assembly 25, are typically made of high-hardness, high-wear-resistant bearing steel. Compared to the balls 44, the rollers 35 provide a larger contact area (line contact or near-line contact), significantly improving the load-bearing capacity and rigidity of the guide structure, making it more suitable for withstanding the heavy loads and impacts generated during press operation. The bearing cage 34 is axially movable within the guide sleeve 24. This arrangement ensures that the entire rolling assembly 25 can move freely and smoothly along the axial direction of the guide post 23 within the guide sleeve 24 as the slider 6 moves up and down, thus providing full-stroke guidance for the slider 6. Multiple rollers 35 are precisely positioned and fixed by the cage 34, forming a single rolling unit. This installation method ensures that the rollers 35 will not scatter or deviate from their predetermined positions during movement, thereby maintaining the stability and reliability of the guiding system. The outer wall of the guide post 23 has multiple axially extending facets 27, which provide a flat rolling surface for the rollers 35. Each roller 35 makes rolling contact with a corresponding facet 27. This design increases the effective contact area between the rollers 35 and the guide post 23, further enhancing the load-bearing capacity and anti-overturning stiffness of the guiding system, and helping to precisely control the movement trajectory of the slider 6. The cylindrical rollers 35 form line contact with the facets 27 of the guide post 23, providing excellent load-bearing capacity and rigidity. The axis of the roller 35 is perpendicular to the axis of the guide post 23, which ensures that the roller 35 moves in a pure rolling manner on the cross-section 27 of the guide post 23, minimizing sliding friction, reducing wear, and improving the smoothness and accuracy of the movement.

[0101] Through the above technical solution, the guide structure is designed as a high-precision guide structure, and a rolling assembly 25 composed of a bearing cage 34 and multiple cylindrical rollers 35 is adopted, significantly improving the performance of the punch press slide 6 guide system. Specifically, the cylindrical rollers 35 form line contact with the tangential surface 27 of the guide post 23, greatly increasing the contact area, thereby significantly improving the load-bearing capacity and anti-overturning stiffness of the guide structure, effectively resisting the huge lateral forces and impact loads generated during the stamping process. The bearing cage 34 precisely spaces and guides the rollers 35, ensuring that the rollers 35 move smoothly along the axial direction within the guide sleeve 24, avoiding friction and misalignment between the rollers 35, thereby reducing motion resistance, reducing wear, and extending the service life of the guide system. The design of the roller 35 axis being perpendicular to the axis of the guide post 23 ensures pure rolling motion, further improving the smoothness and precision of the motion. Overall, this high-precision guide structure ensures that the slider 6 maintains extremely high motion accuracy and position repeatability throughout the entire stroke, minimizing radial and angular runout, thereby significantly improving the machining accuracy and surface quality of the stamped parts, and enhancing the operational stability of the press under high-speed and heavy-load conditions.

[0102] like Figure 11-13 As shown, the guide structure is designed as an adjustable stroke guide structure. This type of adjustable stroke guide structure refers to a guide mechanism whose effective guide length or working range can be adjusted according to actual needs. This structure allows the punch press to maintain optimal guiding performance under different punching strokes, avoiding loss of guiding accuracy due to stroke variations. This can be achieved by changing the relative position or effective working length of the guide components through mechanical adjustment, hydraulic adjustment, or electronic control. For example, it can be achieved by adjusting the position of the guide seat 26, or through a segmented combination of guide elements.

[0103] In this guide structure, the rolling assembly 25 includes a base 36, which is fixedly disposed within the guide sleeve 24. The base 36 serves as a support structure for the rolling assembly 25, supporting and positioning the rolling elements. Fixing the base 36 within the guide sleeve 24 ensures a stable connection between the rolling assembly 25 and the guide sleeve 24, providing a stable mounting base for the subsequent rolling elements. The base 36 can be made of high-strength materials such as alloy steel or cast iron and is securely mounted on the inner wall of the guide sleeve 24 using bolts, pins, or interference fits.

[0104] The base 36 is provided with a circulating raceway 37, and multiple rollers 35 are installed within the circulating raceway 37 and can circulate along it. The circulating raceway 37 is a closed or semi-closed track used to guide the rollers 35 to circulate within it. The rollers 35 are rolling friction elements in the rolling assembly 25. The design of the circulating raceway 37 allows the rollers 35 to continuously renew their contact surfaces through circulatory motion while bearing loads, thereby extending their service life and maintaining a low coefficient of friction. The rollers 35 are typically cylindrical or conical and made of high-hardness wear-resistant steel. The circulating raceway 37 can be formed directly on the base 36 by precision machining or by embedding prefabricated raceway components. When the rollers 35 roll within the circulating raceway 37, some rollers 35 contact the guide post 23 to bear the load, while others circulate back in the unloaded area.

[0105] The base 36 is elongated and has multiple mounting slots 40 spaced axially along its surface. The elongated base 36 provides sufficient length to accommodate multiple rolling support units 39, thus achieving multi-point axial support for the guide post 23. The axially spaced mounting slots 40 provide precise positioning and installation space for the segmented circulating raceway body 38, facilitating assembly and maintenance. The mounting slots 40 can be formed on the elongated base 36 using precision machining methods such as milling and grinding.

[0106] Each mounting slot 40 contains a circulating raceway 38, and each circulating raceway 38 and its internal rollers 35 form a rolling support unit 39. The circulating raceway 38 is an independent component containing the circulating raceway 37. The rolling support unit 39 is the smallest functional unit composed of the circulating raceway 38 and its internal rollers 35. Using independent circulating raceways 38 simplifies the manufacturing process and facilitates high-precision machining and assembly of individual units. Each rolling support unit 39 operates independently, collectively providing support for the guide post 23. The circulating raceway 38 can be made of high-hardness steel and fixed within the mounting slot 40 by bolts or press-fitting.

[0107] Multiple rolling support units 39 are distributed axially at intervals, collectively making rolling contact with their corresponding cross-sections 27. Axially at intervals means these units are arranged at a certain distance along the length of the guide post 23. The corresponding cross-sections 27 are planes on the outer wall of the guide post 23 designed for rolling contact. This distribution allows the guide structure to provide uniform and stable multi-point support to the guide post 23, effectively distributing the load and improving guiding accuracy and rigidity. Simultaneously, because each unit independently makes rolling contact with the cross-sections 27 of the guide post 23, it can better accommodate minor deformations of the guide post 23 and allows for stroke adjustment within a certain range.

[0108] Through the above technical solution, the guide structure is designed as an adjustable stroke guide structure, and multiple mounting slots 40 are arranged axially at intervals on a long strip base 36. Each mounting slot 40 is equipped with a circulating raceway 38 and rollers 35 to form a rolling support unit 39. These units are distributed axially at intervals and roll in contact with the tangential surface 27 of the guide post 23. This design allows the press guide structure to flexibly adjust the effective guide stroke according to different stamping dies and processing requirements, thereby maintaining high precision and high stability throughout the stamping process. The segmented design of multiple rolling support units 39 not only effectively disperses the load acting on the guide post 23, improving the rigidity and load-bearing capacity of the guide system, but also significantly reduces frictional resistance and wear through the cyclic rolling of the rollers 35, extending the service life of the guide structure. In addition, this modular rolling support unit 39 is easy to manufacture, install, and maintain, further improving the reliability and economy of the press, and ensuring that the press can still achieve high-quality stamping processing under variable stroke conditions.

[0109] In both of the above schemes, the cut surface 27 is designed as a plane, which can be uniformly or non-uniformly distributed along the circumference of the guide post 23. Designing the cut surface 27 as a plane ensures a stable and high-precision line or surface contact between the rolling assembly 25 and the guide post 23, thereby effectively transferring loads and reducing local stress concentration. A uniformly distributed cut surface 27 helps achieve balanced load distribution and symmetrical guidance, while a non-uniform distribution can be optimized according to specific load or space requirements. Simultaneously, the guide post 23 has a larger diameter upper section 28 and a smaller diameter lower section 29, wherein an annular stepped surface 30 is formed between the upper section 28 and the lower section 29. This stepped design allows the guide post 23 to have different functions and strengths in different areas; the larger diameter upper section 28 can provide stronger structural support or serve as an installation reference for other components, while the smaller diameter lower section 29 focuses on high-precision guiding functions. The annular stepped surface 30 provides a precise axial positioning reference for the assembly of the guiding system. Specifically, the cut surface 27 is provided on the outer peripheral wall of the lower column 29, and the guide sleeve 24 is fitted onto the outside of the lower column 29. This configuration ensures that the guide sleeve 24 and the lower column 29 of the guide post 23 fit tightly together, enabling the rolling assembly 25 to achieve precise rolling guidance in this area, concentrating the high-precision guiding function in the structurally optimized area.

[0110] Through the above technical solution, the cut surface 27 is designed as a plane and set on the outer peripheral wall of the lower column 29 with a smaller diameter, and the guide sleeve 24 is fitted onto the outside of the lower column 29. This application can ensure a stable and high-precision rolling contact between the rolling assembly 25 and the guide post 23. The stepped design of the guide post 23, that is, having an upper column 28 with a larger diameter and a lower column 29 with a smaller diameter, and an annular step surface 30 formed between them, not only enhances the overall structural rigidity of the guide post 23, but also provides a clear benchmark for the assembly and axial positioning of the guiding system. This structure concentrates the high-precision guiding function in the lower column 29, optimizes the load distribution, effectively reduces local stress, thereby significantly improving the accuracy and stability of the slider 6 guidance and extending the service life of the guiding system.

[0111] Furthermore, in both of the above schemes, the end of the guide sleeve 24 is fixedly provided with a guide seat 26. The guide seat 26 has an inner cavity 31, which is used to accommodate the upper section 28 of the guide post 23 and allows the guide post 23 to move up and down axially in the inner cavity 31. A limiting structure 32 is provided on the guide seat 26. The limiting structure 32 cooperates with the annular step surface 30 to limit the maximum downward stroke of the guide post 23. The limiting structure 32 is an annular retaining ring, which is fixedly installed on the inner wall of the annular opening at the lower end of the guide seat 26.

[0112] Specifically, the guide seat 26 is a component fixed to the end of the guide sleeve 24, and its interior is designed with an inner cavity 31. The size and shape of this inner cavity 31 match the upper section 28 of the guide post 23, allowing the upper section 28 to be accommodated and enabling the guide post 23 to perform smooth axial reciprocating motion within the inner cavity 31. The function of the guide seat 26 is to provide additional support and guidance for the guide post 23, especially at the end of the guide post 23's stroke, helping to maintain the stability of the guide post 23 and providing a mounting base for the subsequent limiting structure 32. The guide seat 26 can be made of various materials, such as high-strength steel, cast iron, or engineering plastics, depending on the working environment and precision requirements of the punch press. Its fixing method can be a secure connection to the end of the guide sleeve 24 through bolting, interference fit, or welding. The limiting structure 32 is a key component set on the guide seat 26, and its main function is to interact with the annular stepped surface 30 on the guide post 23, thereby precisely controlling and limiting the maximum downward movement distance of the guide post 23. When the guide post 23 moves downward to the preset position, the annular stepped surface 30 contacts the limiting structure 32, preventing the guide post 23 from continuing to descend. This engagement ensures that the press slide 6 does not exceed the safe or design-permitted stroke range during operation, thus protecting the mold and press mechanism from overload or collision damage. The design of the limiting structure 32 needs to consider its strength, wear resistance, and contact method with the annular stepped surface 30 to ensure long-term reliability. The annular retaining ring is a specific implementation of the limiting structure 32. It is designed in a ring shape and precisely fixed on the inner wall of the annular opening at the lower end of the guide seat 26. When the guide post 23 moves downward, its annular stepped surface 30 contacts the upper surface of the annular retaining ring, thereby effectively limiting the downward stroke of the guide post 23. The annular retaining ring can be installed by threaded connection, snap ring fixing, interference fit, or welding, ensuring that it remains stable under impact loads. The material of the retaining ring is usually a high-strength, wear-resistant metal, such as alloy steel, to resist wear and deformation during long-term operation. This structure is simple, reliable, easy to manufacture and maintain, and can provide precise stroke control.

[0113] Through the above technical solution, a guide seat 26 is fixedly installed at the end of the guide sleeve 24, and the inner cavity 31 of the guide seat 26 accommodates the upper section 28 of the guide post 23, providing additional stable support for the axial movement of the guide post 23. More importantly, by setting a limiting structure 32 on the guide seat 26 and precisely engaging it with the annular stepped surface 30 of the guide post 23, the maximum downward stroke of the guide post 23 can be effectively limited. Specifically, an annular retaining ring is used as the limiting structure 32 and fixedly installed on the inner wall of the annular opening at the lower end of the guide seat 26, so that when the guide post 23 moves downward, its annular stepped surface 30 can reliably abut against the retaining ring, thereby precisely controlling the bottom dead center position of the slide block 6. This not only avoids mechanical interference or mold damage that may be caused by excessive downward movement of the guide post 23, significantly improving the operational stability and safety of the punch press slide block 6 guiding system, but also simplifies the stroke adjustment and maintenance process, ensuring the consistency and precision of the stamped products.

[0114] like Figure 14 As shown, the guide structure is designed as a combined guide structure, which also includes a copper sleeve 41 fixedly disposed within the guide sleeve 24. The copper sleeve 41 is slidably engaged with the guide post 23. The rolling assembly 25 includes a guide sleeve body 42, a retainer 43, and a plurality of balls 44. The guide sleeve body 42 is fixed within the guide sleeve 24 and located below the copper sleeve 41. An annular gap 45 is formed between the guide sleeve body 42 and the guide post 23. The retainer 43 is slidably disposed within the annular gap 45 along the axial direction. The plurality of balls 44 are mounted on the retainer 43. The outer peripheral surface of each ball 44 makes rolling contact with the inner wall of the guide sleeve body 42 and the outer wall of the guide post 23, respectively.

[0115] Specifically, the combined guide structure aims to combine two or more different guiding methods to integrate the advantages of different guiding methods and compensate for the shortcomings of a single guiding method, thereby achieving better overall performance, such as improving load-bearing capacity, reducing friction, enhancing damping, improving accuracy, or extending service life. In this embodiment, it is specifically manifested as a combination of the sliding fit of the copper sleeve 41 and the rolling contact of the ball bearing 44 rolling assembly. The copper sleeve 41 is a sleeve-shaped part made of copper alloy material, which generally has good wear resistance, self-lubricating properties (in the presence of lubricant), and vibration damping performance. As a sliding guide element, it slides with the guide post 23, providing stable support and a certain damping effect, which helps to absorb impact loads and maintain contact stability under large loads. The copper sleeve 41 is usually installed in the guide sleeve 24 by press-fitting, threaded connection, or other fixing methods, with an appropriate fitting clearance between its inner hole and the outer diameter of the guide post 23 to allow relative sliding and the formation of a lubricating oil film. The material can be an alloy with good sliding properties, such as tin bronze or aluminum bronze. The guide sleeve 42 serves as the external support structure for the rolling assembly 25, used to fix the internal components of the rolling assembly 25. Its function is to provide external support and positioning for the balls 44, and to form an integral unit with the guide sleeve 24, ensuring the stable operation of the rolling assembly 25. The guide sleeve 42 is typically a cylindrical shape or a sleeve with a specific cross-section, securely installed inside the guide sleeve 24 through interference fit, bolt fixing, or other methods. Its inner wall is usually designed with a structure that mates with the balls 44 or the cage 43. The cage 43 is a structure used to space and maintain the distance between the rolling elements, preventing them from contacting and rubbing against each other, and guiding their movement in the circulating raceway or gap. Its function is to ensure the even distribution of the balls 44, reduce friction between the balls 44, and improve the smoothness and lifespan of the rolling assembly 25. The cage 43 is typically made of metal (such as brass, steel) or engineering plastic (such as nylon), and has multiple evenly distributed holes in which the balls 44 are installed. In this embodiment, the cage 43 is slidably disposed within the annular gap 45 along the axial direction. The ball bearing 44 is a spherical rolling element with point contact or small-area contact characteristics, exhibiting a low coefficient of friction and suitable for high-speed, high-precision rolling motion. Its function is to provide rolling support between the guide sleeve 42 and the guide post 23, significantly reducing frictional resistance and improving guiding sensitivity and accuracy. The ball bearing 44 is typically made of high-hardness, high-precision bearing steel (such as GCr15) or ceramic materials. Multiple balls bearing 44 are evenly mounted on the cage 43, forming rolling contact between the guide sleeve 42 and the guide post 23. The annular gap 45 refers to the annular space formed between the guide sleeve 42 and the guide post 23, providing movement space for the cage 43 and the ball bearing 44, ensuring the normal operation of the rolling assembly 25. By precisely machining the dimensions of the guide sleeve 42 and the guide post 23, the radial clearance between them can be controlled to accommodate the installation and movement of the ball bearing 44 and the cage 43.

[0116] Through the above technical solution, the sliding fit of the copper sleeve 41 and the rolling contact of the balls 44 are combined to form a composite guide structure. The copper sleeve 41 provides sliding support and has good damping performance, effectively absorbing impact loads and vibrations during the stamping process, thus significantly improving the operational stability of the press. Simultaneously, the rolling assembly of the balls 44 provides low-friction, high-precision rolling support, ensuring the sensitivity and positioning accuracy of the slider 6. The guide sleeve 42 is fixed inside the guide sleeve 24 and located below the copper sleeve 41. This specific arrangement allows the copper sleeve 41 to primarily bear impact loads and provide damping in the upper part, while the ball assembly 44 provides precise positioning and low friction in the lower part, forming a reasonable mechanical distribution. The cage 43 slides axially within the annular gap 45, ensuring the balls 44 are evenly distributed and move smoothly. The rolling contact between the balls 44 and the inner wall of the guide sleeve 42 and the outer wall of the guide post 23 further reduces friction and improves guiding efficiency and accuracy. This combined guide structure integrates the damping and load-bearing capacity of sliding guides with the low friction and high precision of rolling guides, effectively solving the stability, precision and life problems that may exist in single guide structures under high-speed and high-load stamping environments, thereby significantly improving the overall performance of the press and the quality of the stamped parts.

[0117] In a further embodiment, the upper end of the copper sleeve 41 has a flange 46 extending radially outward, which is mounted on the cavity end face of the guide sleeve 24; a cap 47 is fixedly provided at the end of the guide sleeve 24, which is pressed against the upper surface of the flange 46 to restrict the axial displacement of the copper sleeve 41 and the rolling assembly 25; a sealing ring 48 is provided between the upper end of the copper sleeve 41 and the inner wall of the cavity of the guide sleeve 24, and between the upper end of the copper sleeve 41 and the guide post 23, and the cap 47 presses the sealing ring 48 into the sealing cavity opened at the upper end of the copper sleeve 41; a retaining ring 50 is provided at the lower end of the mounting cavity of the guide sleeve 24, and the lower end of the guide sleeve body 42 abuts against the retaining ring 50; the retainer 43 and the ball bearings 44 thereon are located between the retaining ring 50 and the lower end face of the copper sleeve 41, and can slide axially. Specifically, the upper end of the copper sleeve 41 can be integrally formed or connected in other ways to form a radially outwardly extending flange 46. The function of this flange 46 is to provide an axial support surface for the copper sleeve 41, allowing it to be stably mounted on the cavity end face of the guide sleeve 24. This design enables the copper sleeve 41 to achieve initial axial positioning within the guide sleeve 24 and to withstand axial loads from above, ensuring its accurate and reliable initial installation position within the guide sleeve 24.

[0118] Based on this, a cover 47 is fixedly provided at the end of the guide sleeve 24. The cover 47 is typically fixed to the end of the guide sleeve 24 by bolts, threaded connections, or other fastening methods. When the cover 47 is fixed, its lower surface is tightly pressed against the upper surface of the flange 46 of the copper sleeve 41. This pressing action not only further fixes the axial position of the copper sleeve 41, but also, through the transmission of the copper sleeve 41, indirectly or directly restricts the overall axial displacement of the rolling assembly 25 located below it. The cover 47 ensures the axial tightness and stability of the entire guide assembly, preventing loosening or displacement of components due to vibration or impact during press operation.

[0119] Meanwhile, to achieve effective sealing, sealing rings 48 are provided between the upper end of the copper sleeve 41 and the inner wall of the cavity of the guide sleeve 24, and between the upper end of the copper sleeve 41 and the guide post 23. These sealing rings 48 are typically O-rings, oil seals, or other elastic seals. The sealing cavity at the upper end of the copper sleeve 41 provides space for these sealing rings 48. When the cover 47 is pressed onto the flange 46, it simultaneously presses these sealing rings 48 into the sealing cavity, making them fit tightly and forming an effective sealing barrier. This double sealing design can effectively prevent lubricating oil from leaking from the upper end of the guide structure, while preventing external dust, chips, and other contaminants from entering the interior of the guide structure, thereby protecting the guide components and extending their service life.

[0120] Furthermore, a retaining ring 50 is provided at the lower end of the mounting cavity of the guide sleeve 24. This retaining ring 50 is typically annular and is installed at the lower end of the mounting cavity of the guide sleeve 24 by means of a snap ring, threads, or other fixing methods. The lower end face of the guide sleeve body 42 abuts against the retaining ring 50, thereby positioning and supporting the guide sleeve body 42 axially. In this way, the retainer 43 and its balls 44 are confined within the axial space formed by the retaining ring 50 and the lower end face of the copper sleeve 41. This structure ensures the correct axial position of the rolling assembly 25 within the guide sleeve 24, while allowing the retainer 43 and its balls 44 to slide axially within a defined range to achieve the rolling guidance function.

[0121] Through the above technical solution, the axial positioning and sealing problems of the copper sleeve 41 and the rolling assembly 25 in the guide structure are effectively solved. Specifically, the radially extending flange 46 at the upper end of the copper sleeve 41 mates with the end face of the cavity of the guide sleeve 24 and is pressed by the cap 47, achieving reliable axial fixation of the copper sleeve 41. At the same time, the cap 47 forms a double seal between the copper sleeve 41 and the inner wall of the guide sleeve 24, and between the copper sleeve 41 and the guide post 23 by pressing a sealing ring 48 into the sealing cavity at the upper end of the copper sleeve 41, effectively preventing lubricant leakage and isolating external contaminants. In addition, the retaining ring 50 at the lower end of the mounting cavity of the guide sleeve 24 provides axial support for the guide sleeve body 42, precisely confining the cage 43 and its balls 44 within the working area, ensuring stable operation of the rolling assembly 25 within the allowable axial sliding range. This precise axial fixing and multi-seal design significantly improves the overall stability, guiding accuracy and service life of the combined guide structure, effectively avoiding the decrease in accuracy and premature wear caused by axial movement of components or poor lubrication, thus ensuring the reliability of the punch press slide guide system under high load and high frequency working conditions.

[0122] In a further embodiment, the copper sleeve 41 is provided with an oil hole 51 that connects its inner and outer walls, and the guide sleeve 24 is provided with an oil inlet hole 52 and an oil return hole 53. The oil inlet hole 52 and the oil return hole 53 are respectively connected to the oil hole 51 of the copper sleeve 41, and the oil inlet hole 52 and the oil return hole 53 are located at different positions in the axial direction of the copper sleeve 41 to form a lubricating oil circulation path.

[0123] Specifically, the oil holes 51 on the copper sleeve 41 are used to introduce lubricating oil from the outside of the copper sleeve 41 into the sliding contact area between its inner wall and the guide post 23, or to draw lubricating oil out of the sliding contact area. These oil holes 51 can be designed as radial holes, oblique holes, or a combination of annular grooves and radial holes to ensure that the lubricating oil can effectively reach the sliding contact surface. The number and distribution of oil holes 51 can be optimized according to the length of the copper sleeve 41, the diameter of the guide post 23, and the lubrication requirements. For example, multiple oil holes 51 can be evenly distributed along the axial direction of the copper sleeve 41, or densely distributed in areas with high stress. At the same time, the oil inlet hole 52 and the oil return hole 53 provided on the guide sleeve 24 are used to connect the external lubricating oil supply system with the oil holes 51 on the copper sleeve 41 to form a complete lubricating oil circulation path. The oil inlet hole 52 is usually connected to an external oil pump, which is responsible for pumping fresh lubricating oil into the guide structure; the oil return hole 53 is responsible for collecting used or excess lubricating oil and returning it to the oil tank or cooling filter system. The size and position of these holes need to be precisely aligned with the oil holes 51 on the copper sleeve 41 to ensure smooth oil flow.

[0124] Based on this, the oil inlet hole 52 and the oil return hole 53 are respectively connected to the oil hole 51 of the copper sleeve 41. This means that during assembly, the oil inlet hole 52 and the oil return hole 53 on the guide sleeve 24 can be aligned with the corresponding oil hole 51 on the copper sleeve 41, thereby establishing a flow path for lubricating oil. This connection can be achieved through direct alignment, through an internal flow channel, or through a sealing connector, to ensure that lubricating oil can enter the interior of the copper sleeve 41 from the guide sleeve 24, and flow out from the copper sleeve 41 after lubrication, eventually returning to the oil return hole 53 of the guide sleeve 24. Furthermore, the oil inlet hole 52 and the oil return hole 53 are located at different axial positions of the copper sleeve 41. For example, the oil inlet hole 52 can be located at the upper part of the copper sleeve 41, and the oil return hole 53 can be located at the lower part of the copper sleeve 41, or vice versa. This axial misalignment design is to form an effective lubricating oil circulation path within the sliding fit area between the copper sleeve 41 and the guide post 23. Lubricating oil enters through the oil inlet hole 52, flows through the sliding surface, carries away frictional heat and wear debris, and then flows out through the oil return hole 53.

[0125] Through the above technical solution, lubricating oil can be continuously pumped into the sliding contact area, forming a stable oil film, significantly reducing the coefficient of friction between the copper sleeve 41 and the guide post 23, thereby reducing the generation of frictional heat. Simultaneously, the circulating lubricating oil effectively carries away the heat generated on the sliding surface, achieving cooling of the guide structure and preventing localized overheating. Furthermore, the continuous flushing action of the oil helps remove tiny wear debris from the sliding surface, preventing debris accumulation and accelerated wear. This active lubrication and cooling mechanism effectively solves the problems of insufficient lubrication and poor heat dissipation in traditional sliding guides, significantly improving the long-term operational stability, accuracy retention, and service life of the guide system.

[0126] like Figure 15-17 As shown, the slider 6 is an integrally formed silicon carbide particle-reinforced aluminum matrix composite slider. The punch press also includes an oil cooling channel 54 disposed inside the slider 6. The oil cooling channel 54 includes at least one oil passage opened inside the slider 6 and located directly below the main rib 58 of the slider. The two ends of the oil passage extend to the side of the slider 6 and form an oil inlet and an oil outlet, respectively.

[0127] Specifically, the slider 6 is the core component of the punch press used to mount the upper die and perform reciprocating motion. One-piece molding means that the slider 6 is formed into a complete structure through integral casting, forging, or precision machining, rather than being assembled from multiple parts. The use of silicon carbide particle-reinforced aluminum matrix composite material as the material for the slider 6 is based on its excellent comprehensive performance, including low density (achieving lightweighting and reducing moment of inertia), high specific strength and specific stiffness (ensuring structural strength and resistance to deformation), and good thermal conductivity (facilitating heat transfer). The one-piece molding structure avoids the cumulative errors and stiffness losses that may result from connecting multiple parts, further improving the overall rigidity and precision of the slider 6. The oil cooling channel 54 is a cooling system that removes heat through circulating cooling oil. Its placement inside the slider 6 means that the cooling channel is integrated with the slider 6 body, allowing the cooling oil to flow directly inside the slider 6, thus achieving direct and efficient cooling. This internally integrated design minimizes heat transfer paths, improves cooling efficiency, and avoids interference from external cooling devices on the overall structure and operating space of the punch press. The oil passage is the specific path for the cooling oil to flow inside the slider 6. The oil passage is strategically located inside the slider 6, specifically directly below the main rib 58. The main rib 58 is typically a critical component of the slider 6 structure, bearing the main stress and transmitting impact force; it is also a region of heat generation and concentration. Positioning the oil passage directly below it allows the cooling oil to be closer to the heat source, thus more effectively absorbing and carrying away heat. This layout ensures the structural strength of the slider 6 remains intact while achieving precise cooling of hot spots. The oil passage can be formed by pre-reserving casting channels during the integral molding process or by precision drilling after machining. The oil inlet and outlet are the interfaces connecting the oil cooling passage 54 to the external cooling oil circulation system. Both ends of the oil passage extend to the sides of the slider 6, allowing external cooling oil pumps, coolers, and other equipment to easily connect to the internal oil cooling passage 54, forming a complete closed-loop cooling cycle. The oil inlet introduces low-temperature cooling oil, and the oil outlet discharges high-temperature cooling oil after heat absorption, ensuring continuous circulation and heat exchange of the cooling oil. These interfaces typically use standard threaded or flanged connections to ensure reliable and airtight connections.

[0128] By employing the aforementioned technical solution, a one-piece molded silicon carbide particle-reinforced aluminum matrix composite slide block 6, combined with an internal oil cooling channel 54, can significantly improve the performance of the punch press. The one-piece molded silicon carbide particle-reinforced aluminum matrix composite slide block 6 not only achieves lightweight design and reduces moment of inertia, but its high specific strength and high specific stiffness also ensure the structural stability of the slide block 6 under high-speed stamping, reducing deformation. Simultaneously, the excellent thermal conductivity of the silicon carbide particle-reinforced aluminum matrix composite provides a good foundation for heat conduction in the internal oil cooling channel 54. The internal oil cooling channel 54, particularly the oil passage precisely positioned inside the slide block 6 and directly below the main slide block rib 58, allows the cooling oil to efficiently absorb the heat generated by the slide block 6 during stamping. The cooling oil enters through the oil inlet, circulates within the oil passage, carries away heat, and exits through the oil outlet, effectively controlling the temperature rise of the slide block 6. This precise temperature control greatly suppresses thermal deformation of the slide block 6 caused by thermal expansion, ensuring the stamping accuracy and stability of the punch press during long-term continuous operation. In addition, a stable operating temperature helps reduce component wear, extend the service life of slider 6 and related transmission components, and reduce maintenance costs.

[0129] The silicon carbide particle-reinforced aluminum matrix composite material used in the slider described in this application specifically uses ZAlSi12 cast aluminum alloy as the matrix, and uniformly disperses 20% by volume of silicon carbide particles as the reinforcing phase in the matrix. ZAlSi12 is a typical eutectic aluminum-silicon casting alloy with good fluidity, casting performance, and thermal conductivity. Silicon carbide particles have high hardness, high elastic modulus, and low coefficient of thermal expansion. When uniformly distributed in the aluminum alloy matrix, they can significantly improve the overall stiffness, wear resistance, and dimensional stability of the composite material, while suppressing the plastic deformation of the matrix under thermal load.

[0130] Testing has verified that the density of this composite material is only 2.77 g / cm³, approximately one-third that of traditional cast iron, significantly reducing the weight of the slider and thus decreasing the inertial forces and impact vibrations generated during high-speed reciprocating motion. Simultaneously, the reinforcing effect of the silicon carbide particles makes the tensile strength and yield strength of the composite material comparable to cast iron HT350, while its elastic modulus is significantly higher than that of unreinforced cast aluminum alloy, effectively improving the slider's resistance to bending deformation under stamping loads. Combined with the oil cooling channel located directly below the main rib of the slider, the high thermal conductivity of the aluminum alloy matrix rapidly conducts heat from the mold to the cooling medium, while the low thermal expansion characteristics of the silicon carbide particles suppress dimensional changes in the slider caused by temperature rise. This synergistic effect ensures the high-precision operation of the guiding system under thermo-mechanical coupling conditions.

[0131] It should be noted that the above-mentioned specific material composition with ZAlSi12 as the matrix and 20 vol% silicon carbide particles is only a preferred example of silicon carbide particle-reinforced aluminum matrix composite material. Within the scope of the technical concept of this application, the matrix alloy grade, the type or volume fraction of the reinforcing phase can also be adjusted according to the actual working conditions. For example, other cast aluminum alloys or wrought aluminum alloys can be used as the matrix, alumina or silicon nitride particles can be selected as the reinforcing phase, and the volume fraction of the reinforcing phase can be adjusted within the range of 10% to 30%. As long as the technical effect of achieving both lightweight and high rigidity can be achieved, it falls within the protection scope of this application.

[0132] In practical applications, the complex internal structure of the slider 6, especially the presence of the main slider ribs 58, may lead to uneven heat distribution. If the layout of the oil channels is not precise enough, it is difficult to ensure efficient and uniform cooling of the entire slider 6, especially the stress-generating area, thus affecting the long-term accuracy and stability of the punch press. To address this, this application further proposes that the slider 6 includes an upper plate 59, a lower plate 60, and multiple main slider ribs 58 connecting the upper plate 59 and the lower plate 60. The lower plate 60 is used to mount the punch press die. The oil cooling channel 54 is located above the lower plate 60 and directly below each main slider rib 58, and is arranged along the length of the main slider rib 58. The oil cooling channel 54 is a unidirectional oil passage or a circuitous oil passage.

[0133] Specifically, the slider 6 is structurally designed to include an upper plate 59, a lower plate 60, and multiple main slider ribs 58 connecting the upper plate 59 and the lower plate 60. This one-piece molded structure, especially through the arrangement of the main slider ribs 58, significantly improves the overall rigidity and strength of the slider 6, enabling it to withstand high-frequency, high-intensity stamping loads without easily deforming. The upper plate 59 and lower plate 60 serve as the main load-bearing surfaces, while the main slider ribs 58 provide crucial support and bending resistance in the vertical direction. Simultaneously, they form natural channels or areas within the slider 6, providing a structural foundation for the subsequent layout of the oil cooling channels 54. The lower plate 60, as the component directly mounting the stamping die, is a critical area for heat generation and transfer during the stamping process.

[0134] The oil cooling channel 54 is precisely positioned above the lower plate 60 and directly below each main slider rib 58, extending along the length of the main slider rib 58. This layout strategy is based on an in-depth analysis of the heat source distribution and structural characteristics inside the slider 6. By closely fitting the oil channel above the lower plate 60, heat generated from the stamping die and stamping area can be absorbed directly and efficiently. Simultaneously, by utilizing the structure of the main slider rib 58, arranging the oil channel directly below it and extending it along its length not only utilizes the reinforcing rib as a heat conduction path to more effectively transfer heat to the cooling oil, but also provides structural protection and support for the oil channel, ensuring the uniformity and stability of the cooling effect.

[0135] The oil cooling channel 54 can be designed as a unidirectional oil path or a meandering oil path. A unidirectional oil path typically refers to the cooling oil entering from a single inlet, flowing along a relatively direct path through the interior of the slider 6, and exiting from a single outlet. This design offers advantages such as low flow resistance, high flow rate, and a relatively simple system structure, making it suitable for scenarios requiring rapid heat removal. A meandering oil path, also known as a serpentine or coiled oil path, refers to the cooling oil undergoing multiple turns or coils within the slider 6, thereby extending the residence time of the oil within the slider 6 and increasing the heat exchange area and time between the oil and the slider 6 material. This design can significantly improve heat exchange efficiency and achieve more thorough cooling, especially suitable for applications requiring precise temperature control and uniform cooling, but may result in higher flow resistance. The choice between the two oil path types can be made based on specific stamping process requirements and thermal management needs.

[0136] Through the above technical solution, the slider 6 is designed as a structure including an upper plate 59, a lower plate 60, and slider main ribs 58. The oil cooling channel 54 is precisely positioned above the lower plate 60 and directly below each slider main rib 58, extending along its length. This effectively solves the problems of uneven heat distribution and insufficient cooling efficiency within the slider 6. This structured slider 6 design not only enhances its overall rigidity and strength but, more importantly, provides optimized layout space for the oil cooling channel 54. The oil passage is closely fitted above the lower plate 60, where heat generation is most concentrated, and works in conjunction with the slider main ribs 58 to ensure that the cooling oil can efficiently and evenly absorb heat, avoiding localized overheating. Whether using a unidirectional or circuitous oil passage, a stable and efficient cooling effect can be provided according to actual needs. This refined internal cooling design significantly improves the temperature stability of the press slider 6, effectively suppresses thermal deformation, thereby ensuring high precision and stability in the stamping process, extending the service life of key components, and reducing maintenance costs.

[0137] like Figure 1-3As shown, this embodiment also proposes a lubrication and temperature control oil circuit system integrated into the machine body 1. This system aims to provide a continuous, stable, and temperature-controlled lubricating oil for the critical moving parts of the punch press, reducing friction, minimizing wear, dissipating heat, and maintaining the operating temperature of the parts within the optimal range, thereby ensuring the high precision and stability of the punch press. This lubrication and temperature control oil circuit system includes an oil reservoir 62 located within the machine body 1 and an internal oil passage 63 connected to the oil reservoir 62 within the longitudinal support beam. The oil reservoir 62 is the oil storage unit, typically integrated inside the machine body 1 to save space and facilitate oil collection and circulation; its design ensures sufficient volume to meet system operating requirements. The internal oil passage 63 within the longitudinal support beam is part of the oil return path and is connected to the oil reservoir 62. After completing lubrication and cooling tasks, the oil collects and returns to the oil reservoir 62 via channels within the longitudinal support beam inside the machine body 1, forming a closed loop. This integrated design helps simplify the piping layout and utilizes the structure of the machine body 1 for heat dissipation.

[0138] The system also includes an oil pump 64, a distributor 65, and multiple oil supply branches. The oil pump 64 is the power source for the constant-temperature lubrication system, used to pump oil from the oil reservoir 62 to the distributor 65. The type of oil pump 64 can be selected according to system requirements, such as a gear pump, piston pump, or screw pump, to ensure a stable oil supply. The distributor 65 receives the oil from the oil pump 64 and precisely distributes it to multiple oil supply branches according to preset flow and pressure requirements to meet the needs of different lubrication points. The distributor 65 can adopt a centralized or segmented design to ensure a balanced oil supply to each lubrication point. The distributor 65 delivers oil via the oil supply branch to: the moving parts of the crank mechanism for spray lubrication; the connection between the crankshaft 2 and the drive connecting rod 9; the sliding mating surface 14 of the slide block 3, the shaft 10, and the connection between the shaft 10 and the upper connecting rod 7, the lower connecting rod 8, and the second end of the drive connecting rod 9; and between the guide post 23 and the guide sleeve 24. For high-speed moving and stress-complex components in the crank mechanism, such as the connecting rod big end bearing and the crankshaft 2 journal, spray lubrication ensures uniform oil coverage and removes a large amount of frictional heat, achieving both lubrication and cooling. The connection between the crankshaft 2 and the drive connecting rod 9 is a critical stress point in the punch press transmission chain, bearing high impact loads and high-speed relative motion. Lubricating this connection effectively reduces the coefficient of friction of the contact surface, reduces wear, and extends the service life of the components. The sliding mating surface 14 of the slide block 3 slides in contact with the machine body 1. The rotating shaft 10 connects the slide block 3 to each connecting rod. The friction pairs in these parts require continuous oil film support to reduce direct contact and prevent seizing and wear. The fitting accuracy between the guide post 23 and the guide sleeve 24 directly affects the stamping accuracy of the punch press. Through oil lubrication, a stable oil film can be formed between the two, reducing frictional resistance and ensuring the smooth and precise guidance of the slide block 6, while also carrying away frictional heat. After the oil collects above the stamping area, it flows back to the oil storage chamber 62 through the oil passage 63 inside the longitudinal support beam, completing the entire cycle. This ensures the effective recovery and reuse of the oil, reduces waste, and contributes to the overall thermal management of the system.

[0139] Through the above technical solution, this application effectively solves the problems of wear, heat generation, and decreased precision of moving parts under high-speed and high-load operation of punch presses. The system uses an oil pump 64 to precisely deliver oil from the oil reservoir 62 to key friction pairs such as the moving parts of the crank mechanism, the connection between the crankshaft 2 and the drive connecting rod 9, the sliding mating surface 14 of the slide block 3, the rotating shaft 10, and the guide post 23 and the guide sleeve 24. The oil forms a stable lubricating film in these areas, significantly reducing the coefficient of friction and minimizing direct contact wear of components, thereby extending the service life of the punch press. Simultaneously, the oil effectively carries away the heat generated by friction during circulation and returns through the oil passage 63 inside the longitudinal support beam connected to the oil reservoir 62, achieving precise control of the overall operating temperature of the punch press and avoiding precision drift caused by thermal deformation. This continuous, stable, and temperature-controlled lubrication method ensures that the punch press maintains extremely high motion accuracy and structural stability during long-term operation, significantly improving the quality and production efficiency of stamped products.

[0140] In a specific implementation, the aforementioned constant temperature lubrication system further includes an oil cooler 68, which is circulatedly connected to the oil storage chamber 62; the second oil supply branch 662 of the distributor 65 is connected to the crankshaft 2, and the oil is delivered to the connection point between the crankshaft 2 and the drive connecting rod 9 via the internal oil passage 87 of the crankshaft, forming pressure lubrication; the third oil supply branch 663 of the distributor 65 is connected to the sliding mating surface 14 of the slide 3, and the oil is delivered to the rotating shaft 10 via the internal oil passage 88 of the slide 3, and the rotating shaft 10 is provided with a common hinge shaft internal oil passage 89, which is used to deliver the oil to the respective connection points between the rotating shaft 10 and the upper connecting rod 7, the lower connecting rod 8, and the second end of the drive connecting rod 9; the fourth oil supply branch 664 of the distributor 65 is connected between the guide post 23 and the guide sleeve 24, which is used to form a sliding bearing lubrication interface.

[0141] The oil cooler 68 is a device for precisely controlling the temperature of lubricating oil. It maintains the oil temperature within a preset stable range through a refrigeration cycle. The oil cooler 68 is cyclically connected to the oil reservoir 62, meaning that lubricating oil flows from the reservoir 62, is cooled by the oil cooler 68, and then returns to the reservoir 62, forming a continuous temperature control loop. This design ensures that the oil temperature throughout the lubrication system remains within its optimal operating range, effectively preventing problems such as decreased oil viscosity and deteriorated lubrication performance due to excessively high oil temperature, or reduced oil flowability due to excessively low oil temperature. The oil cooler 68 can be air-cooled or water-cooled and can be equipped with a temperature sensor and an automatic control system to achieve real-time monitoring and precise adjustment of the oil temperature.

[0142] In the lubrication circuit, the first oil supply branch 661 of the distributor 65 is connected to the top of the dynamic balancing guide column 90. Oil is sprayed through the internal oil passages of the dynamic balancing guide column 90 to the crankshaft 2, upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 of the crank mechanism. The distributor 65 is a key component of the lubrication circuit system, responsible for distributing oil from the oil pump 64 to different oil supply branches according to preset flow rates and pressures. The first oil supply branch 661 is a dedicated oil passage, with one end connected to the distributor 65 and the other end precisely connected to the top of the dynamic balancing guide column 90. This connection method ensures that oil can enter the dynamic balancing guide column 90 stably and reliably, providing an oil source for subsequent lubrication processes. The connection method can be threaded, flanged, or quick-connect, supplemented with seals to prevent oil leakage. The dynamic balancing guide column 90, as a guide component for the punch press counterweight 12, is cleverly designed with internal oil passages. These internal oil passages can be pre-cast channels inside the guide pillar or formed through machining methods such as drilling. After the oil enters the top of the dynamic balancing guide pillar 90 through the first oil supply branch 661, it flows downward along these internal oil passages until it reaches the preset spray position. This integrated oil passage design avoids the entanglement and interference of external pipelines, improving the system's compactness and reliability. After flowing through the internal oil passages of the dynamic balancing guide pillar 90, the oil is sprayed directly onto the key moving parts of the crank mechanism, including the crankshaft 2, upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9, through nozzles or orifices at the bottom of the guide pillar. Spray lubrication can form a uniform oil film, effectively reducing the coefficient of friction, reducing wear, and carrying away the heat generated by friction. This direct and concentrated spraying method ensures that these high-load, high-speed moving parts receive sufficient lubrication, thereby extending their service life and maintaining the stable operation of the press.

[0143] Through the above technical solution, the lubrication system cleverly utilizes the dynamic balancing guide column 90 as an integrated channel for oil delivery. The first oil supply branch 661 of the distributor 65 precisely introduces oil into the top of the dynamic balancing guide column 90. The oil is then delivered directly and efficiently to the core moving parts of the crank mechanism, namely the crankshaft 2, upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9, via the pre-set oil passages inside the dynamic balancing guide column 90. This design allows the oil to provide concentrated and continuous lubrication to these critical components in a spray manner, effectively solving the problems of insufficient lubrication or low efficiency that may exist in traditional lubrication methods. By integrating the oil passages inside the dynamic balancing guide column 90, not only is the external pipeline layout simplified and the overall integrity and reliability of the system improved, but it also ensures that the crankshaft 2, upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9, which operate under high loads and high speeds, can always maintain a good lubrication state, significantly reducing friction and wear, effectively controlling component temperature rise, and thus greatly improving the operational stability, reliability, and service life of the press.

[0144] The second oil supply branch 662 of the distributor 65 is specifically designed to deliver lubricating oil to the joint between the crankshaft 2 and the drive connecting rod 9. Specifically, this branch connects the oil to a pre-designed oil passage inside the crankshaft 2. The internal oil passage 87 of the crankshaft is a precision channel pre-machined or cast within the crankshaft 2 body. These channels guide the oil to key friction surfaces such as the crankshaft 2 pins and the big end bearings of the drive connecting rod 9. Here, the oil is forcibly delivered under pressure, forming a stable hydrodynamic oil film that completely separates the metal friction surfaces, thereby achieving pressure lubrication. This lubrication method can effectively withstand high loads and high-speed motion, significantly reducing friction, wear, and heat generation.

[0145] The third oil supply branch 663 of the distributor 65 is responsible for delivering lubricating oil to the sliding mating surface 14 of the slide block 3. After entering the slide block 3, the oil is precisely guided to the rotating shaft 10 through the internal oil passage 88. The rotating shaft 10 is a key hub connecting the upper connecting rod 7, the lower connecting rod 8, and the second end of the drive connecting rod 9, and it also has a precision common hinge shaft internal oil passage 89. These oil passages further deliver lubricating oil to the various joints between the rotating shaft 10 and the upper connecting rod 7, the lower connecting rod 8, and the second end of the drive connecting rod 9. This internal oil passage design ensures that these hinge points, which bear high-frequency, high-load reciprocating motion, receive sufficient and continuous lubrication, thereby effectively reducing wear and maintaining the fit accuracy and transmission efficiency of the kinematic pairs.

[0146] The fourth oil supply branch 664 of the distributor 65 directly delivers lubricating oil to the gap between the guide post 23 and the guide sleeve 24. Under the pressure of the oil, a load-bearing oil film is formed between the relatively moving surfaces of the guide post 23 and the guide sleeve 24, thus constructing a lubrication interface for the sliding bearing. This lubrication method can completely separate the metal contact surfaces, achieving hydrodynamic lubrication or hydrostatic lubrication, significantly reducing the frictional resistance of the guiding mechanism, reducing wear, and effectively suppressing the temperature rise and deformation of the guide pair. To optimize the lubrication effect, the inner wall of the guide sleeve 24 can be designed with oil grooves or oil holes 51 to ensure that the oil is evenly distributed throughout the sliding interface.

[0147] By introducing an oil cooler 68 and connecting it circulately with the oil reservoir 62, this application can precisely control the temperature of the lubricating oil, ensuring that the oil viscosity remains stable during the high-speed, high-load operation of the press, thereby maintaining optimal lubrication performance and effectively avoiding lubrication failure and component precision degradation caused by oil temperature fluctuations. Simultaneously, through the second, third, and fourth oil supply branches of the distributor 65, the lubricating oil is precisely delivered under pressure to the joints between the crankshaft 2 and the drive connecting rod 9, the joints between the rotating shaft 10 and the second ends of each connecting rod, and between the guide post 23 and the guide sleeve 24. These critical friction pairs, operating under high load and high frequency, can form a stable hydrodynamic oil film or sliding bearing lubrication interface. This significantly reduces frictional resistance, wear, and heat generation in these areas, effectively suppressing temperature rise and deformation of the moving parts, thereby greatly improving the press's motion accuracy, transmission efficiency, and long-term operational stability, extending the service life of critical components, and providing a reliable guarantee for achieving high-precision stamping.

[0148] like Figure 18-22 In the illustrated scheme, the punch press also includes a vibration damping system located at the bottom of the punch press body 1. The vibration damping system consists of four air cushion anti-vibration feet 70, which are respectively located at the four corners of the punch press body 1. Each of the air cushion shock absorber feet 70 includes a base plate 71 and a top plate 72; a gas spring 73, disposed between the base plate 71 and the top plate 72, with its upper and lower ends respectively connected to the base plate 71 and the top plate 72; multiple damping devices 74, distributed between the base plate 71 and the top plate 72, each damping device 74 including a damping cylinder 75, installed on the lower end face of the top plate 72; a pair of damping mating plates 76, fixed to the upper end face of the base plate 71, the damping cylinder 75 being located between the two pairs of damping mating plates 76; the damping cylinder 75 is a bidirectional output cylinder, with each of its two output ends respectively provided with a clamping member 77, the damping cylinder 75 driving the clamping member 77 to move outward and press against the corresponding damping mating plate 76, thereby generating a damping force.

[0149] The vibration damping system is a device used to absorb and isolate the vibrations and impacts generated during the operation of the punch press. It typically consists of elastic and damping elements; the elastic elements provide flexible support, while the damping elements dissipate vibration energy. The four air cushion anti-vibration feet 70 are vibration damping support devices that utilize airbags as elastic elements, typically possessing adjustable stiffness and damping characteristics. The air cushion anti-vibration feet 70 are usually constructed of airbags made of rubber or composite materials, filled with compressed air. Positioning the four air cushion anti-vibration feet 70 at the four corners of the punch press body 1 ensures uniform support and vibration damping for the entire punch press body 1, providing flexible support, isolating ground vibrations, and absorbing vibrations generated by the punch press itself. The base plate 71 and top plate 72 are structural components of the air cushion anti-vibration feet 70. The base plate 71 is typically connected to the ground or foundation, and the top plate 72 is connected to the punch press body 1. They are typically made of high-strength metal materials (such as cast iron or steel plates), possessing sufficient stiffness and load-bearing capacity, serving as the upper and lower load-bearing interfaces of the air cushion anti-vibration feet 70, transmitting loads and vibrations. The gas spring 73 is an elastic element that uses gas as its working medium, providing elastic support force through gas compression and expansion. It typically consists of a rubber air bladder, a metal piston, and seals, and is filled with high-pressure gas. Its stiffness can be adjusted by regulating the gas pressure. It provides primary elastic support, bears the static and dynamic loads of the punch press, and isolates vibrations. The multiple damping devices 74 are used to dissipate vibration energy, suppress vibration amplitude, and dampen the vibration process.

[0150] The damping cylinder 75 is a cylinder that uses gas or a gas-liquid mixture as the working medium, generating damping force through the flow resistance of the gas within the cavity or friction with the piston. It can be a unidirectional or bidirectional cylinder, with an internal structure designed with throttling orifices or valves to control gas flow, thereby adjusting the damping force, providing controllable damping force, and dissipating vibration energy. The paired damping mating plates 76 cooperate with the output end of the damping cylinder 75 to jointly generate damping force. They are typically made of high-strength wear-resistant materials with smooth surfaces to ensure effective contact with the clamping member 77, providing an action surface for the clamping member 77 of the damping cylinder 75 and transmitting the damping force to the base plate 71. The damping cylinder 75 is a bidirectional output cylinder, capable of outputting force in two directions, with a clamping component at its output end. Bidirectional output cylinders typically have two piston rods or a piston rod with retractable ends. By controlling the air pressure, the clamping member 77 moves outward, generating friction with the damping mating plates 76. The clamping element 77 can be a friction block, brake shoe, etc. The magnitude of the damping force can be controlled by adjusting the cylinder output pressure or the friction coefficient between the clamping element 77 and the mating plate. By actively controlling the clamping force, an adjustable damping effect can be achieved to adapt to the vibration characteristics under different working conditions.

[0151] The air cushion anti-vibration foot 70 of this embodiment effectively solves the problem of non-adjustable damping force in the prior art by introducing a controllable damping device 74. By driving the clamping member 77 to press against the damping mating plate 76 through the bidirectional output damping cylinder 75, the damping force can be dynamically adjusted according to the actual working conditions of the punch press, thereby improving the adaptability of the vibration reduction effect. This design allows the anti-vibration foot to respond more precisely to vibrations during the stamping process, effectively attenuating impact energy, reducing adverse effects on the processing accuracy of the punch press and the life of the die, and reducing vibration transmission to the factory floor and surrounding environment.

[0152] Through the above technical solution, a vibration damping system is installed at the bottom of the punch press body 1, specifically using four air cushion anti-vibration feet 70. This effectively isolates the severe vibrations and impacts generated by the punch press during high-speed stamping, preventing them from being directly transmitted to the ground or surrounding structures. The gas spring 73 inside each air cushion anti-vibration foot 70 provides flexible support, effectively bearing the weight of the punch press and absorbing most of the impact energy. Simultaneously, the bidirectional output damping cylinder 75 drives the clamping member 77 to move outward and press against the corresponding damping mating plate 76, actively generating adjustable damping force to dissipate vibration energy, suppress vibration amplitude, and attenuate the vibration process. This actively adjustable damping mechanism allows the vibration damping system to adjust its damping characteristics in real time according to changes in stamping conditions, thereby significantly improving the operating stability and stamping accuracy of the punch press, extending the service life of the molds and equipment, and reducing the impact on operators and the environment.

[0153] In a further embodiment, the aforementioned air cushion anti-vibration foot 70 also includes an automatic inflation / deflation control mechanism. This mechanism includes: a mounting bracket 79 fixed to the lower end face of the top plate 72; a trigger block 80 adjustablely mounted on the mounting bracket 79, the trigger block 80 having a first trigger portion 81 and a second trigger portion 82 arranged opposite each other in the vertical direction; and a displacement sensor 83 mounted on one of the damping mating plates 76, the trigger end of the displacement sensor 83 located between the first trigger portion 81 and the second trigger portion 82. When the bottom plate 71 moves relative to the top plate 72, the trigger end of the displacement sensor 83 contacts the first trigger portion 81 or the second trigger portion 82 and triggers a signal, which controls the inflation or deflation of the air spring 73. After the stamping die is changed on the punch press, if the machine body 1 tilts due to different die weights or center of gravity deviation, the automatic inflation / deflation control mechanism independently adjusts the air pressure of the air spring 73 of each air cushion anti-vibration foot 70, causing the punch press machine body 1 to automatically return to a horizontal position.

[0154] This automatic inflation / deflation control mechanism is designed to automatically adjust the air pressure of the air springs 73 of the air cushion anti-vibration feet 70 according to the actual posture and load changes of the punch press body 1, so as to maintain the horizontal state of the body 1. This can be achieved by: using a displacement sensor 83 to monitor the tilt angle of the body 1 or the relative displacement of each air cushion anti-vibration foot 70 in real time, and feeding the monitoring results back to the controller. The controller, according to preset logic or algorithms, instructs the inflation and deflation valves to inflate or deflate the air springs 73.

[0155] Mounting bracket 79 is used to fix the trigger block 80 and provides a support structure for the adjustable height of the trigger block 80. The mounting bracket 79 can be designed with a guide rail or threaded rod so that the trigger block 80 can be precisely adjusted vertically to accommodate different press heights or initial settings. Mounting bracket 79 is typically made of high-strength metal to ensure its stability and reliability during press operation.

[0156] The trigger block 80 serves as the physical reference for the displacement sensor 83 to detect its position. It has a first trigger portion 81 and a second trigger portion 82 arranged vertically opposite each other. These two trigger portions can be protrusions, grooves, or surfaces with specific geometric shapes, used to contact or sense the trigger end of the displacement sensor 83. The material of the trigger block 80 should have good wear resistance and stability to ensure accuracy during long-term use.

[0157] The displacement sensor 83 is used to detect the relative displacement between the base plate 71 and the top plate 72, thereby indirectly reflecting the compression state of the gas spring 73 or the tilt of the fuselage 1. This sensor can be a contact or non-contact sensor. Contact sensors, such as microswitches or limit switches, generate an electrical signal when the trigger end contacts the trigger part. Non-contact sensors, such as inductive sensors or photoelectric sensors, generate a signal when the trigger end senses the trigger part. The sensor's trigger end is located between the first trigger part 81 and the second trigger part 82, forming a detection window. When the relative position of the base plate 71 and the top plate 72 exceeds this window, the sensor is triggered.

[0158] When the displacement sensor 83 detects that the relative displacement between the bottom plate 71 and the top plate 72 exceeds a preset range and triggers a signal, this signal is sent to a control unit (e.g., a PLC or microcontroller). The control unit, based on the type of signal (e.g., contact with the first trigger 81 indicates that the gas spring 73 is overcompressed and needs to be deflated; contact with the second trigger 82 indicates that the gas spring 73 is undercompressed and needs to be inflated), drives the corresponding solenoid valve to control the air source to inflate the gas spring 73 or to expel the gas from the gas spring 73, thereby adjusting the supporting force of the gas spring 73.

[0159] The automatic inflation / deflation control mechanism independently adjusts the air pressure of the air springs 73 of each air cushion anti-vibration foot 70, causing the press body 1 to automatically return to a horizontal position. This means that each air cushion anti-vibration foot 70 is equipped with an independent automatic inflation / deflation control mechanism, or a central control system can independently control the air pressure of each air cushion anti-vibration foot 70. When the press changes molds, causing a change in weight or center of gravity, the press body 1 may tilt. At this time, the displacement sensors 83 on the air cushion anti-vibration feet 70 at different positions will detect different relative displacements and trigger corresponding signals. Based on these independent signals, the control system performs precise inflation or deflation operations on the air springs 73 of each air cushion anti-vibration foot 70 until the relative displacement of all air cushion anti-vibration feet 70 returns to a preset equilibrium state, thereby automatically restoring the press body 1 to a horizontal position. This independent adjustment capability is key to achieving high-precision horizontal calibration.

[0160] Through the above technical solution, this application effectively solves the problem of machine body 1 tilting caused by weight or center of gravity changes after mold replacement in a punch press. The displacement sensor 83 monitors the relative displacement between the base plate 71 and the top plate 72 in real time. When tilting is detected, a trigger signal is issued, and the control system independently adjusts the air pressure of the air springs 73 of each air cushion anti-vibration foot 70 according to the signal. This automated adjustment process avoids the tediousness and inaccuracy of manual intervention, ensuring that the punch press body 1 always remains level, thereby significantly improving the operating accuracy and stability of the punch press. Especially in high-precision stamping operations, the levelness of the machine body 1 is crucial to the quality of the stamped parts. This mechanism can quickly and accurately correct the posture of the machine body 1, ensuring the stability of the stamping process and the consistency of the products, and reducing the scrap rate and equipment wear caused by machine body 1 tilting.

[0161] In some embodiments of this application, the vibration damping system of the punch press employs an air cushion anti-vibration foot 70, which achieves vibration damping through a gas spring 73. However, after changing the stamping die, the punch press body 1 is prone to tilting due to changes in die weight or center of gravity. This affects the processing accuracy and stability of the punch press and requires manual adjustment, which is cumbersome and inefficient. Therefore, this application further proposes that the air cushion anti-vibration foot 70 also includes an automatic inflation / deflation control mechanism. This mechanism aims to automate the management of the air pressure of the gas spring 73 to address the tilting of the punch press body 1 caused by load changes, ensuring the punch press remains level.

[0162] Specifically, the automatic inflation / deflation control mechanism includes a mounting bracket 79 fixed to the lower end face of the top plate 72. This mounting bracket 79 provides a stable mounting base for the trigger block 80, ensuring that the trigger block 80 is fixed in position relative to the base plate 71. The trigger block 80, adjustablely mounted on the mounting bracket 79, has a first trigger portion 81 and a second trigger portion 82 arranged opposite each other in the vertical direction. The adjustability of the trigger block 80 allows for precise calibration of the horizontal reference point during initial installation or maintenance. The first trigger portion 81 and the second trigger portion 82 serve as upper and lower limits for the displacement sensor 83, jointly defining the allowable displacement range when the press body 1 is in a horizontal state. The displacement sensor 83, mounted on one of the damping mating plates 76, has its trigger end located between the first trigger portion 81 and the second trigger portion 82. This displacement sensor 83 can be a contact or non-contact sensor, such as an inductive sensor, photoelectric sensor, or microswitch, used to monitor the relative vertical displacement between the base plate 71 and the top plate 72 in real time. When the press body 1 tilts, the relative position of the base plate 71 and the top plate 72 changes, causing the trigger end of the displacement sensor 83 to contact the first trigger part 81 or the second trigger part 82. When the base plate 71 and the top plate 72 move relative to each other, the trigger end of the displacement sensor 83 contacts the first trigger part 81 or the second trigger part 82 and triggers a signal. This signal indicates that the press body 1 has deviated from a horizontal state, and it includes information on the direction of deviation (upward or downward). The signal is used to control the inflation or deflation of the gas spring 73. Upon receiving the signal, the control system inflates or deflates the corresponding gas spring 73 according to the signal indication to adjust the height of the air cushion anti-vibration foot 70. For example, if the trigger end contacts the first trigger part 81, it indicates that the height of the air cushion on that side is too high, so deflation is performed; if it contacts the second trigger part 82, it indicates that the height is too low, so inflation is performed. When the punch press body 1 tilts due to different die weights or center of gravity deviation after the punch press changes its stamping die, the automatic inflation / deflation control mechanism independently adjusts the air pressure of the air springs 73 of each air cushion anti-vibration foot 70, so that the punch press body 1 automatically returns to level. This means that each air cushion anti-vibration foot 70 is equipped with independent inflation / deflation capabilities or is controlled by a central system, which can accurately compensate for local tilting, thereby achieving automatic leveling of the entire punch press body 1.

[0163] Through the above technical solution, when the punch press changes its stamping die, causing a change in the weight or center of gravity of the machine body 1, the automatic inflation / deflation control mechanism can monitor the relative displacement between the base plate 71 and top plate 72 of the air cushion anti-vibration foot 70 in real time. Once a deviation from the horizontal state is detected, the displacement sensor 83 will immediately trigger a signal, and the control system will independently adjust the air pressure of the air spring 73 of the corresponding air cushion anti-vibration foot 70 according to the signal to perform inflation or deflation operations. This allows the punch press body 1 to automatically and quickly return to a horizontal state, effectively avoiding the tilting problem of the machine body 1 caused by die replacement, significantly improving the processing accuracy and stability of the punch press, while eliminating the tedious process of manual adjustment and improving production efficiency.

[0164] In a further embodiment, this model also includes a sealing structure disposed at the end of the aforementioned guide structure. This sealing structure is a fiberglass dust seal 85, which is made of fiberglass material impregnated with grease. It is installed at the opening of the inner cavity 31 at the upper end of the guide seat 26, and the inner end of the fiberglass dust seal 85 is in sealing sliding contact with the guide post 23. A pressure ring 86 is also included, which is fixedly disposed at the upper end of the guide seat 26 and presses the fiberglass dust seal 85 tightly against the opening.

[0165] Specifically, sealing structures are typically used to prevent impurities such as particulate matter and liquids from the external environment from entering the interior of precision mechanical parts, or to prevent internal lubricant leakage, thereby maintaining the cleanliness, lubrication condition, and operational accuracy of the mechanical system. A fiberglass dust seal 85 is a seal made of fiberglass material, primarily used to block dust and particulate matter. Fiberglass material has good wear resistance, corrosion resistance, and a certain degree of flexibility, allowing it to adapt to slight deformation of components and providing an effective dust barrier. Impregnating fiberglass material with grease can significantly enhance the sealing performance of the dust seal. Grease, as a semi-solid lubricant, can fill the micropores of the fiberglass material, forming a denser barrier and effectively blocking the intrusion of fine dust. At the same time, grease also has adhesive properties, capable of adsorbing ingressed microparticles and providing lubrication to sliding contact surfaces, reducing wear. The guide seat 26 is an important component of the guide structure. The opening of its upper inner cavity 31 is the main channel connecting the external environment with the interior of the guide structure. Installing the dust seal here can block the path of contaminants into the interior of the guide structure at the source, protecting the internal guide post 23, guide sleeve 24, and rolling assembly 25. The inner end of the fiberglass dust seal 85 makes a sealing sliding contact with the guide post 23. This contact method ensures that the dust seal remains in close contact with the guide post 23 as the guide post 23 moves axially, forming a dynamic seal. The sliding contact effectively removes deposits from the surface of the guide post 23 and prevents external contaminants from entering through this interface. Simultaneously, because the dust seal is impregnated with grease, this sliding contact also provides lubrication, reduces frictional resistance, and extends the service life of the dust seal itself.

[0166] By employing the aforementioned technical solution, a fiberglass dust seal 85 is installed at the end of the guide structure and impregnated with grease. This effectively solves the problem of decreased precision and wear caused by dust, debris, and other contaminants entering the guide structure during the operation of the punch press. Specifically, the grease-impregnated fiberglass dust seal 85 is installed at the opening of the inner cavity 31 at the upper end of the guide seat 26, with its inner end in sealed sliding contact with the guide post 23, forming a reliable dynamic sealing barrier. The grease not only fills the micropores of the dust seal, enhancing its ability to block fine dust, but also adsorbs the intruding particles and provides lubrication for the sliding between the guide post 23 and the dust seal, thereby reducing friction and wear. This sealing method ensures that the interior of the guide structure, especially the rolling assembly 25, always maintains a clean operating environment, effectively preventing contaminants from adversely affecting the guiding accuracy and motion stability, and significantly improving the long-term stability and service life of the punch press.

[0167] The following example will provide a more detailed explanation of the above technical solution: We have found that existing punch presses, after prolonged high-speed operation, suffer from decreased stamping accuracy and increased scrap rate due to issues such as component thermal deformation, insufficient lubrication, and vibration. To address these challenges, we propose a novel high-precision, high-stability punch press.

[0168] Overall structure and transmission mechanism The press body 1 serves as the overall support structure, integrating the main moving parts. The crankshaft 2 is mounted on the body 1, serving as the power input. Two slide blocks 3 are located on each side of the press's transmission mechanism, sliding horizontally with the body 1 to ensure smooth movement. A counterweight 12 is located above the transmission mechanism, sliding vertically with the press's top seat 5 to balance inertial forces. A slider 6 is located below the transmission mechanism, used to mount the press die.

[0169] To achieve high-precision transmission, the punch press employs a unique linkage connection method. The first end of the upper connecting rod 7 is hinged to the counterweight 12, and its second end is hinged to the slide 3. The first end of the lower connecting rod 8 is hinged to the slider 6, and its second end is hinged to the slide 3. The first end of the drive connecting rod 9 is connected to the crankshaft 2, and its second end is hinged to the slide 3. The second ends of the upper connecting rod 7, the lower connecting rod 8, and the drive connecting rod 9 are coaxially hinged to the shaft hole 11 of the slide 3 via the same rotating shaft 10. This coaxial hinge design ensures the synchronization and precision of the movement of the three connecting rods at the slide 3, avoiding motion interference and precision loss that may occur with traditional multi-point hinges, thereby improving the stability of the entire transmission chain.

[0170] To address the precision issues caused by thermal deformation during high-speed operation of traditional punch presses, this punch press has been optimized in terms of material selection and thermal management of key moving parts.

[0171] The slide body 13 is made of alloy steel with a low coefficient of thermal expansion, for example, the average coefficient of linear expansion in the range of 20~60℃ is no greater than 2×10. -6 The slide body 13 is made of alloy steel with a low coefficient of friction. The sliding mating surface 14 on the outer side of the slide body 13 and the inner wall of the shaft hole 11 are both provided with a sliding layer material with a low coefficient of friction. This sliding layer material can be cast integrally with the slide body 13 to form a composite structure, or fixed by a separate connection method. Compared with the traditional copper alloy slide 3 with a high coefficient of thermal expansion, this low-thermal-expansion alloy steel slide 3 significantly reduces dimensional changes at operating temperatures, effectively controls the gap fluctuation between the sliding mating surface 14 and the body 1, and ensures the accuracy of the motion trajectory. At the same time, the application of the low-friction coefficient sliding layer reduces frictional heat generation and ensures the stable establishment of the lubricating oil film at different temperatures, avoiding boundary lubrication or even dry friction, and extending the service life of the components.

[0172] Similarly, at least one of the upper connecting rod 7, lower connecting rod 8, and drive connecting rod 9 has a connecting rod body made of alloy steel with a low coefficient of thermal expansion, and the inner wall of the shaft hole 11 of the connecting rod body is provided with a sliding layer material with a low coefficient of friction. This material selection also helps to suppress thermal deformation of the connecting rod during operation and maintain the geometric accuracy of the shaft hole 11. The connecting rod can be a double-shaft-hole connecting rod with shaft holes 11 at both ends, or a ball-end connecting rod with shaft hole 11 at one end and ball head 22 at the other end. The second end of the double-shaft-hole connecting rod can adopt a split structure or a clamping structure. The split structure includes a connecting rod body end 20 and a detachably connected end cap 16, which is fixedly connected by fasteners. The shaft hole 11 of the clamping structure has an axially penetrating opening slit 18 in the circumferential direction, and connecting holes are provided on both sides of the opening slit 18. The radial clamping force of the shaft hole 11 is adjusted by applying torque through fasteners through the connecting holes. These structural designs ensure high-strength transmission while facilitating assembly and maintenance. They also allow for the adjustment of clamping force to compensate for minute gaps, further improving transmission accuracy.

[0173] To cope with the large amount of heat conducted from the bottom of the slider 6 during high-speed stamping, the slider 6 is made of one-piece molded silicon carbide particle-reinforced aluminum matrix composite material, and has an oil cooling channel 54 inside. This oil cooling channel 54 includes at least one oil passage located inside the slider 6 and directly below the main slider rib 58. The two ends of the oil passage extend to the sides of the slider 6, forming an oil inlet and an oil outlet, respectively. The slider 6 includes an upper plate 59, a lower plate 60, and multiple main slider ribs 58 connecting the upper plate 59 and the lower plate 60. The lower plate 60 is used to mount the stamping die. The oil cooling channel 54 is located above the lower plate 60 and directly below each main slider rib 58, and is arranged along the length of the main slider rib 58. The oil cooling channel 54 can be designed as a unidirectional oil passage or a circuitous oil passage. Compared with traditional integral cooling chambers, this design precisely guides the cooling medium to areas with high heat flux density, avoids flow dead zones, achieves more uniform and efficient cooling, effectively suppresses thermal deformation of slider 6, maintains the stability of the fit clearance between slider 6 and guide rail, and thus ensures stamping accuracy.

[0174] like Figure 3 As shown, when the punch press starts working, the external cooling system (e.g., oil cooler 68) pumps cooling oil into the oil inlet of the slide block through the oil inlet pipe 151. After entering the oil cooling channel, the cooling oil flows along the flow channel. Since the oil cooling channel is located immediately above the lower plate and directly below the main rib of the slide block, the cooling oil can directly and efficiently absorb the heat transferred from the mold to the lower plate and the main rib of the slide block; finally, it flows back to the oil cooler 68 through the oil outlet pipe 152.

[0175] A guide structure is provided between the punch press frame and the slide block 6 to ensure the precise vertical movement of the slide block 6. The guide structure includes a guide post 23, a guide sleeve 24 sleeved on the outside of the guide post 23, a rolling assembly 25 disposed inside the guide sleeve 24 and in rolling contact with the guide post 23, and a guide seat 26 fixedly disposed at the end of the guide sleeve 24 to limit the axial movement stroke of the guide post 23.

[0176] This guiding structure can be a high-precision guiding structure. Multiple axially extending cross-sections 27 are provided on the outer wall of the guide post 23. The rolling assembly 25 includes a bearing cage 34 and multiple rollers 35. The bearing cage 34 is axially movable within the guide sleeve 24, and the multiple rollers 35 are mounted on the bearing cage 34. Each roller 35 corresponds to and rolls in contact with one cross-section 27 of the guide post 23. The rollers 35 are cylindrical, and their axial direction is perpendicular to the axial direction of the guide post 23. This design, through multi-point rolling contact, significantly improves load-bearing capacity and guiding accuracy, avoids the stress concentration problem of point contact in traditional ball bearings, and reduces frictional heat generation.

[0177] The guide structure can also be an adjustable stroke guide structure. The rolling assembly 25 includes a base 36, which is fixedly disposed within the guide sleeve 24. A circulating raceway 37 is provided on the base 36, and multiple rollers 35 are installed in the circulating raceway 37 and can circulate along the circulating raceway 37. The base 36 is elongated, and multiple mounting slots 40 are arranged axially at intervals on it. Each mounting slot 40 is provided with a circulating raceway body 38. Each circulating raceway body 38 and the rollers 35 therein form a rolling support unit 39. Multiple rolling support units 39 are distributed axially at intervals and jointly roll in contact with the corresponding tangential surface 27. This design makes the effective stroke of the guide post 23 no longer limited by the length of the guide sleeve 24. By adjusting the arrangement of the rolling support units 39, it can adapt to different stroke requirements and improve the process adaptability of the equipment.

[0178] Furthermore, the guide structure can also be a combined guide structure. It also includes a copper sleeve 41 fixedly disposed within the guide sleeve 24, with the copper sleeve 41 slidingly engaged with the guide post 23. The rolling assembly 25 includes a guide sleeve body 42, a cage 43, and multiple balls 44. The guide sleeve body 42 is fixed within the guide sleeve 24 and located below the copper sleeve 41. An annular gap 45 is formed between the guide sleeve body 42 and the guide post 23. The cage 43 is slidably disposed within the annular gap 45 along the axial direction. The multiple balls 44 are mounted on the cage 43, and the outer circumferential surface of each ball 44 makes rolling contact with the inner wall of the guide sleeve body 42 and the outer wall of the guide post 23, respectively. This combined design combines the advantages of sliding and rolling, providing high load-bearing capacity while ensuring smooth and precise movement.

[0179] The punch press also integrates a constant-temperature lubrication oil circuit system inside the machine body 1, solving the problems of insufficient lubrication and oil temperature fluctuations caused by traditional external pipelines. This system includes an oil storage chamber 62 located within the machine body 1 and an internal oil passage 63 connected to the oil storage chamber 62 within the longitudinal support beam. An oil pump 64 pumps oil from the oil storage chamber 62 to a distributor 65. The distributor 65 delivers oil through multiple oil supply branches to: spray lubrication of the moving parts of the crank mechanism; pressure lubrication of the connection between the crankshaft 2 and the drive connecting rod 9; lubrication of the sliding mating surface 14 of the slider 3, the shaft 10, and the connection between the shaft 10 and the second end of each connecting rod; and lubrication of the sliding bearing interface formed between the guide post 23 and the guide sleeve 24. After the oil collects above the stamping area, it flows back to the oil storage chamber 62 via the internal oil passage 63 within the longitudinal support beam.

[0180] The constant-temperature lubrication system also includes an oil cooler 68, which is circulated to the oil reservoir 62 to achieve precise control of the oil temperature. The second oil supply branch 662 of the distributor 65 is connected to the crankshaft 2, and oil is delivered to the connection point between the crankshaft 2 and the drive connecting rod 9 via the internal oil passage 87 of the crankshaft, forming pressure lubrication and ensuring reliable lubrication under heavy loads. The third oil supply branch 663 of the distributor 65 is connected to the sliding mating surface 14 of the slide block 3, and oil is delivered to the rotating shaft 10 via the internal oil passage 88 of the slide block. The rotating shaft 10 has an internal common hinge shaft oil passage 89, which delivers oil to the respective connection points between the rotating shaft 10 and the upper connecting rod 7, lower connecting rod 8, and the second end of the drive connecting rod 9, solving the problem of insufficient lubrication of these hidden critical friction pairs in traditional solutions. The fourth oil supply branch 664 of the distributor 65 is connected between the guide post 23 and the guide sleeve 24 to form a sliding bearing lubrication interface, effectively reducing friction and wear. This integrated, closed-loop controlled lubrication system ensures adequate lubrication and constant oil temperature for all critical friction pairs, significantly improving the operational stability and lifespan of the equipment.

[0181] To effectively absorb the impact vibration generated by high-speed stamping, a vibration damping system is installed at the bottom of the press body 1. This system consists of four air cushion anti-vibration feet 70, which are respectively located at the four corners of the press body 1. Each air cushion anti-vibration foot 70 includes a base plate 71 and a top plate 72. A gas spring 73 is located between the base plate 71 and the top plate 72, with its upper and lower ends connected to the base plate 71 and the top plate 72, respectively. Multiple damping devices 74 are distributed between the base plate 71 and the top plate 72. Each damping device 74 includes a damping cylinder 75, which is installed on the lower end face of the top plate 72; and a pair of damping mating plates 76, which are fixed to the upper end face of the base plate 71. The damping cylinder 75 is located between the two pairs of damping mating plates 76. The damping cylinder 75 is a bidirectional output cylinder, with a clamping element 77 installed at each of its two output ends. The damping cylinder 75 drives the clamping element 77 to move outward and press against the corresponding damping mating plate 76, thereby generating a damping force. Compared with traditional anti-vibration feet with fixed damping force, this system can dynamically adjust the damping force according to the stamping load and vibration conditions to achieve adaptive vibration reduction.

[0182] The air cushion anti-vibration foot 70 also includes an automatic inflation / deflation control mechanism. This mechanism includes a mounting bracket 79 fixed to the lower end face of the top plate 72; a trigger block 80 adjustablely mounted on the mounting bracket 79, the trigger block 80 having a first trigger portion 81 and a second trigger portion 82 arranged opposite each other in the vertical direction; and a displacement sensor 83 mounted on one of the damping mating plates 76, the trigger end of the displacement sensor 83 located between the first trigger portion 81 and the second trigger portion 82. When the bottom plate 71 moves relative to the top plate 72, the trigger end of the displacement sensor 83 contacts the first trigger portion 81 or the second trigger portion 82 and triggers a signal, which is used to control the inflation or deflation of the air spring 73. After changing the stamping die on the punch press, if the machine body 1 tilts due to different die weights or center of gravity deviation, the automatic inflation / deflation control mechanism independently adjusts the air pressure of the air spring 73 of each air cushion anti-vibration foot 70, causing the punch press machine body 1 to automatically return to a horizontal position. This active vibration reduction and leveling system solves the problems of unadjustable damping force and cumbersome manual leveling in traditional solutions, ensuring that the punch press can maintain optimal dynamic stability and levelness under various working conditions.

[0183] A sealing structure is provided at the end of the guide structure to prevent external dust from entering the mating gap between the guide post 23 and the guide sleeve 24. This sealing structure is a glass fiber dust seal 85, which is made of glass fiber material impregnated with grease. It is installed at the opening of the inner cavity 31 at the upper end of the guide seat 26, and the inner end of the glass fiber dust seal 85 is in sealing sliding contact with the guide post 23. In addition, a pressure ring 86 is included, which is fixedly installed at the upper end of the guide seat 26 and presses the glass fiber dust seal 85 tightly against the opening. Compared with traditional rubber oil seals, the grease-impregnated glass fiber dust seal 85 has a lower coefficient of friction and better wear resistance, avoiding material aging and decreased sealing performance caused by frictional heat during high-speed reciprocating motion. It also reduces abnormal noise and dependence on the lubrication system, effectively protecting the cleanliness of the guide structure's interior and extending its service life and accuracy.

[0184] Through the synergistic effect of the aforementioned technical features, this press exhibits superior performance in high-speed, high-precision stamping operations. The application of low-thermal-expansion materials suppresses thermal deformation at its source, ensuring the dimensional stability of moving parts; the coaxial hinge structure improves transmission accuracy; the efficient slider 6 cooling system maintains the geometric accuracy of slider 6; the advanced guiding structure ensures the vertical movement accuracy and stroke adaptability of slider 6; the integrated lubrication and temperature control oil circuit system ensures sufficient lubrication and temperature stability of key friction pairs; the active vibration damping and leveling system provides excellent dynamic stability and levelness; and the innovative sealing structure effectively prevents contamination. These technical features are interconnected and mutually supportive, jointly constructing a high-precision, high-stability stamping platform, significantly improving the quality of stamped parts and production efficiency.

[0185] The above description is merely an embodiment of this application and is not intended to limit the scope of protection of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of protection of this application.

Claims

1. A high-precision, high-stability punch press, characterized in that, include: Fuselage (1); A crankshaft (2) is mounted on the fuselage (1); Two sliders (3) are respectively set on the left and right sides of the transmission mechanism and slide in cooperation with the body (1) in the horizontal direction; The counterweight (12) is located above the transmission mechanism and slides in a vertical direction with the top seat (5) of the punch press. The slider (6) is located below the transmission mechanism and is used to install the punch die; The upper connecting rod (7) has its first end hinged to the counterweight (12) and its second end hinged to the slider (3); The lower connecting rod (8) has its first end hinged to the slider (6) and its second end hinged to the slide (3); The drive link (9) has its first end connected to the crankshaft (2) and its second end hinged to the slider (3); The second end of the upper connecting rod (7), the second end of the lower connecting rod (8) and the second end of the driving connecting rod (9) are coaxially hinged to the shaft hole (11) of the slider (3) through the same rotating shaft (10); The slide (3) includes: The slide body (13) is made of alloy steel with a low coefficient of thermal expansion; A sliding mating surface (14) is provided on the outer side of the slider body (13); A shaft hole (11) is formed on the slide body (13); The sliding mating surface (14) and the inner wall of the shaft hole (11) are provided with a sliding layer material; At least one of the upper connecting rod (7), the lower connecting rod (8), and the driving connecting rod (9) has a connecting rod body made of low thermal expansion coefficient alloy steel, and the inner wall of the connecting rod shaft hole (21) of the connecting rod body is provided with a sliding layer material; the average linear expansion coefficient of the low thermal expansion coefficient alloy steel in the range of 20~60℃ is not greater than 2×10 -6 / K; It also includes a guide structure disposed between the punch press frame and the slide (6), the guide structure comprising: The guide post (23) has multiple axially extending cross-sections (27) on its outer wall; A guide sleeve (24) is fitted over the outside of the guide post (23); A rolling assembly (25) is disposed within the guide sleeve (24) and rolls in contact with the guide post (23); The guide seat (26) is fixedly disposed at the end of the guide sleeve (24) and is used to limit the axial movement stroke of the guide post (23); The cut surface (27) is a plane and is evenly or unevenly arranged along the circumference of the guide post (23); the guide post (23) has an upper column (28) with a larger diameter and a lower column (29) with a smaller diameter, and an annular step surface (30) is formed between the upper column (28) and the lower column (29); the cut surface (27) is provided on the outer peripheral wall of the lower column (29); the guide sleeve (24) is sleeved on the outside of the lower column (29).

2. The high-precision, high-stability punch press according to claim 1, characterized in that, The sliding layer material and the slide body (13) are a composite structure integrally cast, or the sliding layer material is fixed to the slide body (13) in a separate connection manner; the low thermal expansion coefficient alloy steel has an average linear expansion coefficient of no more than 2×10 in the range of 20~60℃. -6 / K.

3. The high-precision, high-stability punch press according to claim 1, characterized in that, The connecting rod is a double-axis hole type connecting rod with shaft holes at both ends, or a ball-head type connecting rod with a connecting rod shaft hole (21) at one end and a ball head (22) at the other end; the second end of the double-axis hole type connecting rod adopts a split structure or a clamping structure; the split structure includes a connecting rod body end (20) and a detachably connected end cap (16), and the end cap (16) is fixedly connected by fasteners; the connecting rod shaft hole (21) of the clamping structure has an axially penetrating opening gap (18) in the circumferential direction, and a connecting hole (19) is provided on both sides of the opening gap (18), and the radial clamping force of the connecting rod shaft hole (21) is adjusted by fasteners passing through the connecting holes (19) and applying torque.

4. The high-precision, high-stability punch press according to claim 1, characterized in that, The guide sleeve (24) is fixedly provided with a guide seat (26) at its end. The guide seat (26) has an inner cavity (31) for accommodating the upper section (28) of the guide post (23) and allowing the guide post (23) to move axially up and down in the inner cavity (31). A limiting structure (32) is provided on the guide seat (26). The limiting structure (32) cooperates with the annular step surface (30) to limit the maximum downward stroke of the guide post (23). The limiting structure (32) is an annular retaining ring, which is fixedly installed on the inner wall of the annular opening at the lower end of the guide seat (26).

5. The high-precision, high-stability punch press according to claim 1, characterized in that, The guide structure is a high-precision guide structure. The rolling assembly (25) includes a bearing cage (34) and a plurality of rollers (35). The bearing cage (34) is axially movable inside the guide sleeve (24). The plurality of rollers (35) are mounted on the bearing cage (34). Each roller (35) corresponds to a cross-section (27) of the guide post (23) and rolls in contact with it. The roller (35) is cylindrical and its axial direction is perpendicular to the axial direction of the guide post (23).

6. The high-precision, high-stability punch press according to claim 1, characterized in that, The guide structure is an adjustable stroke guide structure. The rolling assembly (25) includes a base (36), which is fixedly installed in the guide sleeve (24). A circulating raceway (37) is provided on the base (36). Multiple rollers (35) are installed in the circulating raceway (37) and can circulate along the circulating raceway (37). The base (36) is long and has multiple mounting slots (40) arranged at intervals along the axial direction. Each mounting slot (40) is provided with a circulating raceway body (38). Each circulating raceway body (38) and the rollers (35) therein form a rolling support unit (39). Multiple rolling support units (39) are distributed at intervals along the axial direction and roll in contact with the corresponding cut surface (27).

7. The high-precision, high-stability punch press according to claim 1, characterized in that, The guide structure is a combined guide structure, which also includes a copper sleeve (41) fixedly disposed in the guide sleeve (24), and the copper sleeve (41) is slidably engaged with the guide post (23); the rolling assembly (25) includes a guide sleeve body (42), a retainer (43) and a plurality of balls (44), the guide sleeve body (42) is fixed in the guide sleeve (24) and located below the copper sleeve (41), an annular gap (45) is formed between the guide sleeve body (42) and the guide post (23), the retainer (43) is slidably disposed in the annular gap (45) along the axial direction, and the plurality of balls (44) are mounted on the retainer (43), and the outer peripheral surface of each ball (44) makes rolling contact with the inner wall of the guide sleeve body (42) and the outer wall of the guide post (23).

8. The high-precision, high-stability punch press according to claim 7, characterized in that, The upper end of the copper sleeve (41) has a flange (46) extending radially outward, the flange (46) being mounted on the cavity end face of the guide sleeve (24); a cap (47) is fixedly provided at the end of the guide sleeve (24), the cap (47) being pressed against the upper surface of the flange (46) to restrict the axial displacement of the copper sleeve (41) and the rolling assembly (25); the upper end of the copper sleeve (41) and the inner wall of the cavity of the guide sleeve (24), and the copper sleeve (41) A sealing ring (48) is provided between the upper end of the sleeve (41) and the guide post (23). The cover (47) presses the sealing ring (48) into the sealing cavity opened at the upper end of the copper sleeve (41). A retaining ring (50) is provided at the lower end of the mounting cavity of the guide sleeve (24). The lower end of the guide sleeve body (42) abuts against the retaining ring (50). The retainer (43) and its ball bearings (44) are located between the retaining ring (50) and the lower end face of the copper sleeve (41) and can slide axially.

9. The high-precision, high-stability punch press according to claim 7 or 8, characterized in that, The copper sleeve (41) has an oil hole (51) that connects its inner and outer walls. The guide sleeve (24) has an oil inlet hole (52) and an oil return hole (53). The oil inlet hole (52) and the oil return hole (53) are respectively connected to the oil hole (51) of the copper sleeve (41). The oil inlet hole (52) and the oil return hole (53) are located at different positions in the axial direction of the copper sleeve (41) to form a lubricating oil circulation path.

10. The high-precision, high-stability punching machine according to claim 1, characterized in that, The slider (6) is an integrally formed silicon carbide particle-reinforced aluminum matrix composite slider. The punch press also includes an oil cooling channel (54) disposed inside the slider (6). The oil cooling channel (54) includes at least one oil passage opened inside the slider (6) and located directly below the main rib (58) of the slider. The two ends of the oil passage extend to the side of the slider (6) and form an oil inlet and an oil outlet respectively.

11. The high-precision, high-stability punch press according to claim 10, characterized in that, The slider (6) includes an upper plate (59), a lower plate (60), and multiple slider main ribs (58) connecting the upper plate (59) and the lower plate (60). The lower plate (60) is used to install the punch die. The oil cooling channel (54) is located above the lower plate (60) and directly below each slider main rib (58), and is arranged along the length direction of the slider main rib (58). The oil cooling channel (54) is a unidirectional oil passage or a detour oil passage.

12. The high-precision, high-stability punch press according to claim 1, characterized in that, It also includes a constant temperature lubrication oil circuit system integrated into the fuselage (1), the constant temperature lubrication oil circuit system comprising: Oil storage chamber (62) located in fuselage (1) and oil passage (63) inside longitudinal support beam connected to oil storage chamber (62); Oil pump (64), distributor (65) and multiple oil supply branches; The oil pump (64) is used to pump oil from the oil storage chamber (62) to the distributor (65); The distributor (65) delivers oil to the following locations via the oil supply branches: (i) The moving parts of the crank mechanism, used for spray lubrication; (ii) The connection between the crankshaft (2) and the drive connecting rod (9); (iii) The sliding mating surface (14) of the slider (3), the pivot (10), and the sleeve joint between the pivot (10) and the second end of the upper connecting rod (7), the lower connecting rod (8), and the drive connecting rod (9); (iv) Between the guide post (23) and the guide sleeve (24); After the oil collects above the stamping area, it flows back to the oil storage chamber (62) through the oil passage (63) inside the longitudinal support beam.

13. The high-precision, high-stability punch press according to claim 12, characterized in that, The constant temperature lubrication oil circuit system also includes an oil cooler (68), which is circulatedly connected to the oil storage chamber (62); the first oil supply branch (661) of the distributor (65) is connected to the top of the dynamic balance guide column (90), and the oil is sprayed onto the crankshaft (2), upper connecting rod (7), lower connecting rod (8) and drive connecting rod (9) of the crank mechanism through the internal oil passage of the dynamic balance guide column (90); the second oil supply branch (662) of the distributor (65) is connected to the crankshaft (2), and the oil is transported to the crankshaft (2) and drive connecting rod (9) through the internal oil passage (87) of the crankshaft. At the joint, pressure lubrication is formed; the third oil supply branch (663) of the distributor (65) is connected to the sliding mating surface (14) of the slide (3), and is transported to the rotating shaft (10) through the internal oil passage (88) of the slide. The rotating shaft (10) is provided with an internal oil passage (89) of a common hinge shaft, which is used to transport oil to the joints of the rotating shaft (10) with the upper connecting rod (7), the lower connecting rod (8) and the second end of the drive connecting rod (9); the fourth oil supply branch (664) of the distributor (65) is connected between the guide post (23) and the guide sleeve (24), which is used to form a sliding bearing lubrication interface.

14. The high-precision, high-stability punch press according to claim 1, characterized in that, It also includes a vibration damping system located at the bottom of the punch press body (1), the vibration damping system consisting of four air cushion anti-vibration feet (70), respectively located at the four corners of the punch press body (1); each of the air cushion anti-vibration feet (70) includes: Bottom plate (71) and top plate (72); A gas spring (73) is disposed between the base plate (71) and the top plate (72), and its upper and lower ends are respectively connected to the base plate (71) and the top plate (72); Multiple damping devices (74) are distributed between the bottom plate (71) and the top plate (72), each damping device (74) comprising: A damping cylinder (75) is installed on the lower end face of the top plate (72); A pair of damping mating plates (76) are fixed to the upper end face of the base plate (71), and the damping cylinder (75) is located between the two pairs of damping mating plates (76); The damping cylinder (75) is a bidirectional output cylinder, with clamping parts (77) respectively provided at its two output ends. The damping cylinder (75) drives the clamping parts (77) to move outward and press against the corresponding damping mating plate (76), thereby generating damping force.

15. The high-precision, high-stability punch press according to claim 14, characterized in that, The air cushion shock absorber foot (70) also includes an automatic inflation / deflation control mechanism, which includes: Mounting bracket (79) fixed to the lower end face of the top plate (72); A trigger block (80) is adjustablely mounted on the mounting bracket (79), the trigger block (80) having a first trigger part (81) and a second trigger part (82) arranged opposite to each other in the vertical direction; A displacement sensor (83) is mounted on one of the damping mating plates (76), and the trigger end of the displacement sensor (83) is located between the first trigger part (81) and the second trigger part (82); When the base plate (71) moves relative to the top plate (72), the trigger end of the displacement sensor (83) contacts the first trigger part (81) or the second trigger part (82) and triggers a signal, which is used to control the inflation or deflation of the gas spring (73); When the machine body (1) tilts due to different die weights or center of gravity deviation after the stamping die is changed, the automatic inflation and deflation control mechanism independently adjusts the air pressure of the air springs (73) of each air cushion anti-vibration foot (70) so that the machine body (1) of the stamping press can automatically return to level.

16. The high-precision, high-stability punch press according to claim 1, characterized in that, It also includes a sealing structure disposed at the end of the guide structure, the sealing structure being a glass fiber dust seal (85), the glass fiber dust seal (85) being a glass fiber material impregnated with grease, installed at the opening of the upper inner cavity (31) of the guide seat (26), and the inner end of the glass fiber dust seal (85) being in sealed sliding contact with the guide post (23).

17. The high-precision, high-stability punch press according to claim 16, characterized in that, It also includes a pressure ring (86), which is fixedly disposed on the upper end of the guide seat (26) and presses the glass fiber dust seal (85) tightly against the opening.

Images