CN103419387B - High-speed precise numerical control press mechanism with driving and driven combination drive - Google Patents
High-speed precise numerical control press mechanism with driving and driven combination drive Download PDFInfo
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- CN103419387B CN103419387B CN201310375595.4A CN201310375595A CN103419387B CN 103419387 B CN103419387 B CN 103419387B CN 201310375595 A CN201310375595 A CN 201310375595A CN 103419387 B CN103419387 B CN 103419387B
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Abstract
The invention provides a high-speed precise numerical control press mechanism with driving and driven combination drive. A crankshaft is simple in design structure and easy to process, force bearing points are few, heating sources are reduced, and the running speed of the high-speed precise numerical control press mechanism is improved. The mechanism comprises the crankshaft, a main sliding block and two auxiliary sliding blocks, wherein the crankshaft is connected with the main sliding block through a connecting rod; two groups of lever motions are separately arranged to connect the auxiliary sliding blocks with the main sliding block; the auxiliary sliding blocks are not directly connected with the crankshaft.
Description
Technical field
The invention belongs to mechanical pressure manufacture field, be specifically related to a kind of high speed accurate numerical control press mechanism.
Background technology
Sheet Metal Forming Technology a kind of apply external force to sheet material, band etc. and be equipped with ancillary technique again and make it to produce plastic deformation or separation, thus obtain and reach the part shape of technical requirement, the processing technology of size.Compared with other technique, punch machining process has that cost is low, easy to operate, quality is good, precision is high, efficiency advantages of higher.High velocity ram machine is as a kind of efficient, high-accuracy and punch machining equipment for automotive that automaticity is high, and drawing velocity is per minute up to even thousands of times of hundreds of, and therefore its production efficiency exceeds tens times of even hundreds of times compared to common punch press.
At present, the theory structure great majority of high speed accurate numerical control press mechanism are all crank block structure (the Zhao Sheng tons of the directly secondary slide block of configuration balance in the reverse direction, open and learn, Gao Changyu, Liu Wei, Zhang Yong. high-speed blanking press inertial force balancing device and characteristic research (two) thereof, " equipment " 2005,5:14-20).The shortcoming of this structure is: bent axle is by connecting rod and slave connecting rod difference Direct driver master slider and secondary slide block simultaneously, and connect the crank throw of master slider and the crank throw phase 180 degree of auxiliary connection slide block, cause crankshaft structure complicated, processing technology is also very complicated; Bent axle drives the revolute at the crank throw place of master slider and secondary slide block be all circumferential rotation type, under the state of running up, become main pyrotoxin, caloric value is larger; The load such as inertia force, stamping press, driving force of master slider and secondary slide block is all finally born by bent axle, and bent axle stress point is many and complicated, very high to the requirement of the mechanical characteristic of bent axle.
Summary of the invention
The present invention proposes the high speed accurate numerical control press mechanism that a kind of active-passive composite drives, and its crankshaft designs structure is simple, be easy to processing, stress point is few, decrease pyrotoxin, improves the speed of service of high speed accurate numerical control press mechanism.
In order to solve the problems of the technologies described above, the invention provides the high speed accurate numerical control press mechanism that a kind of active-passive composite drives, comprising bent axle, master slider, the first secondary slide block, the second secondary slide block, it is characterized in that:
Described bent axle is that the hyperbolic with same-phase crank throw turns bent axle;
Described punch body also comprises first connecting rod, second connecting rod, eccentric massblock, third connecting rod, the first lever, double leval jib, the 5th connecting rod, the second lever, six-bar linkage;
Bent axle to be arranged on punch press body with horizontal level left and right directions and can to rotate relative to fuselage, and eccentric massblock is fixedly mounted on bent axle to become the direction of 180 degree relative to crank throw, and master slider to be arranged vertically on fuselage and to be positioned at immediately below bent axle;
First connecting rod is connected with revolute pair with the crank throw of two on bent axle respectively with one end of second connecting rod, and first connecting rod is connected with kinematic pair with master slider respectively with the other end of second connecting rod;
First secondary slide block and the second secondary slide block to be arranged vertically on punch press body and to be positioned at the top of both sides, crank up center;
The central pivot point of the first lever is connected with punch press body respectively by revolute pair with the central pivot point of the second lever, master slider is connected by third connecting rod one end with the first lever, first secondary slide block is connected with the other end of the first lever by double leval jib, master slider, third connecting rod, first lever, double leval jib is all connected by revolute pair between any two with the first secondary slide block, form first group of leverage, master slider is connected with one end of the second lever by the 5th connecting rod, second secondary slide block is connected with the other end of the second lever by six-bar linkage, master slider, 5th connecting rod, second lever, six-bar linkage is all connected by revolute pair between any two with the second secondary slide block, form second group of leverage,
First group of leverage is parallel to each other for each revolute pair axis be connected with in second group of leverage.
The present invention compared with prior art, its remarkable advantage is to be connected with master slider by secondary slide block by arranging separately two groups of leverages, secondary slide block is not directly connected with bent axle, such bent axle only need have unidirectional crank throw, simplify the structure of bent axle, and further reduce the difficult processing of bent axle, decrease stressed from secondary slide block of bent axle simultaneously.Revolute pair in two groups of leverages of the secondary slide block movement of driving of independent setting all without the need to doing complete cycle motion, thus decreases pyrotoxin.Bent axle stress point reduces, and pyrotoxin reduces, and is conducive to the raising of high speed accurate numerical control press dynamic accuracy.
Accompanying drawing explanation
Fig. 1 is the high speed accurate numerical control press mechanism structure schematic diagram that active-passive composite of the present invention drives, and wherein, Fig. 1 (a) is this structural front view, and Fig. 1 (b) is this structure side view.
Fig. 2 is the another kind of structural representation of high speed accurate numerical control press mechanism that active-passive composite of the present invention drives.
Detailed description of the invention
If Fig. 1 (a) is the high speed accurate numerical control press mechanism structure schematic diagram that active-passive composite of the present invention drives.The high speed accurate numerical control press mechanism that active-passive composite drives, comprises bent axle 1, the secondary slide block 72 of master slider the 3, first secondary slide block 71, second, first connecting rod 21, second connecting rod 22, eccentric massblock 8, third connecting rod 41, first lever 51, double leval jib 61, the 5th connecting rod 42, second lever 52, six-bar linkage 62, bent axle 1 to be arranged on punch press body with horizontal level left and right directions and can to rotate relative to fuselage, and eccentric massblock 8 is fixedly mounted on bent axle 1 to become the direction of 180 degree relative to crank throw, and master slider 3 to be arranged vertically on fuselage and to be positioned at immediately below bent axle 1, first connecting rod 21 is connected with revolute pair with the crank throw of two on bent axle 1 respectively with one end of second connecting rod 22, and first connecting rod 21 is connected with kinematic pair with master slider 3 respectively with the other end of second connecting rod 22, first secondary slide block 71 and the second secondary slide block 72 to be arranged vertically on punch press body and to be positioned at the top of bent axle 1 centre of gyration both sides, the central pivot point 91 of the first lever 51 is connected with punch press body respectively by revolute pair with the central pivot point 92 of the second lever 52, master slider 3 is connected with one end of the first lever 51 by third connecting rod 41, first secondary slide block 71 is connected with the other end of the first lever 51 by double leval jib 61, master slider 3, third connecting rod 41, first lever 51, double leval jib 61 is all connected by revolute pair between any two with the first secondary slide block 71, form first group of leverage, master slider 3 is connected with one end of the second lever 52 by the 5th connecting rod 42, second secondary slide block 72 is connected with the other end of the second lever 52 by six-bar linkage 62, master slider 3, 5th connecting rod 42, second lever 52, six-bar linkage 62 is all connected by revolute pair between any two with the second secondary slide block 72, form second group of leverage, first group of leverage is parallel to each other for each revolute pair axis be connected with in second group of leverage.
First group of leverage and second group of leverage are distributed in the both sides of bent axle 1, Fig. 1 (a) Suo Shi in front view, third connecting rod 41 and the 5th connecting rod 42, first lever 51 and the second lever 52, double leval jib 61 and six-bar linkage 62, first secondary slide block 71 and the second secondary slide block 72 overlap.Bent axle 1 is connected with master slider 3 with second connecting rod 22 by first connecting rod 21, surveys in view shown in Fig. 1 b, and first connecting rod 21 and second connecting rod 22 overlap.
Further, described first group of leverage and each revolute pair axis for being connected in second group of leverage, be parallel to the pivot center of bent axle 1, or horizontally disposed and perpendicular to the pivot center of bent axle 1.
Further, described connection first connecting rod 21, second connecting rod 22 and the kinematic pair of master slider 3, be specifically as follows revolute pair or ball pivot.
Further, as shown in Figure 2, described first group of leverage and second group of leverage are arranged symmetrically in the both sides of bent axle 1, or antisymmetry is arranged in the both sides of bent axle 1.
During work, bent axle 1 drives master slider 3 to pump by first connecting rod 21 and second connecting rod 22 jointly, and pumping of master slider 3 just directly can complete Punching Process.When master slider 3 moves downward, drive the first lever 51 and the second lever 5 to rotate respectively by third connecting rod 41 and the 5th connecting rod 42, the double leval jib 61 and the six-bar linkage 62 that are connected to the first lever 51 and second lever 52 other end drive the first secondary slide block 71 and the second secondary slide block 72 to move upward again respectively.When master slider 3 moves upward, drive the first lever 51 and the second lever 52 to rotate respectively by third connecting rod 41 and the 5th connecting rod 42, the double leval jib 61 and the six-bar linkage 62 that are connected to the first lever 51 and second lever 52 other end drive the first secondary slide block 71 and the second secondary slide block 72 to move downward again respectively.The direction of motion of the first secondary slide block 71 and the second secondary slide block 72 is contrary with the direction of motion of master slider 3, can balance the inertia force of master slider 3.The eccentric inertia force of crank throw 1 is balanced by the eccentric massblock 8 be arranged on bent axle 1.Equilibrium problem is solved well by above-mentioned two kinds of balance modes.Bent axle 1 without the need to the secondary slide block of Direct driver first 71 and the second secondary slide block 72, thus decreases bent axle 1 from connecing the stressed of the first secondary slide block 71 and the second secondary slide block 72.Drive the revolute pair in two of secondary slide block movement groups of leverages all without the need to doing complete cycle motion simultaneously, thus decrease pyrotoxin.
Claims (7)
1. a high speed accurate numerical control press mechanism for active-passive composite driving, comprises bent axle (1), master slider (3), the first secondary slide block (71), the second secondary slide block (72), it is characterized in that:
Described bent axle 1 is that the hyperbolic with same-phase crank throw turns bent axle;
Described punch body also comprises first connecting rod (21), second connecting rod (22), eccentric massblock (8), third connecting rod (41), the first lever (51), double leval jib (61), the 5th connecting rod (42), the second lever (52), six-bar linkage (62);
Bent axle (1) to be arranged on punch press body with horizontal level left and right directions and can to rotate relative to fuselage, eccentric massblock (8) is fixedly mounted on bent axle (1) to become the direction of 180 degree relative to crank throw, and master slider (3) to be arranged vertically on fuselage and to be positioned at immediately below bent axle (1);
First connecting rod (21) is connected with revolute pair with two crank throws on bent axle (1) respectively with one end of second connecting rod (22), and first connecting rod (21) is connected with kinematic pair with master slider (3) respectively with the other end of second connecting rod (22);
First secondary slide block (71) and the second secondary slide block (72) to be arranged vertically on punch press body and to be positioned at the top of bent axle (1) centre of gyration both sides;
The central pivot point (91) of the first lever (51) is connected with punch press body respectively by revolute pair with the central pivot point (92) of the second lever (52), master slider (3) is connected by third connecting rod (41) one end with the first lever (51), first secondary slide block (71) is connected by the other end of double leval jib (61) with the first lever (51), master slider (3), third connecting rod (41), first lever (51), double leval jib (61) is all connected by revolute pair between any two with the first secondary slide block (71), form first group of leverage, master slider (3) is connected with one end of the second lever (52) by the 5th connecting rod (42), second secondary slide block (72) is connected by the other end of six-bar linkage (62) with the second lever (52), master slider (3), 5th connecting rod (42), second lever (52), six-bar linkage (62) is all connected by revolute pair between any two with the second secondary slide block (72), form second group of leverage,
First group of leverage is parallel to each other for each revolute pair axis be connected with in second group of leverage.
2. the high speed accurate numerical control press mechanism that drives of active-passive composite according to claim 1, is characterized in that: described first group of leverage with in second group of leverage for each turns auxiliary shaft line parallel of being connected in the pivot center of bent axle (1).
3. the high speed accurate numerical control press mechanism that drives of active-passive composite according to claim 1, is characterized in that: described first group of leverage is horizontally disposed and perpendicular to the pivot center of bent axle (1) for each revolute pair axis of being connected with in second group of leverage.
4. the high speed accurate numerical control press mechanism of active-passive composite driving according to claim 1, is characterized in that: described connection first connecting rod (21), second connecting rod (22) are revolute pair with the kinematic pair of master slider (3).
5. the high speed accurate numerical control press mechanism of active-passive composite driving according to claim 1, is characterized in that: described connection first connecting rod (21), second connecting rod (22) are ball pivot with the kinematic pair of master slider (3).
6. the high speed accurate numerical control press mechanism that drives of active-passive composite according to claim 1, is characterized in that: described first group of leverage and second group of leverage are arranged symmetrically in the both sides of bent axle (1).
7. the high speed accurate numerical control press mechanism that drives of active-passive composite according to claim 1, is characterized in that: described first group of leverage and second group of leverage antisymmetry are arranged in the both sides of bent axle (1).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310375595.4A CN103419387B (en) | 2013-08-27 | 2013-08-27 | High-speed precise numerical control press mechanism with driving and driven combination drive |
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| CN201310375595.4A CN103419387B (en) | 2013-08-27 | 2013-08-27 | High-speed precise numerical control press mechanism with driving and driven combination drive |
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| CN103419387A CN103419387A (en) | 2013-12-04 |
| CN103419387B true CN103419387B (en) | 2015-05-20 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109318518A (en) * | 2018-10-10 | 2019-02-12 | 南京理工大学 | A kind of enclosed Duo Gan dieing machine mechanism |
| CN109203536B (en) * | 2018-10-10 | 2021-05-07 | 南京理工大学 | Double-lever high-speed precision punch mechanism |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101219581A (en) * | 2008-01-21 | 2008-07-16 | 中山市胜龙锻压机械有限公司 | High speed accurate numerical control press |
| CN102275320A (en) * | 2011-08-31 | 2011-12-14 | 南京理工大学 | High-speed pressure machine |
| CN202208113U (en) * | 2011-07-22 | 2012-05-02 | 广东锻压机床厂有限公司 | Dynamic balance system of a high-speed precise pressing machine |
| CN102975386A (en) * | 2012-11-27 | 2013-03-20 | 南京理工大学 | High-speed precise numerical-control stamping machine mechanismstructure capable of realizing dynamic lower dead point precision compensation |
| CN203510736U (en) * | 2013-08-27 | 2014-04-02 | 南京理工大学 | High-speed precision numerical control punch mechanism driven actively and passively in combined mode |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ATE184236T1 (en) * | 1997-12-12 | 1999-09-15 | Bruderer Ag | PRESS, ESPECIALLY PUNCHING PRESS |
| JP2002144094A (en) * | 2000-11-13 | 2002-05-21 | Yamada Dobby Co Ltd | Press machine |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101219581A (en) * | 2008-01-21 | 2008-07-16 | 中山市胜龙锻压机械有限公司 | High speed accurate numerical control press |
| CN202208113U (en) * | 2011-07-22 | 2012-05-02 | 广东锻压机床厂有限公司 | Dynamic balance system of a high-speed precise pressing machine |
| CN102275320A (en) * | 2011-08-31 | 2011-12-14 | 南京理工大学 | High-speed pressure machine |
| CN102975386A (en) * | 2012-11-27 | 2013-03-20 | 南京理工大学 | High-speed precise numerical-control stamping machine mechanismstructure capable of realizing dynamic lower dead point precision compensation |
| CN203510736U (en) * | 2013-08-27 | 2014-04-02 | 南京理工大学 | High-speed precision numerical control punch mechanism driven actively and passively in combined mode |
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