EP1223027A2 - Power transmission for press machine - Google Patents
Power transmission for press machine Download PDFInfo
- Publication number
- EP1223027A2 EP1223027A2 EP01128165A EP01128165A EP1223027A2 EP 1223027 A2 EP1223027 A2 EP 1223027A2 EP 01128165 A EP01128165 A EP 01128165A EP 01128165 A EP01128165 A EP 01128165A EP 1223027 A2 EP1223027 A2 EP 1223027A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pivotally connected
- linking pieces
- slide
- linking
- connection point
- 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.)
- Granted
Links
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/0029—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height
- B30B15/0035—Details of, or accessories for, presses; Auxiliary measures in connection with pressing means for adjusting the space between the press slide and the press table, i.e. the shut height using an adjustable connection between the press drive means and the press slide
-
- 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
- B30B1/10—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 toggle mechanism
- B30B1/14—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 toggle mechanism operated by cams, eccentrics, or cranks
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/0064—Counterbalancing means for movable press elements
Abstract
Description
- The present invention relates to a power transmission for a press machine provided with a slide and a balancing weight vertically spaced apart from each other.
- There is a press machine provided with a slide and a balancing weight employing a toggle mechanism for a power transmission (e.g., Japanese Patent Appln. Public Disclosure No. 7-132400). This press machine uses two sets of linkages to move the slide and the balancing weight as well as a position adjusting mechanism to make a stroke length of the slide variable.
- This press machine, however, has both linkages connected by a connector and uses long linking pieces pivotally supported on a frame, so that its structure is complicated.
- An object of the present invention lies in simplifying the structure of the press machine having a balancing weight and capable of adjusting a stroke length of the slide.
- The press machine according to the present invention comprises: a first and a second sliders disposed on a frame at a vertical interval from each other so as to move vertically; a connection for connecting the first slider with an eccentric portion of a crankshaft; a pair of first linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with the first and the second sliders; a pair of second linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with a slide and a balancing weight; and a position adjusting mechanism for adjusting the height position of the second slider in the vertical direction, one of the first linking pieces extending to the front end side more forward than a pivot connection point with the other to be pivotally connected with the second linking pieces.
- Rotation of the crankshaft is transmitted to both first linking pieces by the connection to bend and extend the first linking pieces. The bending and extending motion of the first linking pieces is transmitted to both second linking pieces by one of the first linking pieces to bend and extend the second linking pieces. By this, the slide and the balancing weight connected with the second linking pieces are reciprocated vertically at a phase difference of 180° with the bending and extending motion of the second linking pieces. As a result, unbalanced force attributable to the vertical motion of the slide and the balancing weight is offset.
- When the height position of the second slider in the vertical direction is changed by the position adjusting mechanism, the angle of bend of the linking pieces of both linkages is changed, thereby changing the stroke length of the slide.
- If one of the first linking pieces is extended to the front end side more forward than the pivot connection point with the other to be pivotally connected with the second linking piece, the linking piece pivotally connected with the frame can be dispensed with, which also dispenses with the pivot for the linking piece as well as the bracket, thereby simplifying the structure.
- The pivot connection point of both second linking pieces may be a floating connection point not supported on the frame, and the slide as well as the balancing weight may be disposed on the frame immovably in the horizontal direction, and further, one of the second linking pieces may be pivotally connected with a plunger extending from the slide.
- In a preferred embodiment, the position adjusting mechanism includes: a second slider disposed on the frame so as to move vertically; a disk-shaped rotor disposed on the frame so as to rotate about an axis extending in one direction and not to move in the one direction; and a rotating mechanism for rotating the rotor. Either one of the second slider and the rotor has a female screw hole, while the other of the second slider and the rotor has a male screw portion screwed into the female screw hole.
- The distance from the pivot connection point of both first linking pieces to the pivot connection point with the pivot connection point of the one of the second linking pieces and the slide can be equal to the distance from the pivot connection point of both first linking pieces to the pivot connection point with the other of the second linking pieces and the second slider. By doing so, the pivot connection point of both second linking pieces is reciprocated horizontally with mutual bending and extending motion of both first linking pieces, whereby the pivot connection point of the one of the second linking pieces with the slide and the pivot connection point of the other of the second linking pieces with the balancing weight is reciprocated perpendicularly by the same amount in the opposite direction to each other, and the vertical movements of the slide and the balancing weight are surely balanced.
- The press machine further comprises: a pair of third linking pieces pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with the first and second sliders; a pair of fourth linking pieces pivotally connected with each other so as to bend and such that one and the other are respectively pivotally connected with the slide and the balancing weight. Either one of the third linking pieces can be extended to the front end side more forward than the pivot connection point with the other to be pivotally connected with the fourth linking pieces. By doing so, the slide and the balancing weight are connected with the linkage at two positions, thereby stabilizing the movements of the slide and the balancing weight.
- The frame preferably has a guide portion for regulating reciprocation of the balancing weight to the vertical direction. This also makes reciprocation of the balancing weight to the vertical direction, thereby stabilizing the vertical motion of the balancing weight.
- Fig. 1 is a partially sectioned front elevation showing one embodiment of the press machine according to the present invention.
- Fig. 2 is a partially enlarged sectional view of the power transmission and the balancer of the press machine in Fig. 1.
- Fig. 3 is an enlarged sectional view taken along the line 3-3 in Fig. 1.
- Fig. 4 is an enlarged sectional view taken along the line 4-4 in Fig. 1.
- Fig. 5 is an enlarged sectional view taken along the line 5-5 in Fig. 1.
- Fig. 6 is an enlarged sectional view taken along the line 6-6 in Fig. 1.
- Referring to Figs. 1 - 6, the
press machine 10 comprises alower frame 12 mounting a drag and anupper frame 14 supported on thelower frame 12. Acrankshaft 16 is supported on theupper frame 14 so as to rotate about a horizontally extending axis and receives rotation of aflywheel 18 shown in Fig. 3. A so-calledslide 20 supporting a cope is assembled into the lower end of a pair ofplungers 22 extending through the lower end portion of theupper frame 14 so as to move vertically. - Both
plungers 22 are extended upward in parallel from both end portions of theslide 20 and are reciprocated vertically by apower transmission 30 which converts rotation of thecrankshaft 16 into vertical reciprocation. Thereby, theslide 20 is vertically reciprocated. - The
power transmission 30 comprises: aconnection 32 connected with thecrankshaft 16; a pair ofsliders 34 disposed on theupper frame 14 so as to reciprocate vertically and pivotally connected with theconnection 32, i.e., so as to move pivotally; a pair oflinkages 36 which are bended and extended synchronously with each other, following the reciprocation of theslider 34; a pair oflinkages 38 which are made to individually correspond to thelinkages 36 to be bended and extended, following the bending and extending motion of thecorresponding linkages 36; a pair ofsliders 40 disposed on theupper frame 14 so as to displace vertically and pivotally connected with bothlinkages 36; and aposition adjusting mechanism 42 for adjusting the position of thesliders 40 in the vertical direction. - The
connection 32 is connected with an eccentric portion of thecrankshaft 16 and is reciprocated vertically with rotation of thecrankshaft 16. Thesliders guide portion 44 formed in theupper frame 14 so as to move vertically. Bothsliders 34 are reciprocated vertically, following the reciprocation of theconnection 32. Thesliders 40 are not reciprocated vertically by bending and extending motion of bothlinkages 36. - Each
linkage 36 is provided with a pair of linkingpieces pieces linkage 36 are bendably connected with each other by apivot 46 at the central portion of the linkingpiece 36a and the upper end portion of the linkingpiece 36b. One linkingpiece 36a extends to the more downward side than the pivot connection point of the linkingpieces linkage 38 at the lower end portion. - One of the linking
pieces 36a of bothlinkages 36 is pivotally connected with theconnection 32 and theslider 34 at the upper end portion by acommon pivot 48. The other of the linkingpieces 36b of bothlinkages 36 is pivotally connected with theslider 40 at the lower end portion by acommon pivot 50. - In the illustrated example, the
pivots crankshaft 16, but it is not always necessary to arrange thepivots - Also, in the illustrated example, the linking
piece 36a of thelinkage 36 is directly connected with theconnection 32 and theslider 34, but it is possible to pivotally connect theconnection 32 and theslider 34, and to connect the linkingpiece 36a of thelinkage 36 with only one of theconnection 32 and theslider 34. - Each
linkage 38 is provided with a pair of linkingpieces pieces piece 38a and the upper end portion of the linkingpiece 38b by thepivot 54. - Both linking
pieces 38a are connected at their upper end portion with a balancingweight 56 disposed on theupper frame 14 by apivot 58 so as to move vertically. Each linkingpiece 38b is pivotally connected at its lower end portion with theplunger 22 by apivot 60. - Each
linkage 38 is connected with the lower end portion of the linkingpiece 36a of thecorresponding linkage 36 at the pivot connection point of both linkingpieces pivot 54. - The balancing
weight 56 is disposed in aguide portion 62 formed on theupper frame 14 so as to move vertically and is positioned above thelinkages crankshaft 16, thereby balancing unbalanced force attributable to vertical motion of theslide 20. - The
position adjusting mechanism 42 is provided with: a forkedbracket 70 pivotally connected with both linkingpieces 36b and bothsliders 40 by thepivot 50; amale screw 72 extending downward from thebracket 70; aworm wheel 74 screwed into themale screw 72; and aworm screw 76 meshed with theworm wheel 74. In place of employing thebracket 70, themale screw 72 may be pivotally connected with both linkingpieces 36b and bothsliders 40. - The
male screw 72 is connected with thebracket 70 so as not to rotate about theaxis 52. Theworm wheel 74 is supported onsupport portions 78, 80 of theupper frame 14 so as to rotate about theaxis 52 and not to move vertically. The axis portion of theworm screw 76 rotatably extends through theupper frame 14 and has asprocket 82 at an end portion (see Fig. 5). Thesprocket 82 is rotated by a rotating mechanism not shown such as an electric motor. - When the
sprocket 82 is rotated, theworm screw 76 is rotated, theworm wheel 74 meshed with theworm screw 76 is rotated, themale screw 72 screwed into theworm wheel 74 is moved upward or downward, and finally theslider 40 is moved upward or downward. - In the
press machine 10, thesliders 34 are reciprocated in the same direction with vertical reciprocation of theconnection 32, following rotation of thecrankshaft 16. Theslider 40, however, is not moved unless theworm wheel 74 is rotated. - In view of the above, the
pivot 48 acts as a movable side fulcrum of thelinkage 36, and thepivot 50 acts as a fixed side fulcrum of thelinkage 36. Further, since the linkingpieces weight 56 and theplunger 22, thepivots pivot 54, act as floating fulcrums not supported on theframe 14. - The
pivots crankshaft 16. Therefore, pivotal motion of members mutually connected by each pivot or members supported by each pivot is a motion about a horizontal axis. - When rotation of the
flywheel 18 is transmitted to thecrankshaft 16, theconnection 32 and theslider 34 are reciprocated vertically with the rotation of the crankshaft, so that bothlinkages 36 are bended and extended synchronously. By this, bothlinkages 38 are bended synchronously, as a result of which theslide 20 and the balancingweight 56 are synchronously reciprocated in the opposite directions. - The axis of the
pivot 46 is at the midpoint between the axes of thepivots linking piece 36a, and the distance from the axis of thepivot 46 to the axis of thepivot 48 is the same as the distance between the axes of the linkingpieces 44 at both ends of the linkingpiece 44. Consequently, when theslider 34 is reciprocated, thepivot 54 is horizontally reciprocated, and thepivots pieces pivot 54 are synchronously reciprocated upward and downward by the same amount in the opposite directions to each other. Therefore, theslide 20 and the balancingweight 56 are simultaneously reciprocated upward and downward by the same amount in the opposite directions to each other, thereby balancing the vertical movement of theslide 20 and the balancingweight 56. - Reciprocation of the
slide 20 is restricted to the vertical direction because reciprocation of theplungers 22 is regulated to the vertical direction by theframe 14. Reciprocation of the balancingweight 56 is restricted to vertical reciprocation by theguide portion 62, - Consequently, though the
pivots frame 14, horizontal displacement of theslide 20 and the balancingweight 56 is surely prevented, horizontal oscillation of the press machine attributable to the reciprocal motion of theslide 20 and the balancingweight 56 is prevented, and vertical motion of theslide 20 and the balancingweight 56 is stabilized. - Reciprocation of the
slider 34 is regulated to the vertical direction byguide portions 44. Consequently, bending and extending motion of bothlinkages slide 20 and the balancingweight 56. - Independently of rotation of the
crankshaft 16, when theslider 40 is moved upward by theposition adjusting mechanism 42, an angle of bend of eachlinkage 36 becomes small, thereby making an angle of bend of eachlinkage 38 great, so that theslide 20 is moved downward. On the other hand, when theslider 40 is moved downward, the angle of bend of eachlinkage 36 becomes great, thereby making the angle of bend of eachlinkage 38 small and moving theslide 20 upward. - When the
slider 40 is moved upward or downward, the position of theslider 34 in the vertical direction is not varied, and, therefore, the angle of bend of thelinkage 36 is varied, but the range of bending and extending does not translate in the vertical direction. Consequently, by rotating thesprocket 82, the position of a bottom dead center and a stroke length of theslide 20 can be adjusted. - The position of the bottom dead center of the
slide 20 may be adjusted by detecting it by an arbitrary detector, comparing the detected value with a predetermined reference value, and rotating thesprocket 82 so that the detected value can become the reference value. The stroke length of theslide 20 can be set by rotating thesprocket 82 beforehand by a predetermined amount. - If the above-mentioned
position adjusting mechanism 42 is used, an amount of movement of theslider 40 is very small with respect to the amount of rotation of theworm screw 76, both the position of the bottom dead center and the stroke length can be adjusted minutely and accurately. It is, however, possible to use another position adjusting mechanism. - If four
linkages slide 20 and the balancingweight 56 is stabilized. Particularly, by disposing bothlinkages 36 symmetrically with respect to theaxis 52, disposing thelinkages 38 on both sides thereof symmetrically with respect to theaxis 52, disposing the balancingweight 56 above thecrankshaft 16 and thelinkages axis 52, and connecting the undersides of both horizontal end portions of the balancing weight with the linkages, reciprocation of theslide 20 and the balancingweight 56 is stabilized. - In order to make reciprocation of the
slide 20 and the balancingweight 56 more stabilized, it is particularly preferable to arrange one of the linkingpieces pieces axis 52 and to dispose the balancingweight 56 symmetrically with respect to theaxis 52. However, it is possible, for example, to employ only one set oflinkages - The present invention is not limited to the above embodiments. The present invention can be variously modified without departing from its gist.
Claims (7)
- A power transmission for a press machine for transmitting rotation of a crankshaft (16) to a slide (20) and a balancing weight (56) which are vertically spaced apart and moving said slide and said balancing weight vertically at a phase difference of 180°, comprising:a first and a second sliders (34, 40) vertically spaced apart from each other and disposed on a frame (14) so as to move vertically;a connection (32) connecting said first slider with an eccentric portion of said crankshaft;a pair of first linking pieces (36a, 36b) pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with said first and second sliders;a pair of second linking pieces (38a, 38b) pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with said slide and said balancing weight; anda position adjusting mechanism (42) for adjusting the height positions of said second sliders in the vertical direction;
- A power transmission as defined in claim 1, wherein the pivot connection point of both second linking pieces (38a, 38b) is a floating connection point not supported on said frame (14).
- A power transmission as defined in claim 1 or 2, wherein said slide (20) and said balancing weight (56) are disposed on said frame (14) so as not to move horizontally.
- A power transmission as defined in any one of claims 1 through 3, wherein one of said second linking pieces (38a, 38b) is pivotally connected with a plunger (22) extending from said slide (20).
- A power transmission as defined in any one of claims 1 through 4, wherein said position adjusting mechanism (42) includes: a disk-shaped rotor (74) disposed on said frame (14) so as to rotate about an axis extending in one direction and not to move in said one direction; and a rotating mechanism for rotating said rotor; wherein either said second sliders (40) or said rotor (74) has a female screw hole, and the other of said second sliders and said rotor has a male screw portion screwed into said female screw portion.
- A power transmission as defined in claim 5, wherein the distance from the pivot connection point of both first linking pieces (36a, 36b) to the pivot connection point of said one of the second linking pieces (38a, 38b) and the slide (20) is equal to the distance from the pivot connection point of both first linking pieces to the pivot connection point of said second linking pieces and said second slider (40).
- A power transmission as defined in any one of claims 1 through 6, further comprising: a pair of third linking pieces (36a, 36b) pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with said first and second sliders (34, 40); and
a pair of fourth linking pieces (38a, 38b) pivotally connected with each other so as to bend, of which one and the other are respectively pivotally connected with said slide (20) and said balancing weight (50);
wherein either one of said third linking pieces is extended to the front end side more forward than the pivot connection point with the other to be pivotally connected with said fourth linking pieces.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001003266 | 2001-01-11 | ||
JP2001003266A JP2002205197A (en) | 2001-01-11 | 2001-01-11 | Power transmission of press |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1223027A2 true EP1223027A2 (en) | 2002-07-17 |
EP1223027A3 EP1223027A3 (en) | 2003-01-15 |
EP1223027B1 EP1223027B1 (en) | 2007-01-10 |
Family
ID=18871630
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20010128165 Expired - Lifetime EP1223027B1 (en) | 2001-01-11 | 2001-11-27 | Power transmission for press machine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1223027B1 (en) |
JP (1) | JP2002205197A (en) |
DE (1) | DE60125904T2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1650015A1 (en) * | 2004-10-25 | 2006-04-26 | Haulick + Roos GmbH | Press, punch press or forming apparatus |
US10850466B2 (en) | 2015-06-15 | 2020-12-01 | Aida Engineering Ltd. | Dynamic balance device for press machine |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4313816B2 (en) * | 2006-12-27 | 2009-08-12 | 株式会社山田ドビー | Press machine |
CN102555254B (en) * | 2012-02-29 | 2014-04-23 | 西安交通大学 | Main transmission mechanism for high-speed press |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4630516A (en) * | 1982-09-06 | 1986-12-23 | Mabu-Pressen Maschinenfabrik Karl Burkard Kg | Eccentric press |
US4920782A (en) * | 1987-02-03 | 1990-05-01 | Bruderer Ag | Press drive |
JPH07132400A (en) * | 1993-11-11 | 1995-05-23 | Yamada Dobby Co Ltd | Press |
US5687645A (en) * | 1995-06-19 | 1997-11-18 | Sankyo Seisakusho Co. | Mechanical pressing machine |
-
2001
- 2001-01-11 JP JP2001003266A patent/JP2002205197A/en active Pending
- 2001-11-27 DE DE2001625904 patent/DE60125904T2/en not_active Expired - Lifetime
- 2001-11-27 EP EP20010128165 patent/EP1223027B1/en not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4630516A (en) * | 1982-09-06 | 1986-12-23 | Mabu-Pressen Maschinenfabrik Karl Burkard Kg | Eccentric press |
US4920782A (en) * | 1987-02-03 | 1990-05-01 | Bruderer Ag | Press drive |
JPH07132400A (en) * | 1993-11-11 | 1995-05-23 | Yamada Dobby Co Ltd | Press |
US5687645A (en) * | 1995-06-19 | 1997-11-18 | Sankyo Seisakusho Co. | Mechanical pressing machine |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 1995, no. 08, 29 September 1995 (1995-09-29) & JP 07 132400 A (YAMADA DOBBY CO LTD), 23 May 1995 (1995-05-23) * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1650015A1 (en) * | 2004-10-25 | 2006-04-26 | Haulick + Roos GmbH | Press, punch press or forming apparatus |
US10850466B2 (en) | 2015-06-15 | 2020-12-01 | Aida Engineering Ltd. | Dynamic balance device for press machine |
Also Published As
Publication number | Publication date |
---|---|
EP1223027A3 (en) | 2003-01-15 |
DE60125904T2 (en) | 2007-07-05 |
JP2002205197A (en) | 2002-07-23 |
DE60125904D1 (en) | 2007-02-22 |
EP1223027B1 (en) | 2007-01-10 |
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