CN105774010A - Pressing Machine - Google Patents
Pressing Machine Download PDFInfo
- Publication number
- CN105774010A CN105774010A CN201510845854.4A CN201510845854A CN105774010A CN 105774010 A CN105774010 A CN 105774010A CN 201510845854 A CN201510845854 A CN 201510845854A CN 105774010 A CN105774010 A CN 105774010A
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- CN
- China
- Prior art keywords
- crank axle
- main shaft
- connecting rod
- axial portion
- shaft part
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
- B30B1/266—Drive systems for the cam, eccentric or crank axis
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
Abstract
A pressing machine having a structure improved to smoothly transmit a rotary driving force among a plurality of crankshafts, and so as to have improved start/stop performance and improved press forming accuracy, and so as to permit reduction of a cycle time required for forming the desired product. In the pressing machine having a plurality of crankshafts (34) each having main shaft portions (30) and an eccentric shaft portion (32), at least one first connection lever (48) is attached to the eccentric shaft portions (32) of the plurality of crankshafts for rotating the plurality of crankshafts in synchronization with each other, and a second connection lever (56) is attached to pins (54) which are formed integrally with the respective crankshafts, and positions of which as seen in a circumferential direction of the main shaft portions are different from those of the eccentric shaft portions.
Description
Technical field
The present invention relates to forcing press, especially relate to the forcing press possessing the structure being modified as follows, this structure being modified makes: can transmit rotary driving force swimmingly between the crank axle of many crank axles of the slider-actuated made for stamping die installation.
Background technology
In the past, as the forcing press utilizing crank axle to be driven, it is known that following forcing press: make many crank axles synchronously rotate, so that the slide block for stamping die installation moves back and forth.And, as one of this forcing press, present applicant specify that following forcing press before this in Japanese Unexamined Patent Publication 9-155595 publication (patent documentation 1): utilizes yoke (yoke) that the rotary motion of at least 1 crank axle in many crank axles is transferred to other crank axle.Therefore, the rotary motion making the crank axle (driving crank axle) being driven in rotation is transmitted by yoke so that other crank axle (driven crank axle) and such driving crank axle are synchronously rotated.
But, in this transmission structure employing yoke, when the central shaft (center of rotation axle) of the many respective major parts of crank axle is all positioned in a plane with the central shaft of eccentric part, direction of transfer based on the power of yoke becomes straight line, thus there is the direction of rotation temporary transient unascertainable point, the i.e. so-called stop that make driven crank axle.Accordingly, there exist following problem: between many crank axles, be difficult to transmit swimmingly rotary motion.
In such a case, the slide-driving device of the forcing press disclosed in Japanese Unexamined Patent Publication 52-53476 publication (patent documentation 2) specify that: have in the slide-driving device of forcing press of each slide block in left and right, in order to the slider-actuated power of the slide block side by putting on a side is transferred to the slide block side of the opposing party, utilize have dephased 2 connecting rods and by connected to each other for the slider-actuated gear of left and right, it is possible to smoothness and strongly rotate the power transmission to the gear separating configuration.
But, in such an embodiment, there are the following problems: owing to using the geared parts that a lot of moment of inertia (inertia force) is big, therefore, overall as forcing press, moment of inertia based on these geared parts becomes very big, thus, the response during startup of forcing press and when stopping, the startup Stopping Ability of so-called forcing press are poor.Further, since be in order to by driving force from the slide block side (drive source) of a side to the transmission of the slide block side of the opposing party by the structure of connecting rod and multiple gear, therefore response (startup Stopping Ability) and synchronization accuracy are poor.Further, there is a problem in that: when the startup of forcing press and when stopping, the rotation amount of crank axle or even the change because of moment of inertia of the displacement of slide block, machining accuracy is likely deteriorated, and in addition, is also difficult to make the molding cycle of forcing press to accelerate.
And, in such patent documentation 2, in order to avoid connecting rod interference each other, each connecting rod and gear (idle pulley) or the interference rotating spindle unit, adopt following structure: idle pulley is divided into 2 gears rotated coaxially, each connecting rod and each gear are linked respectively, and make the idle pulley after this segmentation obtain synchronization each other via the idler gear of wide cut, therefore, the structure of device entirety becomes extremely complex.Further, it there is a problem in that: except parts number of packages is many, needs to adjust the precision of each gear, gap to make the slide block of left and right synchronously drive, and therefore, the cost making device overall according to its countermeasure is surging.
Prior art literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 9-155595 publication
Patent documentation 2: Japanese Unexamined Patent Publication 52-53476 publication
Summary of the invention
At this, the present invention completes with described situation for background, its problem solved is in that to be provided with the forcing press of the structure being modified as follows, this structure being modified makes: the transmission of the rotary driving force of many crank between centers can be made to become smooth and easy, and then be capable of the improvement starting Stopping Ability of forcing press and the raising of machining accuracy, and it is capable of the high speed of molding cycle.
And, the forcing press of the present invention, for the problem that solves as above and the basic structure being formed as, many crank axles are respectively provided with: two main shaft part, and it positions in coaxial fashion；nullAnd eccentric axial portion，It configures prejudicially relative to this main shaft part between above-mentioned two main shaft part，These crank axles separate the interval of regulation respectively with its state being axially parallel to each other、And sentence, in the two main shaft part, the mode that can rotate and be bearing in framework，The displacement of this eccentric axial portion formed by the rotation based on this crank axle being center of rotation with the central shaft of this main shaft part，The slide block that side, the other end with connecting rod is linked back and forth drives，The one end of above-mentioned connecting rod links with this eccentric axial portion，Above-mentioned forcing press is characterised by，For the rotary driving force of a crank axle in input to above-mentioned many crank axles is transferred to other crank axle、And make the first connecting rod that these many crank axles rotate with being mutually in step be installed on each above-mentioned eccentric axial portion，On the other hand，A side's in the above-mentioned two main shaft part of above-mentioned many crank axles、From the one end that above-mentioned framework is projected toward the outside，It is respectively arranged with the eccentric rod stretched out along the direction axially at a right angle with above-mentioned main shaft part，And，Pin is respectively arranged at these eccentric rods，This pin highlights along the axially in parallel direction with this main shaft part in the circumferential position different relative to the circumferential position of this main shaft part from above-mentioned eccentric axial portion、And the end on its projected direction is positioned at the one end position in the outer part than this crank axle，And，Second connecting rod is respectively arranged in the end on the projected direction of these pins，Synergism by such first connecting rod and the second connecting rod，Above-mentioned rotary driving force is transferred to swimmingly other crank axle above-mentioned.
Additionally, an optimal way according to such forcing press involved in the present invention, in the rotation of the above-mentioned crank axle being center of rotation with the central shaft of above-mentioned main shaft part, the phase place of above-mentioned eccentric axial portion are set to 90 ° with the difference of the phase place of above-mentioned pin.
It addition, in the present invention, it is preferred to adopt following structure: the central shaft of above-mentioned pin is set to bigger relative to the offset of the central shaft of this main shaft part than the central shaft of above-mentioned eccentric axial portion relative to the offset of the central shaft of above-mentioned main shaft part.
Further, in the present invention, it is preferred to above-mentioned second connecting rod is set to the parts thinner than above-mentioned first connecting rod wall.
And, an advantageous manner according to forcing press involved in the present invention, it is provided with many above-mentioned first connecting rods, utilize each of these many first connecting rods respectively by connected to each other for the above-mentioned eccentric axial portion of mutually adjacent above-mentioned crank axle, further, these many first connecting rods are to clip the position of the one end being linked with above-mentioned connecting rod and axially alternately arranging in this eccentric axial portion respectively.
Additionally, in the present invention, it is preferably as follows structure: be equipped with the rotary driving force being subject to this crank axle respectively in the both sides of a crank axle for the input of above-mentioned rotary driving force and other crank axle above-mentioned rotated, it is utilized respectively above-mentioned first connecting rod and by mutually adjacent, above-mentioned eccentric axial portion for a crank axle of this rotary driving force input is connected to each other with the above-mentioned eccentric axial portion of this other crank axle, and, it is installed on two above-mentioned first connecting rods of the crank axle inputted for this rotary driving force, clip the position of the one end being linked with above-mentioned connecting rod and axially alternately arranging in this eccentric axial portion respectively.
Further, in the present invention, above-mentioned eccentric axial portion is configured to: the minor diameter part that large-diameter portion is thinner than the diameter of this large-diameter portion with diameter is formed coaxially, and the one end of above-mentioned connecting rod is assembled in this large-diameter portion, and on the other hand, above-mentioned first connecting rod is installed on this minor diameter part.
In addition, an optimal way according to such forcing press involved in the present invention, above-mentioned slide block is the rectangular shape of long side direction length under overlooking, above-mentioned many crank axles axially become the direction at a right angle relative to the long side direction of this slide block, it is spaced at intervals that above-mentioned many crank axles are configured on the long side direction of this slide block.
Invention effect
So, in forcing press involved in the present invention, first connecting rod is installed on each eccentric axial portion of the eccentric axial portion of many crank axles, on the other hand, the one end of the side's main shaft part in two main shaft part of many crank axles, second connecting rod is installed on pin respectively via eccentric rod, this pin is arranged at the circumferential position different relative to the circumferential position of main shaft part from eccentric axial portion, therefore, synergism by these first connecting rods and the second connecting rod, and the rotary driving force of the crank axle inputted at most root crank axle is transferred to other crank axle swimmingly.
Therefore, according to forcing press involved in the present invention, make the installation portion phase place rotating driving relative to crank axle of the first connecting rod, with the installation portion of the second connecting rod relative to crank axle rotate drive phase place in the direction of rotation of crank axle different, thus, in the transmission mechanism of the rotary driving force based on the first connecting rod, even if when other crank axle arrives stop, the power of the direction of rotation determining other crank axle it is applied with also by the second connecting rod, overall as forcing press, no longer there is the stop of the transmission of the rotary driving force of many crank between centers, so, rotary driving force can be made to transmit swimmingly between these many crank axles.
Additionally, in forcing press involved in the present invention, owing to being the structure not needing geared parts, therefore, the big moment of inertia being had by such geared parts will not be subject to and the harmful effect caused, thus having the advantage that the startup Stopping Ability that can advantageously improve forcing press, and desired punch process can be carried out with high manufacturing accuracy, additionally it is possible to make the molding cycle of forcing press be effectively realized high speed.Further, owing to not needing geared parts, following features can also therefore be played: the structure of forcing press entirety is simplified, and the manufacturing cost of device decreases.
And, structure due to one end that have employed a side that eccentric rod is respectively arranged in two main shaft part of many crank axles, that be projected toward the outside from framework, therefore without increasing framework in order to the second connecting rod is installed, thus the distance having the further advantage that between the main shaft part (bearing) supported by framework will not become big, it is easy to guarantee these main shaft part concentricity each other.
Further, in forcing press involved in the present invention, owing to the end on the projected direction of the pin installed for the second connecting rod is positioned at the one end position in the outer part than crank axle, therefore, it is possible to advantageously avoid the interference of the second connecting rod and crank axle.
Accompanying drawing explanation
Fig. 1 indicates that cross section, the front portion explanation figure of an example of the forcing press according to the present invention.
Fig. 2 is the Section A-A part explanation figure of Fig. 1.
Fig. 3 is the end face part explanation figure in the section B-B of Fig. 2.
Fig. 4 is the end face part explanation figure in the C-C cross section of Fig. 2.
Fig. 5 is the D-D section explanation figure of Fig. 2.
Fig. 6 is the E-E cross section amplifier section explanation figure of Fig. 5.
Fig. 7 indicates that the end face part explanation figure corresponding with Fig. 3 of the different type of drive of the forcing press shown in Fig. 1.
Fig. 8 indicates that the end face part explanation figure corresponding with Fig. 4 of other different type of drive of the forcing press shown in Fig. 1.
Fig. 9 indicates that the end face part explanation figure corresponding with Fig. 2 of other different type of drive of the forcing press shown in Fig. 1.
Figure 10 indicates that the section explanation figure corresponding with Fig. 2 of other examples of the forcing press according to the present invention.
Figure 11 indicates that the cross section local specification figure corresponding with Fig. 2 of an other example of the forcing press according to the present invention.
Description of reference numerals
10,64,66 forcing press
18 frameworks
24 slide blocks
30 main shaft part
32 eccentric axial portion
32a large-diameter portion
32b minor diameter part
34 crank axles
38 connecting rods
48 transmission levers
52 eccentric rods
54 pins
56 depart from bar
60 clutch mechanisms
62 flywheels
The central shaft of P main shaft part
The central shaft of Q eccentric axial portion
The central shaft of R pin
L virtual line
Detailed description of the invention
Hereinafter, in order to make present invention specific, concrete more, with reference to accompanying drawing, embodiments of the present invention are described in detail.
First, Fig. 1 illustrates an example of forcing press according to the present invention in the way of the front view comprising a part of section.Herein, forcing press 10 possesses the framework 18 of the Construction integration being made up of bottom framework 12, intermediate frame 14 and top framework 16, upper surface at the backing plate 20 being placed in regularly in its underpart framework 12 is provided with counterdie 22, on the other hand, at the lower surface of the slide block 24 being disposed in intermediate frame 14, the upper mould 26 constituting stamping die together with such counterdie 22 is installed.Additionally, slide block 24 guides the state for moving along the vertical direction to arrange with a pair slider guide 28,28 relatively arranged by the internal face with intermediate frame 14.It addition, as described later, in top framework 16, multiple (here for the 3) crank axle 34,34,34 with main shaft part 30 and eccentric axial portion 32 is supported as rotating.
It addition, in the bar portion 36,36,36 that is integrally provided in the way of extending above towards vertical direction by surface from it of slide block 24, link with crank axle 34,34,34 via connecting rod 38,38,38.Specifically, each connecting rod 38,38,38 is rotatably assembled in the eccentric axial portion 32 of crank axle 34 respectively at its one end (upper end) via sleeve 40, on the other hand, rotatably it is assembled in the upper end in the bar portion 36 of slide block 24 by crank-pin 42 in the other end (bottom).Thus, the displacement of the eccentric axial portion 32 formed by the rotation based on the crank axle 34 being center of rotation with the central shaft (P) of main shaft part 30, back and forth drive slide block 24 along the vertical direction.Reciprocating motion (moving up and down) with such slide block 24, mould 26 is moved in the way of/separation close relative to counterdie 22, the punch process work piece being configured on this between mould 26 and counterdie 22 specified samely.
Herein, as in figure 2 it is shown, each crank axle 34,34,34 is respectively in the main shaft part 30,30 formed coaxially, via bearing 44,44 and can be bearing in framework 18 (top framework 16) in the way of rotating.Thus, the central shaft P of main shaft part 30,30 is configured to the center of rotation axle of crank axle 34.Although additionally, be not explicitly depicted in fig. 2, but, it is configured in the present embodiment: slide block 24 is made up of the flat board of the wall thickness of rectangular shape when overlooking being long limit, correspondingly, the cross section of top framework 16 is the rectangular box shape on long limit under overlooking.And, crank axle 34,34,34 respectively by they axially along the extension of orthogonal relative to the long side direction of slide block 24 direction in the way of, in other words, by their center of rotation axle P along in the way of the short side direction extension of top framework 16 on the long side direction of slide block 24 (top framework 16) spaced at intervals and configure.
Further, the eccentric axial portion 32 of crank axle 34 is parallel with described main shaft part 30 and be eccentrically formed in the position leaving predetermined distance (X) relative to main shaft part 30 towards the direction (left direction here in Fig. 2) of its radially (with direction axially at a right angle) between main shaft part 30,30.Herein, between the central shaft P and the central shaft Q of eccentric axial portion 32 of main shaft part 30 and the offset X that distance X is eccentric axial portion 32 on axle direction at a right angle.Further, such eccentric axial portion 32 is configured to: constitutes the large-diameter portion 32a of central part and clips this large-diameter portion 32a and constitute minor diameter part 32b, the 32b at both ends and formed coaxially, and the one end of connecting rod 38 assembles relative to this large-diameter portion 32a.Additionally, be integrally formed with scutellate divider plate portions 46,46 between this large-diameter portion 32a and minor diameter part 32b, 32b respectively.
And, in the forcing press 10 of present embodiment, mutually adjacent 2 crank axles 34,34 are linking up by long plate shape separately from each other as the rotary driving force transmission lever 48 (hreinafter referred to as transmission lever 48) of the first connecting rod.It addition, these transmission levers 48,48 respectively via sleeve 50 so that the eccentric axial portion 32 (with reference to Fig. 3 and Fig. 4) of crank axle 34 can be installed in the way of rotating.
More specifically, it is clear that from Fig. 2 and Fig. 3, in figure, the crank axle 34 of the leftmost side and the crank axle 34 of central authorities are linked up by transmission lever 48 in minor diameter part 32b, 32b of the one end side (downside in Fig. 2) of these crank axles 34,34, on the other hand, being clear that from Fig. 2 and Fig. 4, in figure, the crank axle 34 of the rightmost side and the crank axle 34 of central authorities are linked up by transmission lever 48 in minor diameter part 32b, 32b of the side, the other end (upside in Fig. 2) of these crank axles 34,34.Like this, in the crank axle 34 of central authorities, 2 transmission levers 48,48 of installation clip the position (large-diameter portion 32a) being linked with connecting rod 38 and axially alternately arranging in eccentric axial portion 32 respectively.In other words, the both sides at the position (large-diameter portion 32a) being linked with connecting rod 38 that 2 transmission levers 48,48 are disposed in the eccentric axial portion 32 of central crank axle 34, and stretch out from such eccentric axial portion 32 towards parallel and with eccentric axial portion 32 the opposed both direction axially at a right angle of plane with the axle of the eccentric axial portion 32 of the crank axle 34 including central authorities and the crank axle 34 being disposed in its both sides.
Additionally, such as Fig. 2 and Fig. 5, shown in Fig. 6, at each crank axle 34, 34, two main shaft part 30 of 34, in a side (main shaft part 30 here for the downside in Fig. 2) in 30, the one end (end of downside in fig. 2) being projected toward the outside from top framework 16 is respectively arranged with the eccentric rod 52 of tabular, 52, 52, these eccentric rods are in main shaft part 30 radially, and in the direction different relative to the eccentric direction of main shaft part 30 from eccentric axial portion 32 (here for the top in Fig. 5 and Fig. 6, and be the direction of the phase contrast relative to the above-mentioned eccentric direction of eccentric axial portion 32 with 90 °) on stretch out in the same direction.
And, the pin 54 at the thin footpath pole shape projected upwards with the axially in parallel side of main shaft part 30 is integrally provided to the end portion stretching out on direction of this eccentric rod 52.That is, pin 54 is parallel from main shaft part 30 and be eccentrically formed in the circumferential position different relative to the circumferential position of such main shaft part 30 with eccentric axial portion 32 relative to main shaft part 30.And, in the present embodiment, as it is shown in figure 5, from the end on observation of main shaft part 30, eccentric axial portion 32 has angle, θ (here for 90 °) and different from pin 54 relative to the eccentric direction of main shaft part 30 relative to the eccentric direction of main shaft part 30.Herein, the central shaft P of main shaft part 30 and the central shaft R of pin 54 and axle direction at a right angle on distance Y become the offset Y of pin 54, such offset Y is configured to bigger than the offset X of the eccentric axial portion 32 addressed before this.
In addition, being clear that from Fig. 2 and Fig. 6, pin 54,54,54 arranges and is positioned at the one end position in the outer part than crank axle 34,34,34 (main shaft part 30,30,30) for the end on its projected direction.
Further, as it is shown in figure 5, the stop as the second connecting rod of long plate shape departs from bar 56 (hereinafter referred to as departing from bar 56) is respectively arranged in the end on the projected direction of these pins 54,54,54.Such disengaging bar 56 respectively via sleeve 58,58,58 relative to pin 54,54,54 can install in the way of rotating.So, many crank axles 34,34,34 are linked by disengaging bar 56 via eccentric rod 52 and pin 54 at its one end respectively.
In addition, in the present embodiment, as shown in Figure 2, central authorities crank axle 34 be assembled with clutch mechanism 60 integratedly from the other end (end of the upside Fig. 2) that top framework 16 extends towards outside, and via mechanisms such as not shown ball bearings, flywheel 62 is supported as rotating.So, in the forcing press 10 of present embodiment, it is set to a crank axle in many crank axles 34,34, the 34 i.e. crank axle 34 of central authorities receive the constant velocity rotary motion of flywheel 62 via clutch mechanism 60 and the crank axle 34 (hereinafter also referred to driving crank axle 34) that is driven in rotation.On the other hand, the crank axle 34 (hereinafter also referred to driven crank axle 34) being set to be subject to the rotary driving force of such driving crank axle 34 by the crank axle 34,34 of both sides and rotate.
And, in the forcing press 10 of above-mentioned such structure, input is mainly transferred to driven crank axle 34,34 by transmission lever 48,48 to the rotary driving force of driving crank axle 34, drives thus make these many crank axles 34,34,34 rotate when being mutually in step.
But, in Fig. 1 to Fig. 6, the duty inscribed when illustrating on-stream a certain of forcing press 10, herein, it is clear that according to Fig. 3 and Fig. 4, between the adjacent crank axle 34,34 linked by transmission lever 48, the central shaft P of each main shaft part 30 is all generally aligned in the same plane (face that extend along the direction vertical with paper, that represented by virtual line L) and above and is positioned on the centrage of transmission lever 48 with the central shaft Q of the eccentric axial portion 32 being provided with transmission lever 48.
In this state, make it rotate to the clockwise direction (with reference to thin-line arrow in figure) in Fig. 3 and Fig. 4 even if such as driving crank axle 34 being driven, the driven crank axle 34 linked by transmission lever 48 also be able to temporarily clockwise and both direction counterclockwise rotate, therefore the direction of rotation of driven crank axle 34 is not uniquely identified.That is, in the transmission mechanism of the rotary driving force based on transmission lever 48, driven crank axle 34 is positioned at stop.
On the other hand, mutually in the same time under each crank axle 34, 34, 34 and depart from bar 56 linking portion in, as shown in Figure 5, pin 54 is different with angle, θ respectively relative to the eccentric direction of main shaft part 30 from eccentric axial portion 32 relative to the eccentric direction of the main shaft part 30 of crank axle 34, in other words, depart from bar 56 different with θ relative to the rotatable phase of the installation portion of crank axle 34 (eccentric axial portion 32) from transmission lever 48 relative to the rotatable phase of the installation portion of crank axle 34 (pin 54), therefore, utilize this disengaging bar 56 to driven crank axle 34, 34 apply to make its power rotated towards the direction identical with driving crank axle 34.
And, with so from the power of disengaging bar 56 applying for opportunity so that driven crank axle 34,34 departs from from the stop of the transmission mechanism of the rotary driving force based on transmission lever 48,48.So, by transmission lever 48,48 and the synergism departing from bar 56, rotated the driving crank axle 34 of driving relative to by the direction of rotation towards regulation, when synchronizing and towards same direction of rotation, driven crank axle 34,34 is rotated driving.
Further, Fig. 7 to Fig. 9 pass the imperial examinations at the provincial level be illustrated crank axle 34,34,34 rotate in driving another time the state inscribed, slide block 24 be in the state of lower dead center.Herein, as it is shown in fig. 7, in order to make the driven crank axle 34 in left side rotate, the eccentric axial portion 32 of the driven crank axle 34 in left side is played a role by driving crank axle 34 via transmission lever 48 in the way of promoting to the left.Then, as its counteracting force, driving crank axle 34 is subject to the right the power of (being illustrated Fig. 7) by hollow arrow from transmission lever 48.
On the other hand, as shown in Figure 8, in order to make the driven crank axle 34 on right side rotate, the eccentric axial portion 32 of the driven crank axle 34 on right side is played a role by driving crank axle 34 via transmission lever 48 in the way of drawing to the left.Then, as its counteracting force, driving crank axle 34 is subject to the right the power of (being illustrated Fig. 8) by hollow arrow from transmission lever 48.So, as it is shown in figure 9, when rotating driving, driving crank axle 34 is subject to the power that size is roughly the same and direction is identical at the position of the both sides clipping connecting rod 38.
It is clear that from the description above, in the present embodiment, relative to many crank axles 34, 34, 34 respective eccentric axial portion 32 and be separately installed with the transmission lever 48 as the first connecting rod, 48, on the other hand, at many crank axles 34, 34, the one end of 34, via eccentric rod 52, 52, 52 and relative to the pin 54 arranged in the circumferential position different relative to the circumferential position of main shaft part 30 from eccentric axial portion 32, 54, 54 and be separately installed with the disengaging bar 56 as the second connecting rod, therefore, by these transmission levers 48, 48 and depart from bar 56 mating reaction, and the rotary driving force of input to driving crank axle 34 is transferred to other crank axle 34 swimmingly, 34.
Namely, owing to the rotation relative to driving crank axle 34 drives, the phase place of the installation portion (eccentric axial portion 32) of transmission lever 48,48 is respectively different with the phase place of the installation portion (pin 54) departing from bar 56, therefore, in the transmission mechanism of the rotary driving force based on transmission lever 48,48, even if when driven crank axle 34,34 arrives stop, its direction of rotation is uniquely identified also by departing from bar 56.Overall accordingly, as forcing press 10, no longer there is stop when making many crank axles 34,34,34 synchronously rotate, so, between these many crank axles 34,34,34, it is possible to transmit rotary driving force swimmingly.
And, the forcing press 10 of present embodiment is the structure completely without geared parts, therefore, become and will not be subject to the big moment of inertia being had by such geared parts completely and the dysgenic structure caused, thus having the advantage that the startup Stopping Ability (response) that can advantageously improve forcing press 10, and desired punch process can be carried out with high manufacturing accuracy, can also effectively make the molding cycle of forcing press 10 realize high speed further.In a word, in forcing press 10, being formed with the structure that crank axle 34 directly makes connecting rod 38 drive, therefore, response is excellent, it is possible to be advantageously carried out the high speed of molding cycle.
Further, owing to not needing geared parts, therefore following features is also played: the structure of forcing press 10 entirety is simplified, and parts number of packages is also cut down, and the manufacturing cost of device reduces.
Additionally, the side being respectively arranged in two main shaft part 30,30 of crank axle 34 due to eccentric rod 52,52,52, the one end that is projected toward the outside from top framework 16, therefore also have a characteristic that in order to disengaging bar 56 is installed, it is not necessary to increase top framework 16 or even framework 18 is overall.Therefore, the distance between the main shaft part 30,30 (bearing 44,44) supported will not become big to top framework 16, thus having the advantage that it is easy to ensure that these main shaft part 30,30 concentricitys each other.
Further, owing to so utilizing top framework 16 with short interval (span), the main shaft part 30,30 of crank axle 34 to be supported, therefore, crank axle 34 has played intensity for deflection deformation effectively.Namely, in crank axle 34, for the eccentric axial portion 32 being formed between main shaft part 30,30 and be configured in top framework 16, big power (counteracting force) is had from transmission lever 48 effect, but such eccentric axial portion 32 is supported with short interval, hence it is advantageous to inhibit its deflection deformation.Additionally, its result, crank axle 34 can be made itself to realize lightweight (thin footpath), thus having the further advantage that the moment of inertia that can reduce crank axle 34 further, it is possible to realize response, the raising of synchronization accuracy and further high speed.
Further, the one end position in the outer part than crank axle 34 is laid respectively at for the end on the projected direction departing from the pin 54,54,54 that bar 56 is installed, therefore, it is possible to advantageously prevent from coming off the interference of bar 56 and each crank axle 34.
And, in order to the work piece of wider width is carried out punch process, even if when the rectangular shape that slide block 24 is long side direction length under overlooking, it also is able to many crank axles 34, 34, 34 so that they axially become the direction at a right angle relative to the long side direction of slide block 24 (namely, the short side direction of slide block 24) mode on the long side direction of slide block 24 separated from each other compartment of terrain configuration, thus, the main shaft part 30 of crank axle 34, 30 (bearings 44, 44) distance between will not become big, therefore have the advantage that it is easy to ensure that these main shaft part 30, 30 concentricitys each other, the manufacture of crank axle 34 itself becomes easy.
It addition, herein, pin 54 is set to bigger than the offset X of eccentric axial portion 32 relative to the offset Y of main shaft part 30.Namely, in the rotation of crank axle 34 drives, it is set to relatively become big relative to distance X by the distance Y of the central shaft P to the central shaft R of the pin 54 becoming application point from the main shaft part 30 becoming fulcrum, therefore, the power (load) putting on pin 54 and disengaging bar 56 is less than the power putting on transmission lever 48.Therefore, it is possible to will be disengaged from the thickness of bar 56 to be set to the parts thinner than the thickness of transmission lever 48, pin 54 and disengaging bar 56 can be set to thinner or thin footpath, so being capable of lightweight, and moment of inertia can be reduced.
And, in the present embodiment, it is provided with multiple transmission lever 48, utilize each of these multiple transmission levers 48,48 and respectively by connected to each other for the eccentric axial portion 32,32 of mutually adjacent crank axle 34,34, and in arranging the crank axle 34 (here for driving crank axle 34) for being clipped between 2 crank axles 34,34, multiple transmission levers 48,48 clip the position (large-diameter portion 32a) of the one end being linked with connecting rod 38 and axially alternately arranging in eccentric axial portion 32 respectively.Therefore, in driving crank axle 34, do not produce deviation from what transmission lever 48,48 acted in the axial direction with the power axle direction at a right angle, thus, make the central shaft P of such crank axle 34 power tilted to play a role.So, from crank axle 34, bearing 44,44 will not be acted on unexpected power, prevent the flexure (inclination of axle) of this crank axle 34 further, and the concentricity of main shaft 30,30 is guaranteed, it is as a result, it is possible to make crank axle 34 rotate more swimmingly.
It follows that Figure 10 illustrates other embodiment of the forcing press with structure involved in the present invention in the way of the sectional view corresponding with Fig. 2.Additionally, in the forcing press 64 shown in Figure 10, the part for the structure identical with embodiment before this marks identical accompanying drawing labelling and omits detailed description.
That is, in the forcing press 64 shown in such Figure 10, the structure that many crank axles 34,34,34 are linked is formed as by 1 transmission lever 48.Even if under this form, by transmission lever 48 and the synergism departing from bar 56, it is also possible to the rotary driving force of input to driving crank axle 34 is transferred to driven crank axle 34,34 swimmingly.
It addition, for such forcing press 64, in the respective eccentric axial portion 32 of crank axle 34,34,34, making the eccentric direction of large-diameter portion 32a and the eccentric direction of minor diameter part 32b, 32b is symmetry.That is, drive relative to the rotation of crank axle 34, the phase 180 ° of the phase place of large-diameter portion 32a and minor diameter part 32b, 32b.Have a characteristic that under this form and adopt the structure that minor diameter part 32b, 32b of being not connected with transmission lever 48 are linked known dynamic balancing machine (dynamicbalance) (not shown), it is possible to offset the reciprocal vibration driven with slide block 24 such that it is able to the vibration of machine 64 entirety that eases off the pressure.
Although above the representational embodiment of the present invention having been carried out detailed narration, but it only having illustrated, it should be understood that, it is impossible to by concrete describe relevant to this embodiment, the present invention is carried out any determinate explanation.
Such as, pin 54 is at all not limited to the position of illustration relative to the circumferential position of eccentric axial portion 32.That is, as long as eccentric axial portion 32 being set to angle except 0 ° and 180 ° except with pin 54 relative to the eccentric direction angulation θ of main shaft part 30 relative to the eccentric direction of main shaft part 30.Herein, why 0 ° and 180 ° is foreclosed, if being because being set to such angle, θ 0 ° or 180 °, then the installation portion (eccentric axial portion 32) of transmission lever 48 and the installation portion (pin 54) departing from bar 56 can arrive stop simultaneously, driven crank axle 34 can cannot obtain transmission lever 48 and the synergism departing from bar 56, thus cannot be made advantageously to depart from stop.Furthermore it is preferred that such angle, θ is set to 90 °, thus it is preferred to, make the phase place of pin 54 differ 90 ° relative to the phase place of eccentric axial portion 32 in the direction of rotation of crank axle 34.
It addition, the radical of crank axle 34 is also at all not limited to the radical illustrated, as long as possessing many (more than 2) crank axles 34.Herein, citing illustrates the form of the forcing press 66 with 4 crank axles 34,34,34,34 in fig. 11.And, herein it is also preferred that many transmission lever 48,48,48 axially alternately arranging at crank axle 34.Thus, except driving crank axle 34, even if in the driven crank axle 34 (the 2nd crank axle 34 here for from left side) being disposed between 2 crank axles 34,34, it is also possible to advantageously enjoy effect that address before this, that prevent axle from twisting and warping.
Further, eccentric rod 52 stretch out direction so that form is also at all not limited to aforesaid way, for instance even if eccentric rod 52 is set to middle part bending L-shaped shape etc., without produce any impact.In a word, as long as the circumferential position of the pin 54 being integrally provided to this eccentric rod 52 is set to the position different from the circumferential position of eccentric axial portion 32.
Additionally, as being used for the mechanism of rotary driving force input to driving crank axle 34, it is possible to suitably adopt known various mechanism.It addition, the difference according to structure, additionally it is possible to this mechanism is arranged at disengaging bar 56 end of the same side of crank axle 34.
Other is no longer illustrated one by one, but, the knowledge based on those skilled in the art can implement the present invention in the way of being applied with various change, amendment, improvement etc., and, as long as without departing from the purport of the present invention, such embodiment broadly falls into scope of the invention certainly.
Claims (8)
1. a forcing press, many crank axles of this forcing press are respectively provided with: two main shaft part positioned in coaxial fashion；And eccentric axial portion, this eccentric axial portion configures prejudicially relative to described main shaft part between said two main shaft part, described many crank axles separate the interval of regulation and sentencing in the two main shaft part by its state being axially parallel to each other respectively and can be bearing in the way of rotating in framework, the displacement of the described eccentric axial portion formed by the rotation based on the described crank axle being center of rotation with the central shaft of described main shaft part, the slide block that side, the other end with connecting rod is linked back and forth drives, wherein, the one end of described connecting rod links with described eccentric axial portion
Described forcing press is characterised by,
For the rotary driving force of a crank axle in input to described many crank axles is transferred to other crank axle and makes the first connecting rod that described many crank axles rotate with being mutually in step be installed on each described eccentric axial portion,
On the other hand, side's main shaft part in the said two main shaft part of described many crank axles, from the end that described framework is projected toward the outside, it is respectively arranged with the eccentric rod extended along the direction axially at a right angle with described main shaft part, and, these eccentric rods are respectively arranged with pin, this pin highlights along the axially in parallel direction with this main shaft part in the circumferential position different relative to the circumferential position of described main shaft part from described eccentric axial portion, and the end on its projected direction is positioned at outside compared with the one end of this crank axle, and, end on the projected direction of these pins is separately installed with the second connecting rod, synergism by described first connecting rod and the second connecting rod, described rotary driving force is transferred to swimmingly other crank axle described.
2. forcing press according to claim 1, it is characterised in that
In the rotation of the described crank axle being center of rotation with the central shaft of described main shaft part, the phase place of described eccentric axial portion are set to 90 ° with the difference of the phase place of described pin.
3. forcing press according to claim 1 and 2, it is characterised in that
The central shaft of described pin is set to bigger relative to the offset of the central shaft of this main shaft part than the central shaft of described eccentric axial portion relative to the offset of the central shaft of described main shaft part.
4. forcing press according to claim 3, it is characterised in that
Described second connecting rod is the parts thinner than described first connecting rod wall.
5. forcing press according to any one of claim 1 to 4, it is characterised in that
Described first connecting rod is provided with many, it is utilized respectively these many first connecting rods by connected to each other for the described eccentric axial portion of mutually adjacent described crank axle, further, these many first connecting rods are to clip the position of the one end being linked with described connecting rod and axially alternately arranging in this eccentric axial portion respectively.
6. forcing press according to any one of claim 1 to 4, it is characterised in that
Being equipped with other crank axle described respectively in the both sides of a crank axle for the input of described rotary driving force, other crank axle described is subject to the rotary driving force of this crank axle and rotates,
Be utilized respectively described first connecting rod and by mutually adjacent, connected to each other with the described eccentric axial portion of other crank axle described for the described eccentric axial portion of a crank axle of described rotary driving force input,
Further, it is installed on two described first connecting rods of a crank axle for the input of described rotary driving force, clips the position of the one end being linked with described connecting rod and axially alternately arranging in this eccentric axial portion respectively.
7. forcing press according to any one of claim 1 to 6, it is characterised in that
Described eccentric axial portion is configured to: the minor diameter part that large-diameter portion is thinner than the diameter of this large-diameter portion with diameter is formed coaxially, and the one end of described connecting rod is assembled in this large-diameter portion, and on the other hand, described first connecting rod is installed on this minor diameter part.
8. forcing press according to any one of claim 1 to 7, it is characterised in that
Described slide block under overlooking in the rectangular shape of long side direction length, described many crank axles axially become the direction at a right angle relative to the long side direction of this slide block, described many crank axles configure spaced apart from each other on the long side direction of this slide block.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015004765A JP5767416B1 (en) | 2015-01-14 | 2015-01-14 | Press machine |
| JP2015-004765 | 2015-01-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105774010A true CN105774010A (en) | 2016-07-20 |
| CN105774010B CN105774010B (en) | 2017-11-24 |
Family
ID=53888057
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510845854.4A Active CN105774010B (en) | 2015-01-14 | 2015-11-26 | Forcing press |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP3045302B8 (en) |
| JP (1) | JP5767416B1 (en) |
| CN (1) | CN105774010B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106976261A (en) * | 2017-05-05 | 2017-07-25 | 桐乡市凯盛精密机械有限公司 | A kind of forcing press |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113664096B (en) * | 2020-05-15 | 2023-07-14 | 久恩企业股份有限公司 | Feed cam stop block of screen punching machine |
| JP7461653B2 (en) | 2021-06-08 | 2024-04-04 | 株式会社山田ドビー | Press Machine |
| AT525869B1 (en) * | 2022-10-03 | 2023-09-15 | Andritz Tech & Asset Man Gmbh | PRESS WITH AT LEAST TWO ECCENTRIC SHAFTS |
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| JPS6447904U (en) * | 1987-09-18 | 1989-03-24 | ||
| CN1121449A (en) * | 1994-07-25 | 1996-05-01 | 里弗诺伊斯研究发展公司 | Modular die transfer system |
| JPH09155595A (en) * | 1995-12-05 | 1997-06-17 | Yamada Dobby Co Ltd | Press machine |
| CN1454771A (en) * | 2002-05-01 | 2003-11-12 | 村田机械株式会社 | Motor-driven lever type press |
| CN101209596A (en) * | 2006-12-27 | 2008-07-02 | 株式会社山田多比 | Punch machines |
| CN101927575A (en) * | 2009-06-22 | 2010-12-29 | 株式会社山田多比 | Forcing press |
| CN102632637A (en) * | 2012-04-11 | 2012-08-15 | 济南二机床集团有限公司 | Press machine driven by servo motor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS5514477Y2 (en) | 1975-10-15 | 1980-04-02 | ||
| JPS63235098A (en) * | 1987-03-23 | 1988-09-30 | Ishikawajima Harima Heavy Ind Co Ltd | Device for driving press |
| DE102009035214A1 (en) * | 2009-07-29 | 2011-02-24 | Dieffenbacher Gmbh + Co. Kg | Press with a directly driven crank mechanism |
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2015
- 2015-01-14 JP JP2015004765A patent/JP5767416B1/en active Active
- 2015-10-06 EP EP15002851.2A patent/EP3045302B8/en active Active
- 2015-11-26 CN CN201510845854.4A patent/CN105774010B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS6447904U (en) * | 1987-09-18 | 1989-03-24 | ||
| CN1121449A (en) * | 1994-07-25 | 1996-05-01 | 里弗诺伊斯研究发展公司 | Modular die transfer system |
| JPH09155595A (en) * | 1995-12-05 | 1997-06-17 | Yamada Dobby Co Ltd | Press machine |
| CN1454771A (en) * | 2002-05-01 | 2003-11-12 | 村田机械株式会社 | Motor-driven lever type press |
| CN101209596A (en) * | 2006-12-27 | 2008-07-02 | 株式会社山田多比 | Punch machines |
| CN101927575A (en) * | 2009-06-22 | 2010-12-29 | 株式会社山田多比 | Forcing press |
| CN102632637A (en) * | 2012-04-11 | 2012-08-15 | 济南二机床集团有限公司 | Press machine driven by servo motor |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106976261A (en) * | 2017-05-05 | 2017-07-25 | 桐乡市凯盛精密机械有限公司 | A kind of forcing press |
Also Published As
| Publication number | Publication date |
|---|---|
| EP3045302A1 (en) | 2016-07-20 |
| JP2016129899A (en) | 2016-07-21 |
| JP5767416B1 (en) | 2015-08-19 |
| CN105774010B (en) | 2017-11-24 |
| EP3045302B1 (en) | 2017-06-07 |
| EP3045302B8 (en) | 2017-08-16 |
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