GB2610483A

GB2610483A - Cam direct-driven mechanical press

Info

Publication number: GB2610483A
Application number: GB2210938.3A
Authority: GB
Inventors: Hu Zhili; Hua Lin; Wang Rui
Original assignee: Wuhan University of Technology WUT
Current assignee: Wuhan University of Technology WUT
Priority date: 2021-07-27
Filing date: 2022-07-27
Publication date: 2023-03-08
Anticipated expiration: 2042-07-27
Also published as: GB202210938D0; CN113492189B; GB2610483B; CN113492189A

Abstract

A cam direct-driven mechanical press comprises a rack 40, a stamping slider 26, a cam shaft 28 driven by a power mechanism, wherein the cam shaft 28 is installed on the upper portion of the rack 40 through bearings 9, 17, 20, the stamping slider 26 is installed on the rack 40 through a sliding pair, the stamping slider 26 comprises a top support (42 figure 5) and a middle supporting plate (41 figure 5), and two main cams 22, 25 and a return cam 23 are arranged on the cam shaft 28; the top support (42 figure 5) of the stamping slider 26 is provided with an upper roller 24 making contact with the top of the return cam 23, the middle supporting plate (41 figure 5) of the stamping slider 26 is provided with lower rollers 30, 31 making contact with the bottoms of the two main cams 22, 25, and the two main cams 22, 25 and the return cam 23 form a conjugate cam together. Upper and lower working table plates 35, 36 form a stamping working table.

Description

CAM DIRECT-DRIVEN MECHANICAL PRESS TECHNICAL FIELD

[0001] The present disclosure belongs to the technical field of forging and pressing equipment, and relates to stamping equipment, in particular to cam direct-driven mechanical press.

BACKGROUND ART

[0002] The traditional press cannot realize the bottom-dead-point pressure maintaining function by adopting the crank-slider mechanism, the toggle mechanism, the screw mechanism, the multi-connecting-rod mechanism and the like which are driven by ordinary motors. Moreover, the press with a servo system can realize speed variation and speed regulation driving, and also can realize bottom-dead-point pressure maintaining. However, servo motors are in an overload state in the bottom-dead-point pressure maintaining process of the servo press, and the servo system is easy to break down because of long-time loading. Meanwhile, the slider is easy to shake in the pressure maintaining process through the accumulative errors of the transmission system, so that the forming quality of deep-drawn parts (such as 18650/21750 type battery cases) is influenced.

[0003] in order to realize bottom-dead-point precision pressure maintaining, the patent documentation CN109228446A discloses a cam driven multi-station press transmission system. The transmission system comprises a rack, a slider and a main shaft. The slider is slidably installed on the rack, and an upper roller mechanism and a lower roller mechanism are installed on the slider at intervals. The main shaft is installed on the rack, and main cams are installed on the main shaft. The main shaft is located between the upper roller mechanism and the lower roller mechanism. The main cams are respectively tangential to the upper roller mechanism and the lower roller mechanism. According to the present disclosure, the stamping process that the slider moves up and down in a reciprocating mode for pressure maintaining is realized by adopting the constant diameter cam mechanism with small system errors. The patent documentation CN2704475Y discloses an open drawing press. The constant diameter cant is adopted for driving so as to realize the similar process. However, when the motion law of the constant diameter cam within the 180-degree range of the driven member is determined, other 180-degree motion laws can be determined according to equal diameter conditions, and the defect that the motion laws of free design are restricted exist. Moreover, the equal diameter cam press mechanism cannot change the travel of the slider, and is only suitable for stamping forming of a single product, so that the process window is narrow.

SUMMARY

[0004] In order to overcome the defects in the prior art, the present disclosure aims to provide a cam direct-driven mechanical press. The transmission of the conjugate cam is adopted, free design of a 360-degree driven member motion curve call be realized, more extensive stamping process requirements can also be met, and the defect that the curve of a constant diameter can mechanism is only designed within the range of 180°. The hydraulically driven lower working table on which the positions of the lower rollers of the conjugate cam are adjustable is adopted, the defect that the travel cannot be adjustable in the prior art is overcome, and simultaneously, overload protection can also be achieved by adopting the hydraulic system. Meanwhile, driving servo motors can be changed into ordinary motors, the stalling pressure maintaining of the servo motors is replaced into mechanical high-precision pressure maintaining for normal rotation of the ordinary motors, and the specific forming technology needing bottom-dead-point precise pressure maintaining, especially the hot stamping pressure maintaining technology, is met, and in the hot stamping pressure maintaining technology, the plate is needed to make tight contact with the mold all the time and quenching is competed. The mechanical press is driven by multiple motors, and is high in driving power. The conjugate cam mechanism is simple in transmission chain, small in accumulative error, compact in structure, high in rigidity and strength, high in bearing capacity and high in reliability.

[0005] To achieve the purpose, the present disclosure adopts the following technical scheme.

[0006] A cam direct-driven mechanical press comprises a rack, a stamping slider, a cam shaft and a power mechanism, wherein the cam shaft is installed on the upper portion of the rack through bearings, the stamping slider is installed on the rack through a sliding pair in the vertical direction, the stamping slider is a hollowed-out slider and at least comprises a top support and a middle supporting plate, two main cams and a return cam are arranged on the cam shaft, the two main cams are symmetrically distributed by taking the return cam as the center, and the phase positions of the two main cams are the same; the top support of the stamping slider is provided with an upper roller making contact with the top of the return cam, the middle supporting plate of the stamping slider is provided with lower rollers making contact with the bottoms of the two main cams, and the two main cams and the return cam form a conjugate cam together; an upper working table plate is arranged at the bottom of the stamping slider, a lower working table plate is arranged at the position, below the upper working table plate, of the bottom of the rack, and the upper working table plate and the lower working table plate form a stamping working table together; and the power mechanism is used for driving the Ca M shaft to rotate, and the rotation of the cam shaft drives the stamping slider and the upper working table plate on the stamping slider to move up and down through the conjugate cam so as to complete the stamping action.

[0007] Futher, the power mechanism comprises four motors and a reducer casing, the reducer casing is fixedly installed on the rack, the four motors are circumferentially distributed on the reducer casing, the cam shaft extends into the reducer casing, a large gear is arranged on the cam shaft at the end, four pinions meshed with the large gear are arranged around the large gear in the reducer casing, and the output shaft of each motor is connected with one pinion through power transmission after extending into the reducer casing.

[0008] Further, the stamping slider and the sliding pair on the rack are free of clearance fit by using cylindrical rollers.

[0009] Further, the cam shaft is installed on the rack through four bearings, the main cams and the return cam are installed on the cam shaft between the two bearings in the middle, and the four bearings are symmetrically distributed by taking the return cam as the center.

[0010] Further, an anti-swing slider is respectively installed between every two adjacent bearings on the two sides through bearings along the axial direction of the cam shaft, and the anti-swing slider is in sliding-fit connection with the stamping slider.

[0011] Further, the bearings, the main cams and the return cam on the cam shaft are directly provided with sleeves used for axial positioning.

[0012] Further, the lower rollers are installed on the middle supporting plate through a roller support, specifically, a plurality of different heights of hinge pin holes are formed in the middle supporting plate, the lower rollers are installed on the roller support, the roller support is installed in hinge pin holes through hinge pins, the roller support is installed by selecting the different heights of hinge pin holes, and the heights of the lower rollers are adjusted, so that the travel of the stamping slider is adjusted.

[0013] Further, balance cylinders connected with the stamping slider are respectively arranged on the rack on the two sides of the cam shaft.

[0014] Further, the lower working table plate is installed at the bottom of the rack through a plurality of hydraulic cylinders, and the height of the lower working table plate can be adjusted through the hydraulic cylinders, so that the relative travel of the stamping slider is adjusted.

[0015] Further, bottom-dead-point long-time precise pressure maintaining of the stamping slider is realized by designing the contour line of the conjugate cam, and the motion equation of the conjugate cam is as follows: [0016] (6/60-s n (27ra/60/(2701 (0:8:81) [0017] sii=h-hk6/60-sin(27t6/61)/(27c)] (ir.±6x+61) [0018] s2=h (31<6<81+82) [0019] s22=00c+61<o<z+61+62) [0020] s3=h11-(8/83)+sin(2x8/83)/(27)] (81+82<6<61+82+83) [0021] s33=li-hil -(6/63)-fsin (2765/63)/(270 (ir-f6i-162<69E+61+63+63) [0022] in the formula, h is the travel of the stamping slider, the phase difference of the main cam arid the return cam is 1 80°, 6 is the motion rotation angle of the main cam, Si is the rise travel motion curve of the main cam, sn is the rise travel motion curve of the return cam, di is the total rotation angle during rise travel motion of the main cam, s, is the outer dwell motion curve of the main cam, S22 is the outer dwell motion curve of the return cam, 63 is the total rotation angle during pressure maintaining of the main cam, s3 is the return motion curve of the main cam, 533 is the return motion curve of the return cam, and 83 is the total rotation angle during return motion of the main cam; and [0023] the pressure maintaining time is as follows: [0024] [0025] wherein, T1 is the pressure maintaining time during down stamping of the stamping slider, and To is the motion stamping period of the stamping slider.

[0026] The mechanical press has the beneficial effects that driving servo motors can be changed into ordinary motors, the stalling pressure maintaining of the servo motors is replaced into mechanical high-precision pressure maintaining for normal rotation of the ordinary motors, and the specific forming technology needing bottom-dead-point precise pressure maintaining, especially the hot stamping pressure maintaining technology, is met, and in die hot stamping pressure maintaining technology, the plate is needed to make close contact with the mold all the time and quenching is competed. Meanwhile, the transmission of the conjugate cam is adopted, free design of a 360-degree driven member motion curve can be realized, more extensive stamping process requirements can also be met, and the defect that the curve of a constant diameter can mechanism is only designed within the range of 180°. The hydraulically driven lower working table on which the positions of the lower rollers of the conjugate cam arc adjustable is adopted, the defect that the travel of the constant diameter can mechanism cannot be adjustable is overcome, and simultaneously, overload protection can also be achieved by adopting the hydraulic system. The kinematics curve design of different types of stamping sliders and the bottom-dead-point long-time precise pressure maintaining of the slider are realized by designing the contour line of die conjugate cam The mechanical press is driven by multiple motors, and is high in driving power. The conjugate cam mechanism is simple in transmission chain, small in accumulative error, compact in structure, high in rigidity and strength, high in bearing capacity and high in reliability.

BRIEF DESCRIPTION OF THE DRAWINGS

[0027] FIG. 1 is a three-dimensional structural schematic diagram of a front complete machine of a mechanical press in the first embodiment of the present disclosure; [0028] FIG. 2 is a three-dimensional structural schematic diagram of a rear complete machine of a mechanical press in the first embodiment of the present disclosure; [0029] FIG. 3 is a two-dimensional assembly diagram of a transmission mechanism in the first embodiment of the present disclosure; [0030] FIG. 4 is a schematic diagram of the arrangement form of four hydraulic cylinders in the first embodiment of the present disclosure; [0031] FIG. 5 is a schematic diagram of a stamping slider in the first embodiment of the present disclosure; [0032] FIG. 6 is a contour line diagram of a conjugate cam of rollers under a certain rise travel in the second embodiment of the present disclosure; [0033] FIG. 7 is a contour line diagram of a conjugate cam under various rise travels in the second embodiment of the present disclosure; [0034] FIG. 8 is a three-dimensional model of a conjugate cam and rollers in the third embodiment of the present disclosure; and [0035] FIG. 9 is a process curve of a stamping slider in the third embodiment of the present disclosure.

[0036] Reference signs: 1, servo motor; 2, pinion; 3, angular contact ball bearing; 4, angular contact ball bearing; 5, large gear; 6, flat key; 7, shaft end check ring; 8, screw; 9, first bearing; 10, first sleeve; 11, left box; 12, flat socket head cap screw; 13, cross beam; 14, right box; 15, reducer casing check ring; 16, second sleeve; 17, second bearing; 18, anti-swing slider; 19, third sleeve; 20, third bearing; 21, fourth sleeve; 22, first main cam; 23, return cam; 24, upper roller; 25, second main cam; 26, stamping slider; 27, left end cover; 28, main cam shaft; 29, flat key; 30, first lower roller; 3L second lower roller; 32, hinge pin; 33, roller support; 34, hinge pin hole; 35, upper working table plate; 36, lower working table plate; 37, screw; 38, hydraulic cylinder; 39, oil channel; 40, rack; 41, middle supporting plate; 42, top support; and 43, balance cylinder.

DETAILED DESCRIPTION OF THE EMBODIMENTS

[0037] The description of specific embodiments in the present disclosure is further described in conjunction with the following attached figures and embodiments. The following embodiments are used for illustrating the present disclosure, but are not used for restricting the scope of the present disclosure.

[0038] The following describes the embodiments of technical schemes of the present disclosure in detail with reference to the attached figures. The following embodiment serves only to more clearly illustrate the technical solutions of the present disclosure, and therefore, as an example only and cannot limit the scope of protection of the present disclosure in this way.

[0039] In the first embodiment, as shown in FIG. 1 to FIG. 5, a cam direct-driven mechanical press comprises a rack 40, a stamping slider 26, a cam shaft 28 and a power mechanism, wherein the cam shaft 28 is installed on the upper portion of the rack 40 through bearings, the stamping slider 26 is installed on the rack 40 through a sliding pair in the vertical direction, the stamping slider 26 is a hollowed-out slider and comprises a top support 42 and a middle supporting plate 41, two main cams and a return cam 23 are arranged on the cam shaft 28, the two main cams are symmetrically distributed by taking the return cam 23 as the center, and the phase positions of the two main cams are the same; the top support 42 of the stamping slider 26 is provided with an upper roller 24 making contact with the top of the return cam 23, the middle supporting plate 41 of the stamping slider is provided with lower rollers making contact with the bottoms of the two main cams, and the two main cams and the return cam form a conjugate cam together; an upper working table plate 35 is arranged at the bottom of the stamping slider 26, a lower working table plate 36 is arranged at the position, below the upper working table plate 35, of the bottom of the rack, and the upper working table plate and the lower working table plate form a stamping working table together, and the power mechanism is used for driving the cam shaft to rotate, and the rotation of the cam shaft 28 drives the stamping slider 26 and the upper working table plate 35 on the stamping slider 26 to move up and down through die conjugate cam so as to complete the stamping action.

[0040] The power mechanism comprises four motors which are driven in parallel and the same in power. The output shafts of the four motors are respectively connected with the pinions inside the reducer casing. The four pinions jointly drive the large gear, and the large gear drives the cam shaft to rotate.

[0041] The four servo motors are circumferentially distributed on the right box 14 in a 90-degree mode. The right end face of the left box 11 is matched with the left end face of the right box 14. The left box 11 and the right box 14 are precisely connected through six flat socket head cap screws 12 uniformly distributed in the circumferential direction. The output shafts of the four servo motors are respectively connected with the four pinions 2 inside a speed changing box composed of the left box 11 and the right box 14 through splines. The four pinions 2 are uniformly distributed in the speed changing box composed of the left box 11 and the right box 14. The two end axles of the four pinions 2 are respectively matched with four pairs of angular contact ball bearings 3, 4 inside the left box 11 and the right box 14. The left end of the left box 11 is fixedly connected with the cross beam 13. The right end of the right box 14 is matched with a reducer casing check ring 15. The reducer casing check ring 15 is fixed on the cross beam 13 through screws. The cross beam 13 is welded to the rack 40. The four pinions 2 inside the speed changing box jointly drive the large gear 5 to rotate. The large gear 5 transmits the torque to the main cam shaft 28 through flat keys 6. The left end of the large gear 5 is matched with the right end of the first sleeve 10. The right end of the large gear 5 is pressed by a shaft end check ring 7. The shaft end check ring 7 is fixed at the right end of the main cam shaft 28 through screws 8. The left end of the first sleeve 10 abuts against the first bearing 9.

[0042] As shown in FIG. 3, along the axial direction of the main cam shaft 28, from right to left, the main cam shaft 28 is of a bilateral symmetry structure. A right end cover 43, first bearings 9, second sleeves 16, second bearings 17, third sleeves 19, third bearings 20, a first main cam 22, a return cam 23, a second main cam 25, fourth sleeves 21, third bearings 20, third sleeves 19, second bearings 17, second sleeves 16, first bearings 9 and a left end cover 27 are sequentially installed on the main cam shaft 28 from right to left. Specifically, the main cam shaft 28 is firstly installed on the rack 40 through the two first bearings 9 and the two third bearings 20. The two first bearings 9 are located at the positions of the two ends. The two third bearings 20 are located at the position between the two first bearings 9. The second main cam 25 and the first main cam 22 are installed between the two third bearings 20.

[0043] On the right side, the first bearing 9 and the second bearing 17 are limited through the second sleeve 16, the second bearing 17 and the third bearing 20 are limited through the third sleeve 19, and the third bearing 20 and the first main cam 22 are limited through the fourth sleeve 21. [0044] On the left side, the second main cam 25 and the third bearing 20 on the left side are limited through the fourth sleeve 21, the third bearing 20 and the third bearing 17 are limited through the third sleeve 19, and the third bearing 17 and the first bearing 9 on the left side are limited through the second sleeve 16.

[0045] As shown in FIG. 3, the second main cam 25 and the first main cam 22 are of same contours and phase positions and are symmetrically arranged about a center line E-E. The second main cam 25 and the first main cam 22 are connected through a flat key 29 and the main cam shaft 28. The return cam 23 is also connected with the main cam shaft 28 through the flat key 29. The second main cam 25 and the first main cam 22 are distributed on the two sides of the return cam 23. The left end face of the second main cam 25 and the right end face of the first main cam 22 limit the left-and-right motion of the main cams and the return cam through the fourth sleeves 21, the third bearings 20 fixed on the rack 40, the third sleeves 19, the second bearings 17, the second sleeves 16, the first bearings 9, the left end cover 27, and the right end cover 43 which are symmetrically distributed. The second main cam 25 and the first main cam 22 respectively make close contact with the first lower roller 30 and the second roller 31 which are symmetrically distributed about E-E. The return cam 23 makes close contact with the upper roller 24. The first lower roller 30 and the second lower roller 31 are installed on the roller support 33. The roller support 33 is fixed to the middle supporting plate 41 of the stamping slider 26 through hinge pins 32. The upper roller 24 is installed on the top support 42 above the stamping slider 26. A plurality of different heights of hinge pin holes 34 are formed in the middle supporting plate 41. The roller support 33 is installed by selecting the different heights of hinge pin holes 34. The heights of the lower rollers can be adjusted, and different sizes of conjugate cams are replaced simultaneously, so that the travel of the stamping slider 26 is changed. The second bearing 17 is installed inside the anti-swing slider 18. The anti-swing sliders 18 are symmetrically arranged along the center line E-E. The symmetrically arranged anti-swing sliders 18 are in planar sliding fit with the interiors of the left and right sides of the stamping slider 26 to ensure that the base circles of the upper roller, the lower roller, the main cam and the return cam and the cam shaft 28 are located on the same center line.

[0046] The upper working table plate 35 is installed at the bottom of the stamping slider 26. The upper working table plate 35 is parallel to the lower working table plate 36. The lower working table plate 36 is fixed to four hydraulic cylinders 38. The four hydraulic cylinders 38 are fixed with the lower working table plate 36 through screws 37 and matched holes. Hydraulic oil drives the hydraulic cylinders 38 to move through oil channels 39. The hydraulic cylinders 38 drive the lower working table plate 36 to move, so that the travel of the slider 35 is relatively adjustable. Meanwhile, the effect of overload protection is achieved.

[0047] Long-time pressure maintaining of the stamping slider 26 at the bottom dead point can be achieved. The pressure maintaining function is realized by designing the contour line of the conjugate cam, and the low of cycloid motion is taken as an example.

[0048] The motion equations of the main and return cams are as follows: [0049] s, =hi (6/61)-sin(2m6/61)/(2701 (0<6<6, ) [0050] s 1=h-11 [03/60-sin(2n6/61)/(270] (nOS7E-F a 0 [0051] S241 (6161+62) [0052] 522=0 (7r+3,<6<z+6,+8,) [0053] s3=b[1-(6/63)-Esin(27c6/63)/(241 (61+62<6<61+62+63) [0054] s33=h-h[1-(6/63)+sin(27c6/63)/(270] (7t+61+62<6<m+61+62+63) [0055] In the formula, 61+63+63-27t, the phase difference of the main cam and the return cam is 180°, 6 is the transmission angle of the main cam, h is the travel of the stamping slider, st is the rise travel motion curve of the main cam, sii is the rise travel motion curve of the return cam, 61 is the total rotation angle during rise travel motion of the main cam, s3 is the outer dwell (slider pressure maintaining) motion curve of the main cam, 532 is the outer dwell (slider pressure maintaining) motion curve of the return cam, 62 is the total rotation angle during pressure maintaining of the main cam, s3 is the return motion curve of the main cam, s33 is the return motion curve of the return cam, and 63 is the total rotation angle during return motion of the main cam.

[0056] The pressure maintaining time is as follows: [0057] [0058] wherein, T1 is the pressure maintaining time during down stamping of the stamping slider, and To is the motion stamping period of the stamping slider [0059] The mechanical press has the beneficial effects that the servo motors of the power mechanism can be changed into ordinary motors, the stalling pressure maintaining of the servo motors is replaced into mechanical high-precision pressure maintaining for normal rotation of the ordinary motors, and the specific forming technology needing bottom-dead-point precise pressure maintaining, especially the hot stamping pressure maintaining technology, is met, and in the hot stamping pressure maintaining technology, the plate is needed to make close contact with the mold all the time and quenching is competed.

[0060] The stamping slider and the sliding pair on the rack are free of clearance fit by using cylindrical rollers. Specifically, the cylindrical rollers are arranged on the stamping slider, guide rails are arranged on the rack (unshown in the figures), and the rollers are in interference fit with the guide rails, so that unbalance loading is restricted, and the motion accuracy of the sliding pair is improved.

[0061] Balance cylinders 43 connected with the stamping slider are respectively arranged on the rack on the two sides of the cam shaft. The weight of the stamping slider is very large during resting, so that the transmission systems such as the cams and the motors of the driving system bear the load, and the balance cylinders 43 play a role in balancing the weight. When the stamping slider moves upwards, in order to reduce the speed, the impact is reduced for speed reduction balance. Accidents such as connecting rod bolt looseness are avoided, mid the stamping slider without support force is balanced, so that the effect of buffering and protecting workers is achieved.

[0062] In the second embodiment, as shown in FIG. 6, the contour lines and relative positions of the direct acting conjugate cam and the rollers arc obtained under the conditions that the base circle radius of the cam is 40 mm, the travel of the cam is 100 mm (namely die stamping slider), the roller radius is 10 mm and the roller eccentric amount is 0. As shown in FIG. 6, the contour line of the conjugate cam is obtained when the base circle radius of the cam is 40 mm, the eccentric amount is 0 and the roller radius is 10 mm in other different travels.

[0063] In the third embodiment, as shown in FIG. 8, the three-dimensional diagram of the conjugate cam and the roller is obtained. The base circle radiuses of the main cams and the return cam are 40 mm, the displacement of the push rod is 30 mm, the roller radius is 10 mm, the down travel of the slider is 120° (in 1/3 period), the pressure maintaining is 170° (in about 1/2 period), and the return trip is 70° cm about 1/6 period). Under the above conditions, the contrast between the kinematics curve of the slider under different motion laws and the displacement curve of a traditional crank connecting rod press incapable of realizing pressure maintaining is obtained through the design. Namely, in the embodiment, the pressure maintaining time is as follows: 1 70 0,4727:, [0064] [0065] In the pressure maintaining time, the displacement of the slider is 0, and the stamping process needing bottom-dead-point pressure maintaining is met.

[0066] The above-mentioned embodiments are only used for illustrating the present disclosure but not restricting the present disclosure. Although the present disclosure is described in detail by reference to embodiments, those ordinary skilled in the art should understand that the technical scheme of the present disclosure can be amended or equally substituted but not departing from the substance and scope of the technical scheme of the present disclosure, which are all contained in the scope of protection of the present disclosure.

Claims

CLAIMS1. A cam direct-driven mechanical press, comprising a rack, a stamping slider, a cam shaft and a power mechanism, wherein the cam shaft is installed on the upper portion of the rack through bearings, the stamping slider is installed on the rack through a sliding pair in the vertical direction, the stamping slider is a hollowed-out slider and at least comprises a top support and a middle supporting plate, two main cams and a return cam are arranged on the cam shaft, the two main cams are symmetrically distributed by taking the return cam as the center, and the phase positions of the two main cams are the same; the top support of the stamping slider is provided with an upper roller making contact with the top of the return cam, the middle supporting plate of the stamping slider is provided with lower rollers making contact with the bottoms of the two main cams, and the two main cams and the return cam form a conjugate cam together; an upper working table plate is arranged at the bottom of the stamping slider, a lower working table plate is arranged at the position, below the upper working table plate, of the bottom of the rack, and the upper working table plate and the lower working table plate form a stamping working table together; arid the power mechanism is used for driving the cam shaft to rotate, and the rotation of the cam shaft drives the stamping slider and the upper working table plate on the stamping slider to move up and down through the conjugate cam so as to complete the stamping action.
2. The mechanical press according to claim 1, wherein the power mechanism comprises four motors and a reducer casing, the reducer casing is fixedly installed on the rack, the four motors are circumferentially distributed on the reducer casing, the cam shaft extends into the reducer casing, a large gear is arranged on the cam shaft at the end, four pinions meshed with the large gear are arranged around the large gear in the reducer casing, and the output shaft of each motor is connected with one pinion through power transmission after extending into the reducer casing.
3. The mechanical press according to claim 2, wherein the stamping slider and the sliding pair on the rack are free of clearance fit by using cylindrical rollers.
4. The mechanical press according to claim 2, wherein the cam shaft is installed on the rack through four bearings, the main cams and the return cam are installed on the cam shaft between the two bearings in the middle, and the four bearings are symmetrically distributed by taking the return cam as the center.
5. The mechanical press according to claim 4, wherein an anti-swing slider is respectively installed between every two adjacent bearings on the two sides through bearings along the axial direction of the cam shaft, and the anti-swing slider is in sliding-fit connection with the stamping slider.
6. The mechanical press according to claim 4, wherein the bearings, the main cams and the return cam on the cam shaft are directly provided with sleeves used for axial positioning.
7. The mechanical press according to claim 2, wherein the lower rollers are installed on the middle supporting plate through a roller support, specifically, a plurality of different heights of hinge pin holes are formed in the middle supporting plate, the lower rollers are installed on the roller support, the roller support is installed in hinge pin holes through hinge pins, the roller support is installed by selecting the different heights of hinge pin holes, and the heights of the lower rollers are adjusted, so that the travel of the stamping slider is adjusted.
8. The mechanical press according to claim 2, wherein balance cylinders connected with the stamping slider are respectively arranged on the rack on the two sides of the cam shaft.
9. The mechanical press according to claim 2, wherein the lower working table plate is installed at the bottom of the rack through a plurality of hydraulic cylinders, and the height of the lower working table plate can be adjusted through the hydraulic cylinders, so that the relative travel of the stamping slider is adjusted.
10. The mechanical press according to claim 2, wherein bottom-dead-point long-time precise pressure maintaining of the stamping slider is realized by designing the contour line of the conjugate cam, and the motion equation of the conjugate cam is as follows: s3=131 (6160-si n (2z8/60/(2z) (0<8<81) s 8=h-h1(67.31)-sin(2783/61)/(2701(6SR+81) s2=h(6r<O<61+82) s22=0(7c+63<6<7d61+62) s3=h[1-(6763)+sin(2785/63)/(2701(81+62<6<81+82+83) s:33=h-h[1-(8/83)+sin(27113/83)/(2701(z+81+62<d<R+8, +62+6,) in the formula, h is the travel of the stamping slider, the phase difference of the main cam and the return cam is 180°, 8 is the motion rotation angle of the main cam, Si is the rise travel motion curve of the main cam, su is the rise travel motion curve or the return cam, di is the total rotation angle during rise travel motion of the main cam, s, is the outer dwell motion curve of the main cam, S22 is the outer dwell motion curve of the return cam, 6:3 is the total rotation angle during pressure maintaining of the main cam, 53 is the return motion curve of the main cam, s33 is the return motion curve of the return cam, and 83 is the total rotation angle during return motion of the main cam; and the pressure maintaining time is as follows: wherein. T1 is the pressure maintaining time during down stamping or the stamping slider, and To is the motion stamping period of the stamping slider.