Automobile ball cage holder press machine
Through a mechanical linkage structure driven by a single press, precise stamping and adaptive angle flipping of automotive ball cage cages are achieved, solving the problems of high cost and poor flexibility of existing equipment, and realizing efficient and low-consumption production of multiple models.
Patent Information
- Application Number
- CN202610063238.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2026-01-19
- Publication Date
- 2026-03-03
- Estimated Expiration
- Not applicable · inactive patent
AI Technical Summary
Existing automotive ball cage presses require an additional independent drive source, increasing equipment costs and energy consumption. At the same time, the flipping mechanism cannot adapt to production needs with different numbers of holes, limiting the equipment's versatility and flexibility.
Using a single press as the core drive source, the stamping and flipping functions are realized through a mechanical linkage structure. By adjusting the meshing position of segmented gears and movable gears, the angle adaptive adjustment and the precise flipping of the flipping unit are realized, meeting the flexible production needs of multiple product models.
It simplifies the equipment structure, reduces energy consumption, saves production costs, and can punch out mounting holes with uniform spacing and variable number on the same specification cage to meet the production needs of multiple product models.
Smart Images
Figure CN121589178A_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of press technology, and more particularly to an automotive ball cage cage press. Background Technology
[0002] The cage is a core component of the automotive CV joint, typically with a ring-shaped structure and multiple sets of mounting holes evenly distributed on its outer wall. During production, these holes are primarily formed by stamping with a press. To ensure even distribution of the holes and avoid overlapping stamping positions, existing technology requires an additional fine-tuning and tilting mechanism to assist the press: each time the press completes a stamping cycle, the tilting mechanism drives the cage to rotate synchronously by a fixed angle to achieve precise indexing.
[0003] However, the existing flipping mechanism has two major technical defects: first, it requires an independent drive source, which increases equipment cost and energy consumption; second, the rotation angle is fixed, which cannot adapt to the production needs of different numbers of holes. In actual production, the same model of cage often needs to be punched with 5 to 8 holes (with consistent spacing requirements), but the fixed angle flipping mechanism will result in a fixed number of holes. If the number needs to be adjusted, the mechanism must be replaced, which seriously limits the versatility and flexibility of the equipment. Summary of the Invention
[0004] In view of the problems existing in the above-mentioned automotive CV cage press, the present invention proposes an automotive CV cage press to solve such problems.
[0005] To solve the above-mentioned technical problems, the present invention provides the following technical solution: an automotive ball cage retainer press, comprising a base, a press body, a stamping unit, and a flipping unit, wherein the flipping unit includes a transmission component disposed on one side of the stamping unit, an adjustment component located on the side of the transmission component with the end of the adjustment component sleeved on the end of the transmission component, a segmented gear located on one side of the end of the transmission component, a first transmission shaft horizontally disposed in the base with one end of the first transmission shaft meshing with the side of the segmented gear, a second transmission shaft vertically disposed at the other end of the first transmission shaft, and a flipping component horizontally disposed at the top end of the second transmission shaft; The segmented gear has a tapered structure that is thinner at the bottom and thicker at the top. The tapered structure is divided into multiple stages from the thin end to the thick end, and the diameter of each stage is different.
[0006] As a preferred embodiment of the automotive ball cage retainer press of the present invention, the stamping unit includes a main body located on a base, a fixed frame disposed on the side of the main body, a main shaft inserted into the main body and whose top end abuts against the press body, a top block matched and disposed at the end of the main shaft, a rocker plate disposed laterally between the main shaft and the top block, a pressing knife disposed at the outer end of the rocker plate, and a clearance groove opened in the main body.
[0007] In a preferred embodiment of the automotive ball cage cage press of the present invention, the transmission component includes a connecting shaft inserted into a relief groove, the top end of the connecting shaft being fixedly connected to the side of the main body, a guide sleeve rotatably connected to the lower end of the connecting shaft, an extension shaft inserted into the lower end of the guide sleeve, and a rectangular shaft fixedly connected to the lower end of the extension shaft.
[0008] As a preferred embodiment of the automotive ball cage retainer press of the present invention, wherein: multiple sets of spiral guide grooves are uniformly opened on the outer wall of the guide sleeve, and the spiral number of the guide groove is 0.5; an internal gear groove is opened inside the guide sleeve, and the internal gear groove has a long depth in the vertical direction; a set of balls is provided at the end of each set of guide grooves, and the outer end of the balls is fixedly connected to the inner wall of the relief groove.
[0009] As a preferred embodiment of the automotive ball cage retainer press of the present invention, wherein: a one-way gear is fixedly connected to the top end of the extension shaft, and the one-way gear is located in the inner gear groove; multiple sets of clamping blocks are equally distributed on the outer ring of the one-way gear, and the clamping blocks mesh with the tooth groove of the inner gear groove.
[0010] As a preferred embodiment of the automotive ball cage cage press of the present invention, the adjusting component includes a movable gear sleeved on a rectangular shaft, and the movable gear meshes with a segmented gear for transmission. At the same time, the side of the movable gear is perpendicular to the hypotenuse of the segmented gear. A bracket is provided on the upper and lower sides of the movable gear, and a threaded shaft is provided vertically at the end of the bracket, and the upper end of the threaded shaft is threadedly connected to the main body.
[0011] As a preferred embodiment of the automotive ball cage retainer press of the present invention, wherein: both ends of the first drive shaft are provided with bevel gears, the inner end of the first drive shaft meshes with the segmented gear, both ends of the second drive shaft are provided with bevel gears, and the lower end of the second drive shaft meshes with the outer end of the first drive shaft.
[0012] As a preferred embodiment of the automotive ball cage retainer press of the present invention, the flipping component includes a mounting bracket located at the top end of the second drive shaft, a conical wheel sleeve rotatably disposed at one end of the mounting bracket, the inner side of the conical wheel sleeve meshing with a bevel gear at the top end of the second drive shaft, a hexagonal shaft laterally inserted into the shaft center of the conical wheel sleeve, a telescopic cylinder connected to the outer end of the hexagonal shaft, and a limiting part disposed at the inner end of the hexagonal shaft.
[0013] In a preferred embodiment of the automobile ball cage retainer press of the present invention, a plurality of abutment blocks are evenly arranged around the outer wall of the limiting part, and the two sides of the abutment blocks are downward inclined surfaces, and a spring is provided between each set of abutment blocks and the limiting part.
[0014] In a preferred embodiment of the automotive ball cage retainer press of the present invention, the base is provided with a material unloading rack, which is located on the side of the flipping component. A guide groove is provided between the stamping unit and the flipping component, and the inner side of the guide groove is inclined towards the side of the base.
[0015] The beneficial effects of this invention are as follows: It uses a single press as the core driving source and achieves dual functions through a mechanical linkage structure: on the one hand, it drives the stamping head to complete the precise stamping and punching of the cage; on the other hand, it synchronously drives the flipping unit to perform a fixed-angle flipping action, so that the cage automatically rotates to the next angle after a single stamping. No additional independent driving device is required, which effectively simplifies the equipment structure, reduces energy consumption, and saves production costs. The flipping unit has an angle adaptive adjustment function, which can precisely adjust the single flipping angle according to the number of punches required for actual production. Specifically, by adjusting the meshing position of the movable gear and the segmented gear, the transmission ratio between the two is changed, thereby controlling the rotation angle of the flipping component. Ultimately, it can punch out mounting holes with uniform spacing and variable number on the same specification cage, meeting the flexible production needs of multiple product models. Attached Figure Description
[0016] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort. Wherein: Figure 1 This is a schematic diagram of the overall structure of the automotive ball cage cage press of the present invention.
[0017] Figure 2 This is a schematic diagram of the internal structure of the automotive ball cage cage press of the present invention.
[0018] Figure 3 The present invention relates to an automotive ball cage cage press. Figure 2 Enlarged schematic diagram of the structure at point A in the middle.
[0019] Figure 4 The present invention relates to an automotive ball cage cage press. Figure 2 Enlarged schematic diagram of the structure at point B.
[0020] Figure 5 This is a schematic diagram of the stamping unit of the automotive ball cage cage press of the present invention.
[0021] Figure 6 This is a schematic diagram of the structure of the automotive ball cage cage press flipping component of the present invention.
[0022] Figure 7This is a schematic diagram of the guide sleeve of the automotive ball cage cage press of the present invention.
[0023] Figure 8 This is a top view of the connection position between the extension shaft and the guide sleeve of the automotive ball cage retainer press of the present invention.
[0024] Figure 9 This is a schematic diagram of the structure of the limiting part of the automobile ball cage retainer press of the present invention.
[0025] Reference numerals: 1. Base; 11. Unloading rack; 12. Guide groove; 2. Press body; 3. Stamping unit; 31. Main body; 32. Fixing frame; 33. Main shaft; 34. Top block; 35. Rocker; 36. Pressing knife; 37. Relief groove; 4. Transmission component; 41. Connecting shaft; 42. Guide sleeve; 421. Guide groove; 422. Internal gear groove; 423. Ball bearing; 43. Extension shaft; 431. One-way gear ; 432, locking block; 44, rectangular shaft; 5, adjusting component; 51, threaded shaft; 52, bracket; 53, movable gear; 6, segmented gear; 7, drive shaft one; 71, bevel gear one; 8, flipping component; 81, mounting bracket; 82, bevel gear sleeve; 83, hexagonal shaft; 84, telescopic cylinder; 85, limiting part; 86, abutment block; 87, spring; 9, drive shaft two; 91, bevel gear two; 10, retainer. Detailed Implementation
[0026] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
[0027] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and those skilled in the art can make similar extensions without departing from the spirit of the invention. Therefore, the invention is not limited to the specific embodiments disclosed below.
[0028] Reference Figures 1 to 9This invention includes an automotive ball cage retainer press, comprising a base 1, a press body 2, a stamping unit 3, and a flipping unit. The flipping unit includes a transmission component 4 disposed on one side of the stamping unit 3, an adjusting component 5 located on the side of the transmission component 4 with its end sleeved on the end of the transmission component 4, a segmented gear 6 located on one side of the end of the transmission component 4, a first transmission shaft 7 transversely disposed within the base 1 with one end of the first transmission shaft 7 meshing with the side of the segmented gear 6, a second transmission shaft 9 vertically disposed at the other end of the first transmission shaft 7, and a second transmission shaft 9 transversely disposed on the second transmission shaft 9. The flipping component 8 at the top of the press body 2 will serve as the driving source for both the stamping unit 3 and the flipping unit, so that the stamping and flipping operations of both are driven by a unified power source. The press body 2 is used as the core driving source, and the dual functions are achieved through the mechanical linkage structure: on the one hand, the stamping unit 3 is driven to complete the precise stamping and drilling of the cage 10, and on the other hand, the flipping unit is driven to perform a fixed angle flipping action, so that the cage 10 automatically rotates to the next angle after a single stamping. There is no need to configure an additional independent driving device, which effectively simplifies the equipment structure, reduces energy consumption, and saves production costs. Reference Figure 4 The segmented gear 6 has a tapered structure that is thinner at the bottom and thicker at the top. The tapered structure is divided into multiple stages from the thin end to the thick end, and the diameter of each stage is different. The transmission ratio when each stage contacts the external gear is different.
[0029] Reference Figure 5 The stamping unit 3 includes a main body 31 located on the base 1, a fixing frame 32 disposed on the side of the main body 31, a main shaft 33 inserted into the main body 31 and whose top end abuts against the press body 2, a top block 34 matched and disposed at the end of the main shaft 33, a rocker plate 35 disposed laterally between the main shaft 33 and the top block 34, a pressure knife 36 disposed at the outer end of the rocker plate 35, and a clearance groove 37 opened in the main body 31. The fixing frame 32 is used to initially limit the retainer 10. At the same time, the lower end of the fixing frame 32 is provided with a stamping block matched with the pressure knife 36. The main shaft 33 can move vertically downward under the pressure of the press body 2. The downward moving main shaft 33 squeezes the rocker plate 35 through the wedge structure at the end, so that the outer end of the rocker plate 35 is tilted upward. The tilted rocker plate 35 pushes the pressure knife 36 and the fixing frame 32 to perform a punching and pressing operation, thereby realizing the punching operation of the retainer 10.
[0030] Reference Figure 5The transmission component 4 includes a connecting shaft 41 inserted into the relief groove 37, with the top end of the connecting shaft 41 fixedly connected to the side of the main body 31, a guide sleeve 42 rotatably connected to the lower end of the connecting shaft 41, an extension shaft 43 inserted into the lower end of the guide sleeve 42, and a rectangular shaft 44 fixedly connected to the lower end of the extension shaft 43. The connecting shaft 41, through its connection with the main body 31, can follow the main body 31 in a vertical cyclic movement, and the moving connecting shaft 41 will also synchronously drive the guide sleeve 42, the extension shaft 43, and the rectangular shaft 44 to perform corresponding movements.
[0031] Reference Figure 3 and Figure 7 Multiple sets of spiral guide grooves 421 are evenly formed on the outer wall of the guide sleeve 42, and the spiral number of the guide grooves 421 is 0.5. An internal gear groove 422 is formed inside the guide sleeve 42, and the internal gear groove 422 has a relatively long depth in the vertical direction. A set of balls 423 is provided at the end of each set of guide grooves 421, and the outer end of the balls 423 is fixedly connected to the inner wall of the relief groove 37. Through the cooperation of the guide grooves 421 and the balls 423, the connecting shaft 41 can drive the guide sleeve 42 vertically. The downward movement is converted into a movement that rotates while moving downward. Since the number of spiral turns of the guide groove 421 is fixed, the rotation range of the guide sleeve 42 is 180° each time. At the same time, the inner gear groove 422 has a depth setting, so that the guide sleeve 42 always maintains the connection with the extension shaft 43 during the vertical movement. Furthermore, when the guide sleeve 42 moves downward, it rotates clockwise in the positive direction, and when the guide sleeve 42 moves upward, it moves counterclockwise in the negative direction.
[0032] Reference Figure 7 A one-way gear 431 is fixedly connected to the top of the extension shaft 43, and the one-way gear 431 is located in the inner gear groove 422. Multiple sets of locking blocks 432 are evenly distributed on the outer ring of the one-way gear 431, and the locking blocks 432 mesh with the teeth of the inner gear groove 422. The overall tilt angle of the locking blocks 432 matches the tilt angle of the inner gear groove 422. The two can form a ratchet structure by mutual cooperation. When the guide sleeve 42 rotates in the forward direction (when the guide sleeve 42 moves downward), the teeth of the inner gear groove 422 will press against the locking blocks 432, so that the locking blocks 432... When the guide sleeve 42 retracts onto the outside of the one-way gear 431, the locking block 432 cannot engage with the inner gear groove 422. Consequently, the guide sleeve 42 cannot drive the extension shaft 43 to rotate through the inner gear groove 422. However, when the guide sleeve 42 rotates in the opposite direction (when the guide sleeve 42 moves upward), the teeth of the inner gear groove 422 will abut against one end of the locking block 432, causing the inner gear groove 422 and the locking block 432 to mutually limit each other. At this time, the reverse rotation of the guide sleeve 42 will drive the extension shaft 43 to rotate as a whole.
[0033] Reference Figure 5 The adjusting component 5 includes a movable gear 53 sleeved on a rectangular shaft 44, which meshes with a segmented gear 6 for transmission. The side of the movable gear 53 is perpendicular to the hypotenuse of the segmented gear 6. Supports 52 are located on the upper and lower sides of the movable gear 53, and a threaded shaft 51 is vertically positioned at the end of the support 52. The upper end of the threaded shaft 51 is threaded to the main body 31. The movable gear 53 and the rectangular shaft 44 are fitted together, mutually limiting each other in the circumferential direction. Therefore, the rectangular shaft 44 can drive the movable gear... The wheel 53 rotates in a circle, but the two are slidably connected in the vertical direction. Therefore, the movable gear 53 can slide vertically on the rectangular shaft 44. The threaded shaft 51 can drive the bracket 52 and the movable gear 53 slidably inserted on the rectangular shaft 44 to move vertically by rotating. The movable gear 53 moving vertically will change its meshing position with the outer wall of the segmented gear 6, so that the movable gear 53 and the segmented gear 6 mesh at different stages, thereby forming different transmission ratios.
[0034] Reference Figure 6 The transmission shaft 7 has bevel gears 71 at both ends. The bevel gear 71 at the inner end of the transmission shaft 7 meshes with the segmented gear 6. The transmission shaft 9 has bevel gears 91 at both ends. The bevel gear 91 at the lower end of the transmission shaft 9 meshes with the bevel gear 71 at the outer end of the transmission shaft 7. The bevel gear 71 meshes with the lowest position of the segmented gear 6. The transmission ratio between the two is 1:1. At the same time, the transmission ratio between bevel gear 71 and bevel gear 91 is also 1:1. Therefore, when the transmission shaft 7 is driven by the segmented gear 6, the rotation amplitude will be transmitted to the transmission shaft 9 through the meshing of bevel gear 71 and bevel gear 91, so that the transmission shaft 9 will rotate with the same amplitude. Similarly, the transmission ratio between bevel gear 91 and conical sleeve 82 is also 1:1. Therefore, the transmission shaft 9 will also drive the hexagonal shaft 83 inserted in the conical sleeve 82 to change with the same amplitude through the meshing of bevel gear 91 and conical sleeve 82.
[0035] Reference Figure 6The flipping component 8 includes a mounting bracket 81 located at the top of the transmission shaft 9, a conical sleeve 82 rotatably disposed at one end of the mounting bracket 81, with the inner side of the conical sleeve 82 meshing with the bevel gear 91 at the top of the transmission shaft 9, a hexagonal shaft 83 laterally inserted into the axis of the conical sleeve 82, a telescopic cylinder 84 connected to the outer end of the hexagonal shaft 83, and a limiting part 85 disposed at the inner end of the hexagonal shaft 83. The hexagonal shaft 83 can rotate freely within the mounting bracket 81, and the hexagonal shaft 83 has an overall hexagonal prism structure, so the conical sleeve 82 and the hexagonal shaft 83 interact circumferentially. The conical sleeve 82 is limited, and its inner end meshes with the bevel gear 91. Therefore, when the conical sleeve 82 is driven by the transmission shaft 9, it can drive the hexagonal shaft 83 to rotate synchronously. The rotating hexagonal shaft 83 will then drive the limiting part 85 to rotate synchronously, thereby achieving the purpose of driving the cage 10 to rotate. The telescopic cylinder 84 is rotatably connected to the hexagonal shaft 83. At the same time, the telescopic cylinder 84 can push the hexagonal shaft 83 to move horizontally by telescopic movement, thereby assisting the cage 10 to rotate and unload.
[0036] Reference Figure 9 Multiple sets of abutment blocks 86 are evenly arranged around the outer wall of the limiting part 85, and the two sides of the abutment blocks 86 are downward inclined surfaces. A spring 87 is provided between each set of abutment blocks 86 and the limiting part 85. The multiple sets of abutment blocks 86 extend to the outside of the limiting part 85 through their respective springs 87. At the same time, the maximum diameter formed by the expansion of the multiple sets of abutment blocks 86 is greater than the inner diameter of the retainer 10. Therefore, when the abutment blocks 86 extend into the retainer 10 along with the limiting part 85, the abutment blocks 86 will firmly abut against the inner wall of the retainer 10 through the elastic support of the springs 87. This allows the retainer 10 to form a connection with the limiting part 85 through the abutment blocks 86, so that the limiting part 85 can drive the retainer 10 to rotate. This allows the angle position adjustment operation during subsequent punching operations to be realized through the flipping component 8.
[0037] During use, combined with Figures 1 to 9As shown, the retainer 10 to be punched is sleeved on the fixed frame 32. The telescopic cylinder 84 extends outward to abut the limiting part 85 at the outer end of the hexagonal shaft 83 against the inside of the retainer 10. At this time, the limiting part 85 forms a circumferential limiting connection with the retainer 10 through the abutment block 86. Then, the press body 2 pushes the main shaft 33 down. The pressing main shaft 33 pushes the pressure knife 36 at the outer end of the rocker plate 35 closer to the retainer 10. Then, with the cooperation of the pressure knife 36 and the fixed frame 32, the retainer 10 completes the initial punching operation. During the downward movement of the main shaft 33, the main shaft 33 will simultaneously drive the connecting shaft 41 to press the guide sleeve 42 to rotate downward in the forward direction. At this time, the teeth of the internal gear groove 422 inside the guide sleeve 42 press the locking block 432 to fit and retract on the outside of the one-way gear 431, so that the guide sleeve 42 cannot drive the extension shaft 43 to rotate through the cooperation of the internal gear groove 422 and the locking block 432. After the initial punching operation is completed, the main shaft 33 drives the connecting shaft 41 to move upward to reset. At this time, the guide sleeve 42 moves upward and rotates in the opposite direction. The teeth of the inner gear groove 422 will abut against one end of the locking block 432, so that the inner gear groove 422 and the locking block 432 form mutual limiting. At this time, the guide sleeve 42 will drive the extension shaft 43 to rotate as a whole. The extension shaft 43 will drive the movable gear 53 to rotate synchronously through the rectangular shaft 44. The rotating movable gear 53 will drive the segmented gear 6 to rotate synchronously. The segmented gear 6 will drive the conical sleeve 82 to rotate through the transmission shaft 1 7 and the transmission shaft 2 9. The rotating conical sleeve 82 will drive the retainer 10, which abuts against the outer end of the limiting part 85, to rotate synchronously through the hexagonal shaft 83, thereby realizing the flipping operation of the retainer 10. By repeating the above operation, the retainer 10 can be punched with multiple holes evenly. In summary, by using a single press body 2 as the core drive source, a dual function is achieved through a mechanical linkage structure: on the one hand, the stamping unit 3 is driven to complete the precise stamping and drilling of the cage 10; on the other hand, the flipping unit is driven to perform a fixed-angle flipping action, so that the cage 10 automatically rotates to the next angle after a single stamping. No additional independent drive device is required, which effectively simplifies the equipment structure, reduces energy consumption, and saves production costs. Furthermore, refer to Figure 4When different holes need to be punched into the retainer 10, the meshing position of the movable gear 53 and the segmented gear 6 can be adjusted by adjusting the adjusting component 5. The segmented gear 6 can be divided into five stages. Each stage will form a different transmission ratio when it contacts the movable gear 53. Specifically, the transmission ratios of the movable gear 53 and the segmented gear 6 in each stage are 1:1 / 4:1 / 5:1 / 6:1 / 7:1 / 8. Taking the lowest stage of contact between the movable gear 53 and the segmented gear 6 as an example, the transmission ratio between the movable gear 53 and the segmented gear 6 is 1:1 / 4. At this time, each rotation of the movable gear 53 can drive the segmented gear 6 to rotate 1 / 4 turn. That is, the segmented gear 6 can drive the retainer 10 at the outer end of the flipping component 8 to rotate 1 / 4 turn through the transmission shaft 1 7 and the transmission shaft 2 9. The stamping operation on the cage 10 will eventually stamp four sets of equally spaced holes on the outer wall of the cage 10. Therefore, by changing the meshing of the movable gear 53 and the segmented gear 6 at different stages, any number of holes in the range of 4-8 can be obtained. Regardless of the number, the holes are evenly distributed on the outer wall of the cage 10. In summary, the flipping unit has an angle adaptive adjustment function, which can accurately adjust the single flipping angle according to the number of punches required for actual production. By adjusting the meshing position of the movable gear 53 and the segmented gear 6, the transmission ratio between them is changed, thereby controlling the rotation angle of the cage 10. Finally, it is possible to stamp uniformly spaced and variable-number mounting holes on the same specification cage 10, which meets the flexible production needs of multiple product models.
[0038] Reference Figure 1 The base 1 is provided with a material unloading rack 11, and the material unloading rack 11 is located on the side of the flipping component 8. A guide groove 12 is provided between the stamping unit 3 and the flipping component 8, and the inner side of the guide groove 12 is inclined towards the side of the base 1. The inner diameter of the material unloading rack 11 is smaller than the maximum diameter of the abutment block 86 expanding outward outside the limiting part 85. Guardrails are added on both sides of the guide groove 12 to prevent the retainer 10 from falling outward.
[0039] During use, refer to Figure 9 Therefore, when the limiting part 85 drives the abutment block 86 through the unloading rack 11, the inclined side of the abutment block 86 will abut against the inner diameter of the unloading rack 11, thereby squeezing the abutment block 86 to contract towards the inner wall of the limiting part 85. At this time, the retainer 10, which was originally supported and limited by the expanded abutment block 86, will detach from the abutment block 86. During the movement driven by the limiting part 85, the side of the retainer 10 will also abut against the side of the unloading rack 11, thereby causing the retainer 10 to detach from the limiting part 85 and fall downward into the guide groove 12. Thus, it can be concluded that through the above operation, this device also realizes the automated unloading operation, further improving the flexibility of the device.
[0040] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not intended to limit it. Although the present invention has been described in detail with reference to preferred embodiments, those skilled in the art should understand that modifications or equivalent substitutions can be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all such modifications or substitutions should be covered within the scope of the claims of the present invention.
Claims
1. A press for automotive ball cage retainers, comprising a base (1), a press body (2), a stamping unit (3), and a flipping unit, characterized in that: The flipping unit includes a transmission component (4) disposed on one side of the stamping unit (3), an adjustment component (5) located on the side of the transmission component (4) with the end of the adjustment component (5) sleeved on the end of the transmission component (4), a segmented gear (6) located on one side of the end of the transmission component (4), a transmission shaft one (7) horizontally disposed in the base (1) with one end of the transmission shaft one (7) meshing with the side of the segmented gear (6), a transmission shaft two (9) vertically disposed at the other end of the transmission shaft one (7), and a flipping component (8) horizontally disposed at the top of the transmission shaft two (9). The segmented gear (6) has a tapered structure that is thinner at the bottom and thicker at the top. The tapered structure is divided into multiple stages from the thin end to the thick end, and the diameters of each stage are different.
2. The automotive ball cage cage press according to claim 1, characterized in that: The stamping unit (3) includes a main body (31) located on the base (1), a fixing frame (32) disposed on the side of the main body (31), a main shaft (33) inserted into the main body (31) and whose top end abuts against the press body (2), a top block (34) matched and disposed at the end of the main shaft (33), a rocker plate (35) disposed laterally between the main shaft (33) and the top block (34), a pressing knife (36) disposed at the outer end of the rocker plate (35), and a relief groove (37) opened in the main body (31).
3. The automotive ball cage cage press according to claim 2, characterized in that: The transmission component (4) includes a connecting shaft (41) inserted into the relief groove (37), with the top end of the connecting shaft (41) fixedly connected to the side of the main body (31), a guide sleeve (42) rotatably connected to the lower end of the connecting shaft (41), an extension shaft (43) inserted into the lower end of the guide sleeve (42), and a rectangular shaft (44) fixedly connected to the lower end of the extension shaft (43).
4. The automotive ball cage cage press according to claim 3, characterized in that: Multiple sets of spiral guide grooves (421) are evenly opened on the outer wall of the guide sleeve (42), and the spiral number of the guide groove (421) is 0.
5. An internal gear groove (422) is opened inside the guide sleeve (42), and the internal gear groove (422) has a long depth in the vertical direction. A set of balls (423) is provided at the end of each set of guide grooves (421), and the outer end of the balls (423) is fixedly connected to the inner wall of the relief groove (37).
5. The automotive ball cage cage press according to claim 4, characterized in that: The top end of the extension shaft (43) is fixedly connected to a one-way gear (431), and the one-way gear (431) is located in the inner gear groove (422). Multiple sets of locking blocks (432) are equally arranged on the outer ring of the one-way gear (431), and the locking blocks (432) mesh with the tooth grooves of the inner gear groove (422).
6. The automotive ball cage cage press according to claim 3, characterized in that: The adjusting component (5) includes a movable gear (53) sleeved on a rectangular shaft (44), and the movable gear (53) meshes with a segmented gear (6) for transmission. Meanwhile, the side of the movable gear (53) is perpendicular to the hypotenuse of the segmented gear (6). A bracket (52) is provided on the upper and lower sides of the movable gear (53), and a threaded shaft (51) is provided vertically at the end of the bracket (52). The upper end of the threaded shaft (51) is threadedly connected to the main body (31).
7. The automotive ball cage cage press according to claim 1, characterized in that: The first transmission shaft (7) is provided with bevel gears (71) at both ends. The bevel gears (71) at the inner end of the first transmission shaft (7) mesh with the segmented gear (6) for transmission. The second transmission shaft (9) is provided with bevel gears (91) at both ends. The bevel gears (91) at the lower end of the second transmission shaft (9) mesh with the bevel gears (71) at the outer end of the first transmission shaft (7).
8. The automotive ball cage cage press according to claim 1 or 7, characterized in that: The flipping component (8) includes a mounting bracket (81) located at the top of the transmission shaft (9), a conical sleeve (82) rotatably disposed at one end of the mounting bracket (81), and the inner side of the conical sleeve (82) meshing with the bevel gear (91) at the top of the transmission shaft (9), a hexagonal shaft (83) laterally inserted into the shaft of the conical sleeve (82), a telescopic cylinder (84) connected to the outer end of the hexagonal shaft (83), and a limiting part (85) disposed at the inner end of the hexagonal shaft (83).
9. The automotive ball cage cage press according to claim 8, characterized in that: Multiple sets of abutment blocks (86) are evenly arranged around the outer wall of the limiting part (85), and the two sides of the abutment block (86) are downward inclined surfaces. A spring (87) is provided between each set of abutment blocks (86) and the limiting part (85).
10. The automotive ball cage cage press according to claim 1, characterized in that: The base (1) is provided with a material unloading rack (11), and the material unloading rack (11) is located on the side of the flipping component (8). A guide groove (12) is provided between the stamping unit (3) and the flipping component (8), and the inner side of the guide groove (12) is inclined to the side of the base (1).