SU1328047A2 - Drive of transfer mechanism for multistation automatic stamping machines - Google Patents

Abstract

The invention relates to forging and manufacturing and can be used in multi-positional forging machines. The aim of the invention is to improve positioning accuracy and reduce dynamic loads. This goal is achieved by the fact that in the drive of the transfer mechanism for multi-position punching machines containing a driving articulated four-link with lever 6 on the driven link and gear 8 mounted on the end of the lever with its crank 9 on its initial circumference, the gear sector 10 fixed on frame 2 and engaged with gear 8, as well as connecting the crank 9 with the carriage 13 by means of the hinge 12 with a radius of the initial circle three times smaller than the length of the lever 6, the center of the hinge 12 connecting the rod 11 with the carriage 13 is mixed relative to the central axis of the mechanism by the value of (q-p) and the length of the string is 11 l RVi # 4- (lq), where R is the radius of the initial circumference of the gear sector, and the coefficients p and q are determined depending on the angle vmax turning the lever 6 when the carriage 13 is standing. p 9 max 2,084-vmax (0.48+ + 0.28490 max) q 8psin eMaKc + 3sin 20MaKc / / 8 (1-cos Emks). When the crankshaft 1 rotates during the rotation of the lever 6 from an angle to 9 max 65 ° the carriage 13 is standing in the most forward position with minimal deviations. 4 il. (L 00 1CHE 00 about N to

Description

The invention relates to forging production, can be used in multi-positional forging machines and is an improvement of the invention according to the author. St. No. 1237293.

The purpose of the invention is to improve positioning accuracy and reduce dynamic loads.

FIG. Figure 1 shows the kinematic diagram of the drive of the transfer mechanism with the rearmost position of the carriage; in fig. 2 - the same, with the extreme front position of the carriage; in fig. 3 is a diagram of the carriage displacement; in fig. 4 shows plots of the carriage of the carriage of the transfer mechanism near the extreme forward position.

The drive of the transfer mechanism of the multi-station landing machine includes a crankshaft-type drive shaft 1 mounted in the base 2 of the automaton. The crankshaft 3 of the shaft 1 is connected with the levers 4 and 5 of the hinged four-bar drive OkABO. A lever 6 is rigidly connected to the lever 5, on the end of which a gear wheel 8 is mounted on the axis 7, carrying a crank 9, the axis of which is an arc link and the lever 6 rigidly connected with it about the axis O are insignificant. Axis 7, located at the end of the lever 6, and crank 9, located in gear 8, in this period of motion lie on one straight or very close to it position, therefore, a slight swing of lever 6 is compensated for by rolling gear pinion 8 along gear sector 10. As a result, the crank 9 maintains its position, and the carriage 13 stands in the rear extreme position, holding the grippers to the stamping position.

With further rotation of the drive shaft 1 from the crank 3, movement through lever 15 is transmitted to levers 5 and 6, which rotate relative to the hinge O. When the lever 6 is rotated, gear 8, rotating on axis 7, rolls along gear sector 10. Therefore, crank 9 performs a complex movement, which consists of moving the axis 7 along a circle, the radius of which is equal to the length of the lever 6, and the rotational movement of the crank 9 relative to the axis 7 when the gear 8 rolls along the gear sector 10. If the distance between axis 7 and

20

on the starting circle, the gear 25 axis of the crank 9 is three times smaller than the length of 8, and the radius of the crank 9 is three times the size of the lever 6 and the axis of the crank 9 is

less than the length of the lever 6. The gear 8 is meshed with the toothed sector

10, rigidly mounted on the frame 2 machine.

Crank 9 is connected by means of a hinge 11 by means of a hinge 12 to a carriage 13, which is mounted in guides 14 of an automaton bed. In the carriage 13, the mechanisms for gripping the workpieces and the elements of the upnap of the initial circle of gear 8 are located, then the crank 9 moves along an algebraic curve called an astroid.

In this case, the astroid turned 30 at an angle of 45 ° relative to the coordinate axes. During the period of movement along the trajectory I between points C and D, the crank 9 moves in a horizontal direction, equal in magnitude to the movement of the carriage 13 of the transfer mechanism SK. This equality

display them (not shown). The center of the hinge is 35 due to the fact that the ordinates of the points B and Gra 12 of the connection of the tractor 11 with the carriage 13 in the given coordinate system are equal, and

offset from the central axis x of the mechanism by

the carriage 13 moves along the X axis and the length of the string 11 is constant. After the axis of the crank 9 reaches the point G, it starts at 40 with a period of standing up of the carriage 13 in the forward position. During this period, the axis of the crank 9 moves along curve II, close to a circle of a certain radius. In this case, if the length of the string 11 is equal to this radius, and the joint of the joint of rod 11 with the carriage 13 is located in the center of this circle, during the period of movement of the crank 9 along curve II the carriage 13 will stand.

H (q-p),

a length of ti gi 11

 RVp4 (T

-q)

where R is the radius of the initial circle of the tooth sector 45;

40

p and q are the coefficients determined depending on the angle-in the mach.shift of the lever 6 when the carriage 13 is standing up.

In the extreme forward position, the stroke of the carriage 13 is limited by the stop 15 mounted on the frame 2 of the machine.

The drive works as follows. The drive shaft 1 rotates with the crank 3 in the direction of the arrow. In this case, point A moves around the circumference, but the movements of the levers 5 of the hinge four-link and the lever 6 rigidly connected with it relative to the axis O are insignificant. Axis 7, located at the end of the lever 6, and crank 9, located in gear 8, in this period of motion lie on one straight or very close to it position, therefore, a slight swing of lever 6 is compensated for by rolling gear pinion 8 along gear sector 10. As a result, the crank 9 maintains its position, and the carriage 13 stands in the rear end position, holding the grippers to the stamping position.

With further rotation of the drive shaft 1 from the crank 3, movement through lever 5 is transmitted to levers 5 and 6, which rotate relative to the hinge O. When you rotate lever 6, gear 8, rotating on axis 7, rolls around gear sector 10. Therefore, crank 9 performs a complex movement, which consists of moving the axis 7 along a circle, the radius of which is equal to the length of the lever 6, and the rotational movement of the crank 9 relative to the axis 7 when the gear 8 rolls along the gear sector 10. If the distance between axis 7 and

0

5, the axis of the crank 9 is three times less than the length of the lever 6 and the axis of the crank 9 is

the axis of the crank 9 is three times less than the length of the lever 6 and the axis of the crank 9 is

on the initial circle of gear 8, then crank 9 moves along an algebraic curve called an astroid.

In this case, the astroid is rotated by an angle of 45 ° relative to the coordinate axes. During the period of movement along the trajectory I between points C and D, the crank 9 moves in a horizontal direction, equal in magnitude to the movement of the carriage 13 of the transfer mechanism SK. This equality

This is explained by the fact that the ordinates of points C and D in the received coordinate system are equal, and

This is explained by the fact that the ordinates of points C and D in the received coordinate system are equal, and

the carriage 13 moves along the X axis and the length of the string 11 is constant. After the axis of the crank 9 reaches the point G, it begins with the period of standing of the carriage 13 in the forward position. During this period, the axis of the crank 9 moves along curve II, close to a circle of a certain radius. In this case, if the length of the string 11 is equal to this radius, and the joint of the joint of rod 11 with the carriage 13 is located in the center of this circle, during the period of movement of the crank 9 along curve II the carriage 13 will stand.

For the period of standing of the carriage 13, it is not necessary to use the whole curve I from point D to point D. As with the opposite direction and the carriage 13 stands, the angle of rotation of axis 7 and levers 6 and 5 is determined by the cyclogram of the transfer mechanism carriage in the system of mechanisms machine, taking into account the operating conditions of the drive mechanisms.

At the extreme forward position of the mechanism, the carriage 13 stands at a time

gate lever 6 at an angle. When the movement of the mechanism of the carriage 13 is in reverse, it also stands in the extreme forward position until the lever 6 rotates the angle, npi of which, i.e. until the lever 6 comes to the starting point of the trajectory II of the carriage stand. Next, the carriage 13 is mixed to the extreme rear position.

An analysis of the cyclograms of multi-positional forging machines shows that the longest rotation of the crank of the main shaft along the angle of rotation of the carriages of the transfer mechanisms can be ensured by turning the lever 6 to the angle. Therefore, in order to ensure a better carriage of the 13 B carriage, the period of rotation of the lever 6 in the range from 0 ° to 65 ° it is necessary to select the coordinates of the center of the astroid, i.e. the mixing of the center of the hinge 12 of the connecting rod 11 with the carriage 13 relative to the central axis of the mechanism and the length of the rod 11, equal to the conditional radius of curvature of the astroid, for this range of angles.

The calculated-ex and ep and mental values of the indicated parameters are practically for all mechanisms of transfer of the existing bulk forming machines, i.e. for the range of angles of rotation of the lever 6 when the carriage is standing 3 0 Emayu: 65 ° next. Mixing the hinge center 12 joints

H (q-p),

cable length 11

 RVp4 (l-q) -,

the radius of the initial circumference of the tooth sector 10; coefficients determined depending on the angle of the chromium ry chag when the carriage stands 13

H -

,, 084th "ah40.48 + 0.2849e" ak;

8pSin 6MaK: - | -3sin 26MaKc 8 (1-pops-vmak)

For the known transfer mechanism, the dimensions of the links are as follows, mm: Crank radius 3 of the drive shaft 45; link length 4,205; lever length 5 55; lever length 6 48; crank radius 9 16; the distance between the axes O and OC of the hinge four-table 200; the radius of the initial circumference of the toothed sector 1064. The angle between the levers 5 and 6. In this case, the mixing of the center of the hinge 12 of the connecting rod 11 with the carriage 13 relative to the central axis of the mechanism is 19 mm; and the length of the cable is 1 46.39 mm.

Curve 16 (FIG. 3) shows the main periods of operation of the transfer mechanism with the specified sizes. The advantage of the proposed drive transfer mechanism for

15

10 20

25

thirty

35

40

45

50

55

Compared to what is known, it is to improve the number of drivers on the section of the undercarriage 13 in the extreme forward position. Curve 17 11ok; 1z yet kinematic displacements from the extreme. south of the carriage 13. As can be seen, the deviation of the carriage 13 is about 0.1 mm, while when using the known drive of the carriage transfer mechanism the carriage deviations from the extreme forward position (curve 18) are more than 0.6 mm Such deviations should be compensated by the installation of the stop 15 due to elastic deformations in the mechanism. In the proposed mechanism, the stop 15 practically serves to facilitate the adjustment of the mechanism.

In order to check the optimality of the choice of mixing the hinge center of the joint of the tractor 11 with the carriage 13 relative to the central axis of the mechanism H and the length of the rod 11, 1, the position of the carriage 13 relative to the extreme front position was calculated for various deviations; values H and 1 from the calculated ones. For the case when the carriage is pulled, 39 mm, and the offset from the central axis mm, the carriage deviations from the extreme forward position in the range of the considered angles of rotation of the drive shaft crank 55-145 ° cannot be represented on the same scale with the graphs given as the amplitude the deviation is 7.436 mm. With the same length of g, 39 mm and displacement of the center of the hinge 12 of connecting grip 11 with the carriage mm, the amplitude of the deviations of the carriage from the extreme forward position in the range of the same angles of rotation of the drive shaft crank is 3.588 mm. While maintaining the optimal deviation of the hinge center of the coupling between the yoke 11 and the carriage relative to the axis of the mechanism, 19mm and with a decrease in the length of the yoke 11, for example, 0 mm, the amplitude of the deviations of the carriage 13 from the extreme forward position in the range of angles of rotation of the drive shaft 55-145 ° is 3.676 mm, and as the length of the string 11 increases to 1 56.0 mm, the amplitude of these deviations is 1.726 mm. With a simultaneous increase in the length of the rod of 11.0 mm and the displacement of the center of the hinge of the coupling rod 11 with the carriage H 25 mm, the amplitude of the deviations is 4.26 mm for the same conditions.

The values of the amplitude of the deviations of the position of the carriage from the frontmost in the given angle of the crank of the drive shaft, obtained for values of 1 and H that differ from the optimal pair of values calculated from the indicated dependencies, illustrate the stepwise increase in the amplitude of the deviations (not less than as far doc).

Thus, the proposed drive allows to obtain the required cyclogram of the operation of the carriage of the transfer mechanism carriage and replace the cam mechanisms in the drive by; (; i1K11full kinematic mechanisms ensuring the standing process with high positioning accuracy of the carriage. At the same time, beie in the system of the transfer mechanism, vibrations and associated with them high dynamic loads that lead to the loss of blanks when transferring them from one position to another. The use of the proposed drive reduces the dynamic loads and and OAPC; 1 rapidity a multiposition machines increase, and consequently their productivity gelnost.

Claims (1)

Invention Formula Drive transfer mechanism for multi-position punching machines according to ed. St. No. 1237293, characterized in that. that, for the purpose of guivicena, positioning accuracy and reduction of dynamic force The hinge, the hinge center of the coupling with the carriage is shifted relative to the central axis of the mechanism by (q-p), and the length 1- (l-q), a) adius beginning / 1n the circumference of the toothed sector; ko: :) you are. determined from dependencies G () ma „, 2.084-G«, Kc (0.48-fO, 28496 «« :);  8 p51p OmaksCh-Zt 20max 8 {1-COS-GV. where () M; IKC - the angle of rotation of the lever when standing carriage. // ten 15 sixteen forward 87 hovering ffopemnu d zden / no / ioweHULf survival no /} et / {u - b wen c / a 20 25 Phage.Z and mm Editor I. Nikolaichuk Order 3429/12 VNIIPI USSR State Committee for Inventions n discoveries 113035, Moscow, Zh-35, Raushsk iab., 4/5 Production and Printing Enterprise, Uzhgorod, ul. Project, 4 Compiled by N. Timofeeva Tehred I. VeresKorrektor S. Cherni Circulation 582 Subscription