JPS62134126A - Clamping/unclamping device for transfer press machine - Google Patents

Abstract

PURPOSE:To realize a quick separation and a slow approach of a feed bar against the up-and-down motion of a slide, by connecting a specifically a lever member, and an eccentric member on a crank shaft for moving up and down the slide, in a device for bringing the feed bar into contact and separate through the lever member. CONSTITUTION:Between the first eccentric member 13 for rotating together with a crank shaft 2, and a lever member 26, the first connecting member 14 whose one end has been connected to the member 13, and the second connecting member 18 which is connected freely turnable to the other end thereof and can execute freely a linear reciprocating motion are provided. Also, a moving member 24 which is freely movable in the direction of its oscillation center against the member 26 is provided on the member 18. When the shaft 2 rotates, the member 14 executes a crank motion, the member 18 executes only a linear up-and-down reciprocating motion, and together with the member 18, and member 24 moves up and down by executing a reciprocating motion in its oscillation center direction against the member 26. As a result, the member 26 is oscillated, a rack member 33 executes a linear reciprocating motion, pinions 34, 35, and the second eccentric members 36, 37 are turned, holding members 7, 8 and feed bars 9, 10 are brought into contact therewith and separate, and clamping and unclamping are executed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a clamping and unclamping device for approaching and separating feed bars of a transfer press machine. The present invention relates to an improvement of a device provided with the member.

[Background Art and Problems Therein] The present applicant previously provided a clamping and unclamping device for a transfer press machine as Utility Application No. 4648/1983.

In this device, a first eccentric member is fixed to the crankshaft of a press machine, a swingable lever member is connected to the first eccentric member via a rod-shaped connecting member, and the lever member is provided with a linear reciprocating motion. A freely movable rack member is connected, two pinions arranged at fixed positions and rotatable positions are meshed with the rack member, and a second eccentric member is fixed to each pinion, and these second eccentric members are connected to each other. is connected to a foot bar holding member which holds the feed bar and is movable in the clamp and angular directions. When the crankshaft is rotated, the first eccentric member rotates, and the lever member swings. As a result, the rack member moves back and forth linearly, causing the pinion and the second eccentric member to rotate, and the foot bar approaches and separates. conduct.

According to this device 'd, since the approaching and separating operations of the two feed bars are mechanically followed, high-speed operation of press working can be realized, and the effect of the first and second eccentric members allows the approach limit position, It can be said that the residence time at the separation limit position can be relatively short. However, when using a larger mold, the downward movement of the slide must be controlled to avoid collision between the upper mold and the feed bar. It is desired to move away (unclamp) as quickly as possible and approach (clamp) as late as possible with respect to the upward movement of the slide.

[Object of the Invention] The object of the present invention is that the feed bar is moved quickly away from the feed bar and approached slowly in response to the vertical movement of the slide, so that the relationship between the size of the upper die and the feed bar is better, and the vertical dimension is reduced. The present invention provides a clamp and unclamp device for a transfer press machine that is adaptable to large upper molds.

[Means and effects for solving the problem] Therefore, in the device according to the present invention, a swingable lever member is connected to a first eccentric member that rotates together with a crankshaft that moves the slide up and down, and a swingable lever member is connected to this lever member. connects a rack member capable of linear reciprocating motion, and engages two pinions provided with a second eccentric member on the rack member, and the second eccentric member.

By connecting the feed bar holding member that holds the feed bar and is movable in the work clamp and angle direction, the rack member is reciprocated linearly by the lever member that swings with the rotation of the first eccentric member. In the clamping and unclamping device for a transfer press machine, the pinion and the second eccentric member are rotated to move the two feed bars closer to each other and separate them from each other.
The connection mechanism between the eccentric member and the heel member includes a first connecting member whose one end is connected to the first eccentric member, and a first connecting member which is rotatably connected to the other end of the first connecting member and can freely reciprocate linearly. a second connecting member, and a movable member provided on the second connecting member so as to be movable in the direction of the center of movement of the lever member with respect to the lever member; 1
The rotation angle of the crankshaft is small due to the movement of the moving member relative to the lever member due to the linear reciprocating movement of the second connecting member and the movement of the heel member through the connecting member, the second connecting member, and the moving member. The lever member is characterized in that the swinging of the lever member is delayed during the interval, and when the rotation angle of the crankshaft becomes large and the lever member exceeds the midpoint of the swing angle, the swinging becomes faster.

[Example 1] In FIG. 1, the slide 1 is connected to a crankshaft 2 which is rotated by a motor (not shown) through a connector 3, and when the slide 1 moves up and down due to the rotation of the crankshaft 2, it connects with the upper die 4 attached to the slide 1. The workpiece is pressed with a lower die 6 attached to a bolster 5.

1tjl i between slide 1 and bolster 5 as shown in Figure 2
-"- is a feed bar near both ends, two parallel feed bars 9.10 held by holding members 7 and 8 are arranged, the feed bar 9.10 is provided with a finger 11, and the feed bar 9. , 10 approach, the workpiece is clamped by the fin force 11, and is unclamped by separating.The feed bar holding member 7,
8, and by this sliding,
The feed bars 9 and 10 advance in the horizontal direction in FIG. 1 to transport the workpiece clamped by the fingers 11 to the next processing stage, and after unclamping the workpiece, retreat to the original position.

As shown in Figure 1, the end of the crankshaft 2 or the crank 1k
The end of the rotating shaft connected to l12 protrudes from the side surface of the crown 12 of the press machine, and a first eccentric part l12 is attached to this protruding end.
3 is fixedly installed, and the first eccentric member 13 rotates together with the crankshaft 2. As shown in Figure 2, the upper end of a long rod-shaped 14th connecting member 14 is connected to the eccentric pin 1.3A of the 41g1 eccentric member 13, and this first connecting member 14 is connected to the left and right sides of the press machine as shown in Figure 1. placed on both sides. The lower portions of these first connecting members 14 are inserted into boxes 15 and 16 provided on the left and right sides of the press machine, and the lower portions of the first connecting members 14 are inserted into boxes 15 and 16 provided on the left and right sides of the press machine.
The main components of the clamping and unclamping device according to this embodiment are housed inside the housing 16 . Since the structures of the clamping and unclamping devices housed in each box 15 and 16 are the same, the following description will be made with respect to one device.

A device for advancing and retracting the foot pars 9 and 10 is also housed inside one side 15 of the boxes 15 and 16, and this device includes a rod member whose upper end is connected to the crankshaft 2 via an eccentric member. 17 reciprocates up and down with the rotation of the crankshaft 2, thereby inputting driving force.

Figure 3 shows the structure of the clamp and unclamp device δ,
A rod-shaped second connecting member 1 is attached to the lower end of the first connecting member 14.
The joint member 19 fixed to the double chain of 8 is the pin 20.
The second connecting member 18 is rotatably connected to the frame 2.
It is slidably inserted into a cylindrical guide member 22, 23 fixed to 1, and can freely reciprocate linearly in the vertical direction. A moving member 24 is attached to the second connecting member 18, and this moving member 24 is slidably fitted into a guide groove 27 of a lever member 26 that swings in a vertical plane about a horizontal axis 25, and is moved. The member 24 is a slider movable relative to the lever member 26.

As described above, the first connecting member 14 and the second connecting member 18 are arranged between the first eccentric member 13 and the lever member 26,
The first connecting member 14, the second connecting member 18, and the moving member 24 constitute a connecting mechanism that connects the first eccentric member 13 and the lever member 26.

5 to 7 show the specific structure of the moving member 24 and the lever member 26. As shown in FIGS. 6 and 7, the lever member 26 is composed of two flexible plates 28, and these plates A groove 28A for providing the guide groove 27 is formed in the groove 28, and a sliding member 29 for ensuring good sliding of the moving member 24 is fixed on the lower inner surface of the groove 28A. The moving member 24 has a pin 30 inserted through the second connecting member 18.
It consists of a square plate-shaped piece 31 rotatably attached to both ends of the plate, and the piece 31 is slidably arranged between the upper and lower sliding members 29, and the piece 31 is attached to the inner side ends of the two plates 28. The pin 30 is prevented from coming off in the axial direction by a protrusion 31A formed on the portion, and thereby the pin 30 is positioned in the axial direction between the movable member 24 and the lever member 26.

As shown in FIG. 5, the guide groove 27 extends toward the center of swing of the lever member 26 by the shaft 25, so that the movable member 24 is movable relative to the lever member 26 toward the center of swing of the lever member 26.

As shown in FIG. 3, a rack member 33 is connected to the lever member 26 via a connecting rod member 32, and the rack member 33 is supported horizontally by a support member (not shown). 9. It is capable of linear reciprocating movement in the approach and separation directions of 10. Two pinions 34.35 mesh with the rack member 33, and these pinions 34.35 are supported by a support member (not shown) so as to be rotatable about axes 34A, 35A perpendicular to the orientation 1δ.

The pinion 34.35 has a second eccentric member 36°37,
Eccentric bins 36A, 37A of these eccentric members 36, 37
and the feed/height holding member 7.8 are connected by a connecting rod member 38.39. Two round bar-shaped guide members 40 are inserted through the feed par holding member 7.8 and the feed par holding member 7.8 and the feed par 9,1o.
is movable to clamp and unclamp the workpiece (in the direction of approach and separation of the feeder).

When the feed pars 9 and 10 perform two-dimensional movements such as approaching and separating operations, forward movement, and backward movement, the second eccentric member 36, 37 is connected to the stove 7 by the F member 38, 39, and the feed par holding member 7 is moved as shown in FIG. , 8, but if the feeder 9.10 performs three-dimensional movements such as approaching, separating, advancing, retracting, and raising and lowering, the As shown, the second eccentric member 36.37 and the feed bar holding member 7.8 are connected by connecting the connecting rod 38.39 to a support member 41.42 that supports the feed bar holding member 7.8 in a vertically movable manner. and may be connected via support members 41 and 42. In FIG. 4, the same members as those described above are given the same reference numerals.

To explain the structure of FIG. 4, the feed bar holding member 7,
8 is rack par 43.44. It is movable up and down with respect to the support member 41.42 by guide bars 45.46, and a pinion 47.48 which meshes with the rack par 43.44 is rotatably provided inside the support member 41.42.

A large-diameter gear 49 is disposed at the swing center @j25 of the lever member 26 described in 1i71, a small-diameter gear 50 that meshes with the large-diameter gear 49 is fixed to a small-diameter gear 50, and a cylinder 5 is attached to the cam 51.
The piston rod 5 is constantly energized by the air pressure of 2.
No. 3 roller 54 is in contact with it. piston low 7do 53
is a rack member, and a spline shaft 56 is inserted into the inside of a pinion 55 that fits into the rack member.
are slidably inserted into and engaged with the insides of the pinions 47 and 48.

Next, we will discuss the effect.

When the crankshaft 2 rotates, the first eccentric member 13
The connecting member 14 and the second connecting member 18 connected in series to the first connecting member 14 move up and down. In this case, the first
The connecting member 14 performs a crank motion centering on the eccentric bin 13A, but the second connecting member 18 only performs a linear vertical reciprocating motion.

The moving member 24 moves up and down together with the second connecting member 18, and this up-and-down movement is performed while relative movement occurs between the moving member 24 and the guide groove 27, and the moving member 24 moves up and down with respect to the lever member 26. It moves up and down while reciprocating in the direction of the swing center of 26.

As a result, the lever member 26 swings about the shaft 25, and this swing causes the rack member 33 to linearly reciprocate, causing the pinion 34.35 and the second eccentric member 36.37 to rotate. As a result, the feed bar holding member 7.8 and the foot bars 9, 10 are moved along the guide member 40. If the eccentric pins 36A, 37A of the second eccentric member 36.degree. 37 are at a point symmetrical position with respect to the rotation center of the pinion 34.degree. 35 at the start of rotation of the crankshaft 2, the feed bar 9.10 will move symmetrically. The workpiece is moved closer to the workpiece for clamping, and separated for unclamping.

In the case of the structure shown in FIG. 4, the large-diameter gear 49 rotates due to the swing of the lever member 26, and this rotation is transmitted to the cam 51 via the small-diameter gear 50, causing the piston rod 5 to move up and down.
3 rotates the pinion 55 and spline shaft 56, as well as pinions 47 and 48, and the rack par 4
3.44, the feed bar holding member 7.8 and the feed bar 9.10 move up and down. Feet par 9,10
The raising operation is performed between the approach operation and the forward operation, and the lowering operation is performed between the 1111 advance operation and the separation operation.

FIG. 8 is an operational principle diagram showing the movement trajectory of the feed bars 9 and 10 when the crankshaft 2 rotates once and one drive cycle is completed. At this time, the lever member 26 is swinging back and forth. When the crank @112 rotates 360°, the second
The eccentric bins 36A, 37A of the eccentric members 36, 37 reciprocate in the range from the A position to the B position.
7A once reversely rotates from position C to position A, then reaches position B, returns from position B to position A, and then returns to position C. Feed bar 9.10 is eccentric bin 36A, 37A
Because the rotational movement of the workpiece is approached and separated by the workpiece clamp and angular component, we compared the residence time of the feet par 9 and 10 at the approach limit position and its vicinity, and at the separation limit position and its vicinity. This allows the feed bars 9 and 10 to move forward and backward, as well as to raise and lower the feed bars 9 and 10 in advance.

Also, when the crankshaft 2 rotates 360°, the moving member 2
4 performs a linear reciprocating motion in the range from the D position to the E position by moving relative to the lever member 26 through the guide groove 27. The swinging of the lever member 26 for approaching and separating the feed pars 9 and 10 is based on the previous Utility Model Application 1986-46.
This can also be realized by connecting the first eccentric member and the lever member with one connecting member as in No. 48 (hereinafter referred to as the earlier application); As in the example, two connecting members 14, 18 and a moving member 24
There is a difference in the swing angle of the lever member 26 with respect to the rotation angle of the crankshaft 2 depending on the case.

To explain this specifically, in the case of the previous application, the connection end on the lever member side of the connection member that connects the first eccentric member and the lever member runs along the circular arc trajectory F connecting the D position and the E position. Move back and forth. The radius of the first eccentric member and the length of the lever member are sufficiently small compared to the distance between the first eccentric member and the lever member, and the length component of the connecting member in the left-right direction in FIG. 8 can be ignored. When rotated by the same angle, the moving member 24 of this embodiment and the lever member side connecting end of the connecting member of the previous application are at the same horizontal height 1t in FIG. In other words, when the rotation angle of the crankshaft is 600 (this also applies to the case of 300' because the lever member swings back and forth with one rotation of the crankshaft), the moving member 24 is in the G position. The connection ends on the side of the /<one member are located at the G' position, respectively. Similarly, if the rotation angle of the crankshaft is 900 degrees (also 270 degrees), the H position and
', and when the angle is 120° (also 240°), it is at the work position and the ■' position.

Therefore, considering only the one-way swing of the lever member, if the crankshaft rotation angle is 00.900.180°, the swing angle of the lever member in this embodiment and the previous application will be the same. , 60°, the swinging angle in this embodiment is θ1, the swinging angle in the previous application is θ2, and 120°.
In the case of 0, it is 03 in this embodiment, and it is θ4 in the previous application.

Therefore, when the rotation angle of the crankshaft is in the range of 0° to 90°, the swinging angle of the lever member 26 of this embodiment is smaller than that of the previous application, so the swinging movement of the lever member 26 is delayed. On the other hand, in the range from 90° to 1800°, the swinging angle of this embodiment is larger than that of the previous application, so the swinging motion of the lever member 26 becomes more advanced.

The feed bar 9 when the lever member 26 swings with the above-mentioned characteristics with respect to the rotation of the crankshaft 2. IQ
approach,! The movement locus of the Fin is shown by a solid line J in FIG. On the other hand, the dash-dotted line shows the interlocking trajectory of the approach and separation of the feed bar in the previous application when the conditions such as the lever ratio of the lever member and the eccentricity of the second eccentric member are the same as in this embodiment. As shown in this graph, in this embodiment, feet per 9 and 10 are required to move between the approach limit position and the separation limit position, and the range of rotation angle of the rank shaft 2 is larger than that of the previous application. Also small, feed bar 9,
Crankshaft 2 when 10 has reached the approach limit position or a position near this, or the separation limit position or a position near this.
The range of rotation angles is larger than that of the earlier application. Therefore, in this embodiment, the residence time of the feed bars 9 and 10 at these positions is ensured for a long time.

In particular, since the feed bars 9 and 10 quickly return to the separation limit position as described above and remain at the separation limit position until late, the relationship with the upper die 4 becomes advantageous. That is, the upper mold 4 can be replaced with one of various flammability, but the large upper mold 4
Even if the upper mold 4 is replaced with a particularly large upper die 4, the feed bars 9 and 10 will separate quickly when the slide 1 descends, and the feed bars 9 and 10 will separate quickly when the slide I ascends.
0 approaches late, so upper type 4 and feet par 9.10
There will be no interference with the upper mold, and it will be possible to replace it with upper molds of various sizes.

Although the above-described embodiment is a pre-sliding type in which the movable member is slidably fitted into the guide groove of the lever member, the structure of the movable member is not limited to this. It may be of a roller type that moves along the lever member, and if necessary, the moving member moves along the lever member.
It suffices if it is movable in the direction of the swing center of the pulling member.

[Effects of invention According to the invention, for the vertical movement of the slide.

Since the feed bar is moved away quickly and approached slowly, the relationship between the size of the upper mold and the feed bar becomes better.

[Brief explanation of drawings]

Fig. 1 is a front view of the transfer press machine, Fig. 2 is a side view thereof, Fig. 3 is a perspective view showing the structure of the clamping and unclamping device, and Fig. 4 is an example in which the feed bar moves in three dimensions. Such a clamp. A front sectional view of the unclamp device, FIG. 5 is a partially sectional front view showing the structure around the moving member and lever member, and FIG.
FIG. 7 is a cross-sectional view taken along the line ■--■ in FIG. 5, and FIG. 8 is a diagram showing the principle of operation. l...Slide, 2...Crankshaft, 7, 8-...
- Fee 1" bar ffl holding member, 9.10... Feed bar 11... finger, 13... first eccentric member, 14... first connecting member, 18... second connecting member, 24... Moving member, 26... Lever member, 33.
... Rank member, 34.35 ... Pinion, 36.3
7... Second eccentric member.

Claims (1)

[Claims] (1) A swingable lever member is connected to the first eccentric member that rotates together with the crankshaft that moves the slide up and down, and a rack member that is capable of linear reciprocating movement is connected to this lever member, and this rack member is held at a fixed position. 2.
The feed has two parallel pinions in mesh, a second eccentric member provided on each pinion, and two parallel feed bars equipped with workpiece clamping fingers, and is movable in the clamping and unclamping directions. In a clamping/unclamping device for a transfer press machine connected to a bar holding member, a first connecting member having one end connected to the first eccentric member is provided between the first eccentric member and the lever member; a second connecting member rotatably connected to the other end of the connecting member so as to be capable of linear reciprocating movement;
A clamping and unclamping device for a transfer press machine, characterized in that the second connecting member is provided with a movable member that is movable in the direction of the swing center of the lever member with respect to the lever member.