CN112895009A - Novel die-cutting machine - Google Patents
Novel die-cutting machine Download PDFInfo
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- CN112895009A CN112895009A CN202011619414.4A CN202011619414A CN112895009A CN 112895009 A CN112895009 A CN 112895009A CN 202011619414 A CN202011619414 A CN 202011619414A CN 112895009 A CN112895009 A CN 112895009A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26F—PERFORATING; PUNCHING; CUTTING-OUT; STAMPING-OUT; SEVERING BY MEANS OTHER THAN CUTTING
- B26F1/00—Perforating; Punching; Cutting-out; Stamping-out; Apparatus therefor
- B26F1/38—Cutting-out; Stamping-out
- B26F1/44—Cutters therefor; Dies therefor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B26—HAND CUTTING TOOLS; CUTTING; SEVERING
- B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
- B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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Abstract
The invention discloses a novel die-cutting machine, which comprises a double-toggle rod mechanism and a cam mechanism, wherein the double-toggle rod mechanism in the main cutting mechanism of the die-cutting machine is rotationally driven by the cam mechanism, the cam mechanism comprises a cam, an upper driven piece and a lower driven piece, the cam is an equal-width cam, the end part of the upper driven piece is connected with the double-toggle rod mechanism, the end parts of the upper driven piece and the lower driven piece, which are close to the cam, are respectively provided with a cross rod or a transverse plate, the two cross rods or transverse plates are mutually parallel, the distance is a certain value, and the cam rotates in a space between the two cross rods or. The cam is adopted to drive the double-toggle rod mechanism, so that stable motion can be obtained, the cam can be kept synchronous when the speed is changed, the cam is always in a stable state, the motion stability of the main cutting mechanism is obviously improved, the well-designed cam mechanism can be used for the lifetime of equipment, and the service life is long; and the cam has compact structure and high reliability, can realize high-speed automation and obviously improve the working efficiency of the die-cutting machine.
Description
Technical Field
The invention relates to a novel die cutting machine.
Background
The main cutting mechanism of the die cutting machine drives the moving platform to move up and down, so that the functions of die cutting and hot stamping are realized. According to the current market of die-cutting machines and the conditions of die-cutting machine manufacturers, the main cutting mechanism is most widely applied to a double-toggle-rod mechanism driven by a connecting rod.
The motion law and the working performance of the double-toggle-rod mechanism have great influence on the speed and the precision of the die cutting machine. The double toggle rods are connected by hinges, and the moving platform connected with the double toggle rods performs reciprocating motion of left-right swinging and up-down swinging. In order to achieve good die cutting quality, when the die cutting machine really enters a die cutting state, the upper platform and the lower platform are strictly parallel, and the stress of the whole platform is uniform. To achieve this effect, the components of the double toggle lever mechanism are required to have strict dimensional relationships and dynamic characteristics. However, during operation of the die cutting machine, each bar member generates an inertial force when moving at a high speed, causing the speed of the bar member to fluctuate, and possibly causing vibration, noise, and the like.
Taking a MW1050 full-automatic flat-pressing flat-die cutting machine as an example, ADAMS software is applied to simulate a double-toggle rod mechanism, although the plane of the top platform is basically kept in a horizontal state in the working process of die cutting indentation, in the whole die cutting process, the maximum horizontal displacement of the movable platform can reach 3.4563mm, the maximum horizontal speed reaches 21.3277mm/s, and the maximum horizontal acceleration is 402.8365mm/s 2. The data show that the up-and-down reciprocating motion of the movable platform is in a state of up-and-down fluctuation and left-and-right shaking.
When the inclination angle of the movable platform in the horizontal direction is increased, the stress between the movable platform and the guide sliding block is correspondingly increased. Such a moving process is not beneficial to improving the processing speed of the die-cutting machine or improving the precision of the die-cutting machine; in addition, it can also affect the service life of the die cutting machine. The disadvantages of the entire double toggle lever are therefore as follows:
1) the pressure holding time is not long, even if the process requirements of most materials can be met, with the improvement of science and technology, people have higher and higher requirements on the materials, so that the processing performance of special materials is difficult to guarantee. For example, when processing large plastic materials, not only a sufficient die cutting force but also a sufficient dwell time are required;
2) although the upper plane of the movable platform is basically horizontal in the die cutting working stroke, the movable platform still has large horizontal displacement in the whole moving process, and the conditions of up-down fluctuation and side-to-side fluctuation are presented.
Disclosure of Invention
In order to solve the technical problem, the invention provides a novel die-cutting machine which can enable a movable platform to stably operate.
The invention provides the following technical scheme:
novel cross cutting machine, including two toggle link mechanism and cam mechanism, two toggle link mechanism in the cross cutting machine owner cutting mechanism are by cam mechanism rotary drive, cam mechanism includes the cam, go up follower and follower down, the cam is the constant width cam, it meets with two toggle link mechanism to go up the follower tip, it all is equipped with horizontal pole or diaphragm at the tip that is close to the cam to go up the follower, lower follower, two horizontal poles or diaphragms are parallel to each other and apart from being a definite value, the cam is at the space internal rotation between two horizontal poles or diaphragms and then drive the follower, the follower removes down.
Further, the cam is a symmetrical arc cam with equal width.
Further, the cam is an equiarc-side triangular cam.
Further, the cam is an asymmetric arc cam with the same width.
Furthermore, two ends of two parallel cross rods or transverse plates are connected by connecting rods to form a closed frame.
Further, the stroke of the die-cutting motorized platform is 40 mm.
Compared with the prior art, the invention has the beneficial effects that: the cam is adopted to drive the double-toggle rod mechanism, so that stable motion can be obtained, the cam can be kept synchronous when the speed is changed, the cam is always in a stable state, the motion stability of the main cutting mechanism is obviously improved, the well-designed cam mechanism can be used for the lifetime of equipment, and the service life is long; and the cam has compact structure and high reliability, can realize high-speed automation and obviously improve the working efficiency of the die-cutting machine.
Drawings
Fig. 1 is a schematic view of a cam driven dual toggle mechanism as described in example 1.
Fig. 2 is a schematic view of a symmetrical circular arc constant-width cam in embodiment 1.
Fig. 3 is a schematic view of a medium arc-edged triangular cam in embodiment 2.
FIG. 4 is a schematic view of an asymmetric circular arc constant-width cam in embodiment 3.
FIG. 5 is a schematic view of Δ KOK.
Fig. 6 is a schematic diagram of the contour line of the constant-width cam a.
Fig. 7 is a schematic diagram of the contour line of the constant-width cam b.
Fig. 8 is a schematic diagram of the contour line c of the constant-width cam.
Fig. 9 is a schematic diagram of the contour line of the constant-width cam d.
Fig. 10 is a schematic diagram of the contour line of the constant-width cam e.
Fig. 11 is a schematic view of the contour of the constant-width cam f.
Fig. 12 is a diagram of horizontal displacement, speed, acceleration and vertical displacement of the cam with the width equal to phi 150 degrees a.
Fig. 13 is a diagram of horizontal displacement, speed, acceleration and vertical displacement of the cam with the width equal to phi 150 degrees b.
FIG. 14 is a diagram of horizontal displacement, speed, acceleration and vertical displacement of a phi 150 ℃ cam with equal width.
Fig. 15 is a diagram of horizontal displacement, speed, acceleration and vertical displacement of the cam with equal width of phi 105 degrees d.
Fig. 16 is a diagram of horizontal displacement, speed and acceleration of a cam with equal width of phi 115 degrees e.
Fig. 17 is a diagram of horizontal displacement, speed and acceleration of a cam with equal width of phi 115 degrees f.
In the figure: 1. cam, 2, upper follower, 3, lower follower, 4, double toggle rod mechanism, 5, frame, 6, fixing plate, 61, lantern ring, 7, cross bar, 8, connecting rod.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Novel cross cutting machine, including two toggle link mechanism and cam mechanism, two toggle link mechanism in the cutting machine owner cuts the mechanism is by cam mechanism rotary drive, as shown in fig. 1, cam mechanism includes cam 1, go up follower 2 and lower follower 3, the cam is the cam of uniform width, can guarantee in the motion process, the pressure angle is unchangeable all the time, more specifically be symmetrical circular arc cam of uniform width, 2 tip of going up the follower meet with two toggle link mechanism 4, go up follower 2, lower follower 3 all is equipped with horizontal pole 7 at the tip of being close to cam 1, two horizontal poles 7 are parallel to each other and apart from being a definite value, cam 1 is rotatory and then drive follower 2 around the dead axle in the space between two horizontal poles 7, 3 upper and lower movements of follower, thereby drive two toggle link mechanism 4 drive cross cutting machine platform and make and cam structure adaptation law up-and-down move.
Two ends of two cross bars 7 parallel to each other are connected by connecting rod 8 and form closed frame 5, and this frame 5 can realize high pair and seal, does not need other external force device, reduces drive power, improves the work efficiency of cross cutting machine, and its working plane of closed frame easily forms the wedge oil film with the contact surface of cam, and wearing and tearing are little, more are applicable to the high-speed rotation of cam.
In order to play a good guiding role for the upper driven member 2 and the lower driven member 3 and prevent the two from deviating in the moving process, a fixing plate 6 can be arranged at a position close to the closed frame 5, and two lantern rings 61 which are respectively penetrated by the upper driven member 2 and the lower driven member 3 are fixedly arranged on the fixing plate 6, so that the moving reliability of the upper driven member and the lower driven member can be ensured.
For a die cutting machine, normal operation of the die cutting machine can be ensured as long as a gripper bar can smoothly pass through a die cutting platform in an intermittent paper feeding mechanism, the thickness of the gripper bar is about 30 mm, but the stroke of a movable platform of the traditional die cutting is about 80 mm, and the stroke of the movable platform is too much, so that the cutting speed of the die cutting machine is influenced, the energy consumption of the whole machine is increased, and the processing efficiency is influenced; and in addition, the motion stability is influenced, and the stroke of the die cutting platform is reduced as much as possible under the condition of ensuring that the gripper bar passes through smoothly, so that the stroke of the movable platform is selected to be 40 mm.
The following describes part of the design of the cam of the present embodiment with reference to fig. 2:
the following parameters are listed: the displacement profile angle Φ of the cam, the working plane distance H of the frame follower, the frame follower travel H, are known from fig. 2:
OK1＝OK2＝R；OK＝r；O1K1＝O2K2＝r1；O2K1＝O2K＝O1K2＝r2。
wherein R + R ═ H and R-R ═ H, by addition or subtraction of the two formulae
Formed by an isosceles triangle OO1O2Can obtain the product
From FIG. 2, the following equation 2.1 can be written:
O1O2+r1＝OO1+r h+r＝OO1+r1(formula 2.1)
Adding the above formulas and substituting to obtain
The obtained formula is substituted into formula 2.1, and the formula can be obtained
r1＝h+r-OO1 r2＝OO1+r
Through the formula, the sizes of the symmetrical circular arc equal-width cam with the displacement profile angle phi not equal to 120 degrees can be basically determined, and the sizes of the cam are conventionally designed according to relevant parameters of the die cutting machine.
The cam mechanism driven dual toggle lever mechanism employed in the present application is compared with conventional cylinder driven and link driven actions as follows:
1. driving by using an air cylinder: in terms of energy consumption, the energy consumption of the cam is less than that of an air cylinder device, the energy of the air cylinder is converted by an air compressor, and conversion loss and leakage exist; in the service life, the well-designed cam mechanism can be used for the lifetime of equipment, but the cylinder cannot be used; on the structural motion characteristic, the cam mechanism has compact structure and high reliability, and can realize high-speed automation; in the aspect of stable and reliable movement, a pneumatic device is used, the impact is large when the pneumatic action is finished, a throttle valve needs to be adjusted when the speed is changed, when the production speed is increased greatly, the cylinder device obviously has no function, the cam mechanism can obtain stable movement, the cam can be kept synchronous when the speed is changed, and the cam is always in a stable state; in the time sequence of the movement, the action of the air cylinder is required to be one action to be completed before the next action is carried out, the displacement and the time of the cam are determined, and the next action can be started when one action is not finished.
2. Link drive, the following table shows the comparison of the advantages of the two mechanisms
In summary, the cam mechanism is simple in structure and low in later maintenance cost, while the link mechanism is relatively large in structure and not suitable for occasions with small space, and obviously the cam mechanism has great advantages for the die cutting machine.
Example 2
The cam of this embodiment is an equilateral triangular cam as shown in fig. 3, in which the cam profiles are formed by circular arcs drawn by radii R around three vertices O, A and B of an equilateral triangle Δ OAB, and after one cycle of operation, the upper follower and the lower follower stop at the upper and lower limit positions in the frame, respectively, where the position shown is the start of the upper limit position.
Example 3
The cam of this embodiment is an asymmetric arc cam with the same width as that shown in fig. 4, and when the cam is operated, if only one side of the cam is loaded, the cam profile can be adopted, and in order to reduce abrasion, the operating profile of the cam can be designed to be a small curvature arc.
Specifying a size code number:
OK2＝OK3＝R；OK＝OK5＝r；O2K3＝O2K4＝r1；O1K4＝O1K5＝r2；
O2K＝O2K1＝r3；O1K1＝O1K2＝r4；OO1＝A。
wherein R + R ═ H and R-R ═ H, by addition or subtraction of the two formulae
From fig. 4 it can be written that: o is1O2＝A-h+OO2
By Δ O in FIG. 41O2O, substituting the value of the formula into the formula, and finishing to obtain
The remaining geometry of the cam can be determined by the following equation:
r1＝R-OO2 r2＝OO1+r r3＝OO2+r r4＝R-OO1
all the geometric dimensions of the asymmetrical circular arc equal-width cam can be calculated through the formula.
Wherein, the minimum dimension H of the asymmetrical arc cam with the same width0And dimension a is determined as follows:
1)H0is determined
As shown in fig. 5, since the cam profile is designed with equal width, Δ KOK must be within the profile, according to geometric theorem, it can be found that:
when phi is more than or equal to 120 degrees, R is more than or equal to KK;
the side OK in Δ KOK is the maximum side, and when r is 0:
R-r≈R＝h,R+r＝R≈h＝H0(formula 2.4)
The lowest size H of the cam outer contour can be determined by the formula 2.40＝R。
When phi is less than 120 degrees, R is less than KK;
the lower limit value of KK is equal to the minimum dimension H of the cam profile0The minimum size can be obtained as follows:
2) determination of A
The upper limit of dimension A cannot exceed the cam profile, and thus, the upper limit of dimension A is
After sorting, the lower limit value formula of A can be determined:
the following displacement profiles for each cam are respectively: carrying out simulation analysis on the cam with phi of 150 degrees, phi of 120 degrees, phi of 115 degrees and phi of 105 degrees, taking the stroke of a frame driven piece (namely an upper driven piece, a lower driven piece and a frame) as h of 185mm, designing the outline of each cam for comparison, and firstly taking phi of 150 degrees, wherein the design steps are as follows:
1) cam profile minimum dimension H0
Obtaining H according to the formula 2.40＝h＝185。
2) Limit range of the calculated dimension A
According to the above formula
Substituted data is available
106.8098≤A≤185
3) Calculate the dimension OO2
According to formula 2.3, when A is 185
Get A equal to OO2＝OO1Then, according to the formula 2.2, obtain
When A is 150, the formula is shown as 2.3, and the compound is obtained
(1) Calculating the dimensions R and R
(2) Calculating the remaining dimension r1,r2,r3,r4
When a is 185:
r1＝185-106.81219＝78.18781
r2＝185+0＝185
r3＝106.8129+0＝106.8129
r4＝185-185＝0
when A is OO2＝OO1124.7993:
r1＝185-124.7993＝60.2007
r2＝124.7993+0＝124.7993
r3＝124.7993+0＝124.7993
r4＝185-124.7993＝60.2007
when a is 150:
r1＝185-112.2691＝72.7309
r2＝150+0＝150
r3＝112.2691+0＝112.2691
r4＝185-150＝35
the same principle can be used to obtain the cam profile geometric dimension of phi 120 degrees, phi 115 degrees and phi 105 degrees. See table 2.1 below for details.
TABLE 2.1 different value cam profiles
The calculated geometry from the given data was used to draw a cam profile using simulation software, as shown in fig. 6-11.
The obtained cams with different contour lines are guided into ADAMS software, are matched with a double-toggle-rod mechanism for analog simulation, and the driving value 750 d.min of the driving part cam is input to obtain simulation data of horizontal displacement, horizontal speed and horizontal acceleration of the movable platform, and the horizontal displacement, horizontal speed and horizontal acceleration change values of the movable platform under the driving of the six cams are shown in the lower graphs of FIGS. 12 to 17.
According to the simulation data of the profiles, as long as the cam is adopted to drive the double-toggle-rod mechanism, the motion stability of the main cutting mechanism of the novel die cutting machine is greatly improved, the cam has remarkable advantages in service life due to the characteristics of the mechanism, and meanwhile, the overall working efficiency of the die cutting machine can be greatly improved.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (6)
1. Novel cross cutting machine, its characterized in that: including two toggle link mechanism and cam mechanism, two toggle link mechanism are by cam mechanism rotary drive, cam mechanism includes cam (1), goes up follower (2) and lower follower (3), and the cam is the constant width cam, goes up follower (2) tip and meets with two toggle link mechanism (4), goes up follower (2), lower follower (3) all is equipped with horizontal pole (7) or diaphragm at the tip that is close to the cam, and two horizontal poles or diaphragm are parallel to each other and apart from being a definite value, and cam (1) space internal rotation between two horizontal poles or diaphragm and then drive follower (2), lower follower (3) remove.
2. The die cutting machine of claim 1, wherein: the cam is a symmetrical arc cam with equal width.
3. The die cutting machine of claim 1, wherein: the cam is an equiarc-side triangular cam.
4. The die cutting machine of claim 1, wherein: the cam is an asymmetric arc cam with equal width.
5. The die cutting machine of claim 1, wherein: two ends of the two parallel cross rods (7) or the two ends of the transverse plates are connected by connecting rods (8) to form a closed frame (5).
6. The die cutting machine of claim 1, wherein: the stroke of the movable platform of the die cutting machine is 40 mm.
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| CN202011619414.4A CN112895009A (en) | 2020-12-30 | 2020-12-30 | Novel die-cutting machine |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB890132A (en) * | 1958-09-19 | 1962-02-28 | Bobst Fils Sa J | Improvements in or relating to platen presses for working sheet material |
| TW448061B (en) * | 2000-11-30 | 2001-08-01 | Wu Ching Lung | Rotational motion damper |
| CN202186111U (en) * | 2011-07-27 | 2012-04-11 | 上海耀科印刷机械有限公司 | Driving mechanism for movable platform of automatic die cutting machine |
| CN207736418U (en) * | 2018-01-18 | 2018-08-17 | 东莞市东浩印刷有限公司 | A kind of automatic die cutter |
| CN208841573U (en) * | 2018-07-23 | 2019-05-10 | 苏州东诚欣电子有限公司 | A kind of die-cutting machine Zhu Qie mechanism |
| CN109927103A (en) * | 2019-04-28 | 2019-06-25 | 青岛科技大学 | A kind of new automatic double-deck perforating device |
-
2020
- 2020-12-30 CN CN202011619414.4A patent/CN112895009A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB890132A (en) * | 1958-09-19 | 1962-02-28 | Bobst Fils Sa J | Improvements in or relating to platen presses for working sheet material |
| TW448061B (en) * | 2000-11-30 | 2001-08-01 | Wu Ching Lung | Rotational motion damper |
| CN202186111U (en) * | 2011-07-27 | 2012-04-11 | 上海耀科印刷机械有限公司 | Driving mechanism for movable platform of automatic die cutting machine |
| CN207736418U (en) * | 2018-01-18 | 2018-08-17 | 东莞市东浩印刷有限公司 | A kind of automatic die cutter |
| CN208841573U (en) * | 2018-07-23 | 2019-05-10 | 苏州东诚欣电子有限公司 | A kind of die-cutting machine Zhu Qie mechanism |
| CN109927103A (en) * | 2019-04-28 | 2019-06-25 | 青岛科技大学 | A kind of new automatic double-deck perforating device |
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