EP0546249A2 - Pressmaschine - Google Patents

Pressmaschine Download PDF

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Publication number
EP0546249A2
EP0546249A2 EP92111480A EP92111480A EP0546249A2 EP 0546249 A2 EP0546249 A2 EP 0546249A2 EP 92111480 A EP92111480 A EP 92111480A EP 92111480 A EP92111480 A EP 92111480A EP 0546249 A2 EP0546249 A2 EP 0546249A2
Authority
EP
European Patent Office
Prior art keywords
slide
slide unit
pressing machine
pads
con
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.)
Withdrawn
Application number
EP92111480A
Other languages
English (en)
French (fr)
Other versions
EP0546249A3 (en
Inventor
Tadayoshi Uehara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aida Engineering Ltd
Original Assignee
Aida Engineering Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from JP32541591A external-priority patent/JPH0757436B2/ja
Priority claimed from JP3325414A external-priority patent/JPH0790396B2/ja
Application filed by Aida Engineering Ltd filed Critical Aida Engineering Ltd
Publication of EP0546249A2 publication Critical patent/EP0546249A2/de
Publication of EP0546249A3 publication Critical patent/EP0546249A3/en
Withdrawn legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/02—Punching blanks or articles with or without obtaining scrap; Notching
    • B21D28/20—Applications of drives for reducing noise or wear
    • 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
    • B30B1/265—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 using a fluid connecting unit between drive shaft and press ram
    • 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
    • B30B15/0041—Control arrangements therefor

Definitions

  • the present invention relates to a pressing machine for working a material by causing a slide to move up and down with rotations of a crank shaft.
  • a pressing machine is constructed such that: a slide connected via a con'rod to a crank shaft is moved up and down with rotations of the crank shaft; and a material is worked by a top tool secured to the slide and a bottom tool secured to a bolster.
  • a slide guide is provided on a column for joining a bed to a crown. The slide makes the up-and-down motions while being guided by this slide guide.
  • a guide post is provided in a die unit composed of the upper and bottom tools. The top tool is guided by this guide post with respect to the bottom tool, thus making the vertical motions.
  • a plurality of die units are fitted to one slide.
  • the top tools exert adverse influences on each other.
  • the thrust load acts on the top tool, it follows that the top tool works the material with a core deviation from the bottom tool. The top and bottom tools undergo a large frictional force. This results in such a problem that a life-span of the die is reduced.
  • the material is simultaneously worked by the top and bottom tools on the respective working stages when the slide reaches a bottom dead center.
  • a molding load of the pressing machine increases. This also conducts to such a problem that vibrations and noises caused by the pressing machine augment.
  • the pressing machine requires a slide adjusting operation when the height dimension of the top or bottom tool varies at replacement of the die and also a slide adjusting device for effecting a bottom dead center compensating operation when the bottom dead center of the slide changes in the case of a thermal expanding deformation of the slide due to press working heat.
  • the pressing machine needs a breakthrough countermeasure device for reducing the vibrations and noises caused in the pressing machine when punching out the material with the top tool.
  • a pressing machine for working a material by a top tool secured to a slide connected via a con'rod to a crank shaft and by a bottom tool secured to a bolster
  • a pressing machine according to the present invention is constructed such that: the crank shaft is formed with a plurality of eccentric members with an angular phase difference; a plurality of slide members independently separated from each other are connected via the con'rods to these eccentric members; a pressing machine frame is mounted with slide horizontal position adjusting devices, so disposed as to confront these slide members in the horizontal direction, for adjusting the horizontal position of the slide unit; and a slide lifter for making the slide member ascendable and descendable with respect to the con'rod is provided between the slide member and the con'rod.
  • the slide horizontal position adjusting device is constructed of: position detecting sensors for detecting positions of the members of the slide unit in the two orthogonal horizontal directions; a plurality of pads attached to the frame of the pressing machine with slight gaps from the four perpendicular surfaces of the members of the slide unit which face in the two orthogonal horizontal directions, the pads causing pressures of supplied pressure oils to act on the perpendicular surfaces; and control valves, provided in a hydraulic circuit for supplying the pressure oil to the pads, for setting the slide unit in a proper horizontal position by regulating the supply of the pressure oils to the respective pads in accordance with the slide horizontal position detected by the position detecting sensors.
  • the slide lifter is constructed of: a hydraulic cylinder fixed to an upper end of the slide unit; a vertically movable pressure receiving member including a piston portion for sectioning an internal chamber of the hydraulic cylinder into an upper and lower chambers, the pressure receiving member having its upper part, protruded from the hydraulic cylinder, to which a lower part of the con'rod is connected; and changeover valves, provided in a connection circuit for connecting the upper and lower chambers, for flowing the pressure oil of the lower chamber into the upper chamber.
  • a pressing machine according to the present invention is provided with a single slide member and only the slide horizontal position adjusting device or only the slide lifter.
  • the respective slide members are connected via the con'rods to the crank shaft eccentric members with an angular phase difference.
  • these slide members move up and down at timings which deviate corresponding to the angular phase difference.
  • the material is not worked simultaneously with descents of the slide members. Therefore, the molding load of the pressing machine is reduced.
  • the respective slide members are independently separated from each other. Hence, even when the thrust load acts on the top tool on the single working stage, the top tools secured to these slide members do not exert adverse influences on each other. Further, the horizontal positions of the individual slide members are adjusted by the slide horizontal position adjusting devices. Therefore, the core deviation between the top and bottom tools is obviated, and the material is thus worked. A molded product is formed at a high accuracy by effecting the automatic core-adjustment between the top and bottom tools with the slide horizontal position adjusting devices during working of the material. Besides, the life-span of the dies also increases.
  • the slide members are raised and lowered by the slide lifters with respect to the con'rods, thereby performing the slide adjusting operation and the slide bottom dead center compensating operation as well.
  • the core-deviation between the top and bottom tools can be obviated by the slide horizontal position adjusting device.
  • the slide adjusting operation and the slide bottom dead center compensating operation can be performed by the slide lifter. Besides, it is feasible to attain reductions in the vibrations and noses in the breakthrough.
  • a motor 3 is mounted on a crown 2 of a pressing machine 1.
  • a driving force of the motor 3 is transferred via a belt 4, a flywheel 5 and a clutch 6 to a crank shaft 8 fitted with a brake 7.
  • An eccentric unit 9 consisting of totally three pieces of eccentric members 9A, 9B, 9C is provided on the crank shaft 8 axially rotatably supported in an interior of the crown 2.
  • Upper portions of con'rods 10 are rotatably fitted to the eccentric unit 9.
  • a slide unit 12 is connected through a slide lifter 11 to lower portions of the con'rods 10.
  • the slide unit 12 includes, as similar to the eccentric unit 9, totally three pieces of slide members 12A, 12B, 12C. These slide members are independently separated from each other.
  • the eccentric members 9A, 9C are formed with the same angular phase in the circumferential direction of the crank shaft 8.
  • the eccentric member 9B is, however, formed with an angular phase advanced in the rotating direction of the crank shaft 8 with respect to these eccentric members 9A, 9C. For this reason, there is a difference in the angular phase between the eccentric members 9A, 9C and the eccentric member 9B.
  • the slide member 12B reaches a bottom dead center first.
  • the slide members 12A, 12C reaches the bottom dead center second.
  • Top tools 13 are secured to the lower surfaces of the respective members of the slide unit 12.
  • Bottom tools 15 corresponding to the top tools 13 are secured to an upper surface of a bolster 14.
  • These top tools and bottom tools, 13, 15 are combined to constitute working stages A, B, C for effecting progressive-working on a material 16.
  • the material 16 composed of a coil material is intermittently fed by a feed roller device 17 every time the slide unit 12 moves up and down.
  • the material 16 is worked sequentially by the top tools 13 and the bottom tools 15 on the respective working stages A, B, C.
  • the top tools 13 and the bottom tools 15 in this embodiment are dies and punches for punching out the material 16.
  • a molding load of the pressing machine is not a total of working loads on the working stages A, B, C.
  • the molding load is a total of the working loads on the two working stages A, C, resulting in a reduction in the molding load. For this reason, in accordance with this embodiment, it follows that vibrations and noises of the pressing machine which are caused when working the material 16 are decreased.
  • the slide unit 12 is constructed of a circular platen 19 encased in a lower box-like case 18 and a guide member 20 standing erect from the platen 19.
  • the guide member 20 assuming a cross in plane includes a forward extending portion 20A, a backward extending portion 10B, a leftward extending portion 20C and a rightward extending portion 20D which extend in back-and-forth directions and in right-and-left directions.
  • These extending portions 20A, 20B, 20C, 20D have, as illustrated in FIG. 3, surfaces, 21, 22, 23, 34, 25, 26, 27, 28 by twos which are directed opposite to each other.
  • the surfaces 25, 28, the surfaces 26, 27, the surfaces 21, 24 and the surfaces 22, 23 shape four perpendicular surfaces D, F, E, F, G on the slide unit 12, which face in orthogonal horizontal directions, i.e., in the back-and-forth directions and in the right-and-left directions.
  • a frame 29 of the pressing machine 1 is fitted with pads 30 confronting the surfaces 21 - 28 with slight gaps therebetween.
  • These pads 30 are supplied with a high pressure oil from a hydraulic source 31 via a hydraulic circuit 32.
  • the pressures of the pressure oil supplied to the respective pads 30 act on the surfaces 21 - 28.
  • the pressure oil is supplied in common from a branch circuit of the hydraulic circuit 32 to the two pads 30 shown in FIG. 3 and confronting the two surfaces among the surfaces 21 - 28, these two surfaces forming one perpendicular surface among the four perpendicular surfaces D - G.
  • the pressure oil is supplied from a branch circuit 32A of the hydraulic circuit 32 to the two pads 30 confronting the surfaces 25, 28 which form the perpendicular surface D facing frontwards in the to-and-fro directions.
  • the pressure oils are supplied from branch circuits 32C, 32D to two pairs of pads 30 respectively confronting the surfaces 21, 24 and the surfaces 22, 23 which form the perpendicular surfaces F, G facing bilaterally in the right-and-left directions.
  • the pads 30 are provided at upper and lower two stages. With this arrangement, the pressure oils are actually supplied in common to the four pads 30 from one branch circuit.
  • the branch circuits 32A - 3D are provided with control valves 33 - 36.
  • These control valves 33 - 36 are ON/OFF-operated by electric signals transmitted from an unillustrated control unit. In the case of an ON operation, the pressure oil is supplied to the pads 30. Whereas in an OFF operation, the pressure oil from the hydraulic circuit escapes into a tank 37.
  • the control valves 33 - 36 are high-respondency valves each exhibiting a very high OFF-switching speed; and the OFF operation can be executed many times within a short time.
  • the control valves 33 - 36 are normally ON-operated. Hence, the pressure oil having the same pressure is supplied to all the pads 30.
  • the slide unit 12 is in a constant position in the to-and-fro directions and in the right-and-left directions owing to a pressure balance between the pressure oils. Besides, the slide unit 12 does not rotates about a vertical shaft.
  • one of the control valves 33 - 36 is OFF-operated, no pressure oil is supplied to the pad 30 connected to this control valve during this OFF operation. The pressure balance between the pressure oils is thereby lost, with the result that a horizontal thrust force toward the pads 30 supplied with no pressure oil is caused in the slide unit 12. If the control valve is OFF-operated many times within the short time, the slide unit 12 moves largely in the horizontal direction.
  • a moving quantity of the slide unit 12 can be set by the number of OFF-operations of the control valve.
  • control valves 33 - 36 are intended to prescribe the supply of the pressure oil to the pads 30.
  • the position of the slide unit 12 can be properly modified to a horizontal position by the ON/OFF switching operations of these control valves 33 - 36.
  • the pressure oil supplied to the respective pads 30 flows out of the slight gaps between the surfaces 21 - 28 of the slide unit 1 and the pads 30 shown in FIG. 5.
  • the effluent pressure oil drops down onto the upper surface of the platen 19.
  • a side wall 19A is formed along the outer peripheral edge of the platen 19.
  • An oil receptacle 39 is formed on the upper portion of the platen 19. The oil is therefore reserved in the oil receptacle 39 and fed back to the tank via an oil suction collecting circuit connected to the platen 19.
  • a back-and-forth position detecting sensor 40 and a right-and-left position detecting sensor 41 which confront in the horizontal direction with gaps from the backward extending portion 20B and the leftward extending portion 20C of the slide unit 12.
  • These sensors 40, 41 detect a back-and-forth position and a right-and-left position of the slide unit 12.
  • Transmitted from the sensors 40, 41 to the control unit are electric signals of the detected back-and-forth and right-and-left positions of the slide unit 12. Based on the electric signals, the control unit transmits electric signals to effect ON/OFF changeovers of the control valves 33 - 36.
  • a slide horizontal position adjusting device 42 for adjusting two positions of the slide unit 12 in orthogonal horizontal directions is constructed of the pads 30 so provided on the frame 29 of the pressing machine 1 as to confront the slide unit 12 in the horizontal direction, the back-and-forth position detecting sensor 40 and the right-and-left position detecting sensor 41.
  • This slide horizontal position adjusting device 42 is constructed to include the control valves 33 - 36 and the control unit as well.
  • the frame 29 of the pressing machine 1 is also mounted with a height position detecting sensor 43 for detecting a height position of the slide unit 12.
  • This sensor 43 is mounted on the frame 29 with a gap from the rightward extending portion 20D of the guide member 20 of the slide unit 12 in accordance with this embodiment.
  • An electric signal, transmitted from the sensor 43, of the height position of the slide unit 12 is inputted to the control unit.
  • the respective members of the slide unit 12 make the vertical motions while the pressures of the pressure oils from the respective pads 30 act on the surfaces 21 - 28 of the guide member 20, assuming the cross in plane, of the slide unit 12.
  • all the control valves 33 - 36 are ON-operated, and hence the slide unit 12 is in the constant position in the back-and-forth directions and in the right-and-left directions with the pressure balance of the pressure oils from the respective pads 30. In this state, the slide unit moves up and down.
  • a leftward thrust load W 1 acts on the top tool 13 as reaction from the material 16.
  • the top tool 13 and the slide unit 12 move left to cause an eccentric quantity e due to this thrust load W, .
  • This movement of the slide unit 12 is detected by the right-and-left position detecting sensor 41 shown in FIG. 3.
  • the control unit Based on the electric signal transmitted from this sensor 41, the control unit performs the OFF operation of the control valve 36 for a short period of time. Lost consequently is the lateral pressure balance between the pressure oils from the pads 30 which act on the slide unit 12.
  • the top and bottom tools 13, 15 punch out the material 16 with no core deviation, and a molding accuracy of a molded product out of the material 16 increases.
  • the top tool 13 is automatically core-adjusted and fitted to the bottom tool 15 in this manner, whereby these tools 13, 15 do not frictionally contact each other. It is therefore possible to prevent a reduction in the lifetime of the tools 13, 15.
  • the three slide members 12A, 12B, 12C are independently separated from each other. Hence, even when the thrust load W 1 acts on the top tool 13 on a certain working stage, this thrust load W 1 is not transferred to the top tools 13 on other working stages. Accordingly, the tools 13 on the respective working stages A, B, C exert no adverse influence on each other.
  • the top and bottom tools 13, 15 on the individual working stages A, B, C are automatically core-adjusted by the slide horizontal position adjusting device 42 provided in each of the slide members 12A, 12B, 12C. Then, the material 16 is worked, thereby enhancing the molding accuracy of the molded product.
  • the automatic core-adjustment for aligning the top and bottom tools 13, 15 may be performed after the above-described sensors have detected the movements of the slide unit 12 and the top tool 13 due to the thrust load W 1 during the punch-out of the material 16 as explained before.
  • the horizontal position of the slide unit 12 is constantly detected by the sensor before punching out the material 16 by the top and bottom tools 13 and 15, whereby the automatic core-adjustment may be executed based on the detection of the core deviation quantity e.
  • FIG. 6 illustrates the slide lifter 11 provided between the slide member and the con'rod 10 shown in FIGS. 1 and 2.
  • This slide lifter 11 constructed of a hydraulic cylinder 44 fixed to an upper end of the slide unit 12 and a vertically movable pressure receiving member 45 for receiving a hydraulic pressure in the hydraulic cylinder 44.
  • a piston portion 46 is provided in the lower part of the pressure receiving member 45.
  • An internal chamber of the hydraulic cylinder 44 is sectioned by this piston portion 46 into an upper chamber 47 and a lower chamber 48.
  • the stepped piston portion 46 consists of an upper large-diameter portion 46A and a lower small-diameter portion 46B.
  • the upper chamber 47 in which the large-diameter portion 46A makes vertical motions has a large area.
  • the lower chamber 48 in which the small-diameter portion 46B makes the vertical motions has a small area.
  • An upper portion 45A of the pressure receiving member 45 protrudes upwards from the hydraulic cylinder 44.
  • a lower portion of the above- mentioned con'rod 10 is rotatably connected via a wrist pin 49 to this upper portion 45A.
  • Hydraulic circuits 50, 51 extending from the hydraulic source 31 are connected to the upper and lower chambers 47, 48.
  • the hydraulic circuit 50 is provided, from the upstream side, with a first changeover valve 52 and a first variable throttle valve 53.
  • the hydraulic circuit 51 is provided, from the up stream side, with a pressure-Oreducing valve 54 and a second variable throttle valve 55.
  • a connection circuit 56 for connecting the upper chamber 47 to the lower chamber 48 is interposed between the hydraulic circuits 50, 51.
  • This connection circuit 56 is provided with a second changeover valve 57.
  • the circuits 50, 56 are opened and closed by ON/OFF operations of the first and second changeover valves 52, 57.
  • the ON/OFF operations of these valves 52, 57 are performed automatically by the control unit or by manual operations.
  • the second changeover valve 57 is operated based on the electric signal of the height position of the slide unit 12, which is transmitted from the height position detecting sensor 43 to the control unit.
  • the supply of the hydraulic pressure into the hydraulic cylinder 44 from the hydraulic source 31 involves the following steps.
  • the first and second changeover valves 52, 57 are operated to close the hydraulic circuit 50 and the connection circuit 56. Thereafter, when the high pressure oil is fed from the hydraulic source 31, this pressure oil is depressurized down to a predetermined pressure by the pressure-reducing valve 54. Then, the pressure oil is supplied via the hydraulic circuit 51 to the upper chamber 47, and the pressure receiving member 45 is lowered down to a decent limit by the hydraulic pressure.
  • the first changeover valve 52 is ON-operated to open the hydraulic circuit 50. Then, the high pressure oil from the hydraulic source 31 is fed via the hydraulic circuit 50 to the lower chamber 48.
  • a pressure of the pressure oil supplied to this lower chamber 48 is not the depressurized by the pressure-reducing valve 54, and hence, even when the area of the lower chamber 48 is smaller than that of the upper chamber 47, the pressure receiving member 45 is raised by the hydraulic pressure within the lower chamber 48.
  • the pressure oil forced out from the upper chamber 47 returns to the tank 37 from the pressure reducing valve 54.
  • the first changeover valve 52 is OFF-operated to close the hydraulic circuit 50.
  • the upper chamber 47 is thereby filled with the lower pressure oil, while the lower chamber 48 is filled with the high pressure oil.
  • the second changeover valve 57 is ON-operated to open the connection circuit 56. Then, the pressure oil of the lower chamber 48 flows into the upper chamber 47 via the connection circuit 56, whereby the pressure receiving member 45 is lowered.
  • the second changeover valve 57 defined as a high-respondency control valve is ON/OFF-operated many times, a good deal of pressure oil flows into the upper chamber 47. It follows that the pressure receiving member 45 is descended corresponding to a large stroke. A descent quantity of the pressure receiving member 45 can be determined by the number of ON/OFF operations of the second changeover valve 57.
  • the slide unit 12 is raised and lowered by the slide lifter 11 with respect to the con'rod 10. It is therefore possible to perform the slide adjusting operation for determining the height position of the slide unit 12 in accordance with height dimensions of the top and bottom tools 13, 15. It is also feasible to effect a bottom dead center compensating operation when the bottom dead center of the slide unit 12 fluctuates in the case of a thermal expanding deformation of the slide unit 12 due to the press working heat.
  • the slide lifter 11 incorporates a function as a slide adjuster capable of performing such operations.
  • the ascending and descending motions of the slide unit 12 with respect to the con'rod 10 are carried out by the influx of the pressure oil of the lower chamber 48 into the upper chamber 47 via the connection circuit 56 provided with the second changeover valve 57.
  • the slide lifter 11 is constructed to include the connection circuit 56 and the second changeover valve 57 as well.
  • the slide lifter 11 make the following action in addition to the slide adjusting operation and the slide bottom dead center compensating operation.
  • the pressure of the pressure oil in the lower chamber 48 is high due to a downward thrust force of the pressure receiving member 45. Therefore, when the second changeover valve 57 is ON-operated, the pressure oil of the lower chamber 48 flows into the upper chamber 47 via the connection circuit 56. A flow rate of the pressure oil at this time is restricted by the variable throttle valves 53, 55.
  • the elastic energy accumulated in the column 59 is thereby converted into a flow speed energy of the pressure oil forced out by the pressure receiving member 45 from the lower chamber 48 into the upper chamber 47 and simultaneously into an exothermic energy in the variable throttle valves 53, 55. For this reason, when the top tool 13 punches out the material 16, the elastic energy accumulated in the column 59 does not become an energy to cause large vibrations and noises of the pressing machine 1 due to rapid descents of the slide unit 12 and the top tool 13. A breakthrough of the pressing machine 1 during the punch-out is reduced. Hence, the slide lifter 11 has a function as a breakthrough countermeasure device.
  • the second changeover valve 57 is OFF-operated, or the first changeover valve 52 is ON-operated simultaneously with or slightly after a completion of the punch-out. Consequently, the high oil pressure from the hydraulic source 31 runs into the lower chamber 48 via the hydraulic circuit 50, whereby the lowered pressure receiving member 45 is raised, and the slide lifter 11 reverts to the previous state. Then, the first changeover valve 52 is OFF-operated, resulting in a return to a state enough to perform the next working operation.
  • the slide unit 12 is provided with the guide member 20 assuming the cross in plane.
  • the surfaces 21 - 28 of the guide member 20 configure the perpendicular surfaces D, E, F, G facing in the tow orthogonal horizontal directions, i.e., in the to-and-fro directions and in the right-and-left directions.
  • These perpendicular surfaces can be also, however, configured by forming the slide members in quadrangles.
  • the present invention includes the slide members assuming such configurations,
  • the slide unit 12 has three pieces of slid members 12A, 12B, 12C.
  • the number of the slide members is not, however, limited to this.
  • the two eccentric members 9A, 9C among the eccentric members 9A, 9B, 9C of the crank shaft 8 assume the same angular phase. However, the angular phases of all the eccentric members may be made different.
  • the con'rod 10 is connected through the wrist pin 49 to the slide lifter 11. This connection may be, however, effected by a connecting member having a spherical contact ball part.
  • the pressing machine may be provided with any one of the slide horizontal position adjusting device 42 and the slide lifter 11. Besides, a single member of the slide unit 12 may suffice for the pressing machine.
  • FIG. 7 illustrates a case where the pressing machine having the single member of the slide unit 12 is equipped with the slide horizontal position adjusting device 42 but with no slide lifter 11.
  • the pressing machine performs the function of one of these devices.
  • the performance of the pressing machine can be more enhanced than in the prior art.
  • each embodiment can exhibits the function as the slide horizontal position adjusting device without adding any modification.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Presses And Accessory Devices Thereof (AREA)
EP19920111480 1991-11-13 1992-07-07 Pressing machine Withdrawn EP0546249A3 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP32541591A JPH0757436B2 (ja) 1991-01-23 1991-11-13 プレス機械のスライド水平方向位置調整装置
JP325414/91 1991-11-13
JP325415/91 1991-11-13
JP3325414A JPH0790396B2 (ja) 1991-01-21 1991-11-13 プレス機械

Publications (2)

Publication Number Publication Date
EP0546249A2 true EP0546249A2 (de) 1993-06-16
EP0546249A3 EP0546249A3 (en) 1993-08-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920111480 Withdrawn EP0546249A3 (en) 1991-11-13 1992-07-07 Pressing machine

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EP (1) EP0546249A3 (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996022846A1 (en) * 1995-01-27 1996-08-01 The Whitaker Corporation Stamping and forming machine with a power distribution mechanism
WO1999007493A1 (en) * 1997-08-06 1999-02-18 The Whitaker Corporation Assembly machine
EP0953438A1 (de) * 1998-04-30 1999-11-03 Bruderer Ag Stanzpresse, insbesondere Schnelläuferpresse
CN101462135B (zh) * 2008-07-31 2011-08-31 宁波澳玛特高精冲压机床股份有限公司 一种偏心曲轴冲床
CN104309148A (zh) * 2014-09-22 2015-01-28 沃得重型机床（中国）有限公司 三点机械压力机传动装置
CN104624777A (zh) * 2015-01-22 2015-05-20 安徽万嘉新能源科技有限公司 一种太阳能保温箱外罩冲孔装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3005404A (en) * 1959-09-01 1961-10-24 Tucker & Sons Hydraulic connecting unit for punch-press rams
DE1812860A1 (de) * 1968-12-05 1970-06-18 Koch Robert Nach dem Oeillet-Verfahren arbeitende Stanze
DE2040742A1 (de) * 1970-08-17 1972-03-02 Eugen Siempelkamp Presse,insbesondere Gesenkschmiedepresse
FR2600932A3 (fr) * 1986-07-03 1988-01-08 Inoplast Sa Perfectionnements aux presses de moulage, notamment par compression de materiaux composites ou autres
DE4128895A1 (de) * 1990-08-30 1992-03-05 Aida Eng Ltd Verfahren und vorrichtung zum fuehren eines gleiters einer pressmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3005404A (en) * 1959-09-01 1961-10-24 Tucker & Sons Hydraulic connecting unit for punch-press rams
DE1812860A1 (de) * 1968-12-05 1970-06-18 Koch Robert Nach dem Oeillet-Verfahren arbeitende Stanze
DE2040742A1 (de) * 1970-08-17 1972-03-02 Eugen Siempelkamp Presse,insbesondere Gesenkschmiedepresse
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US5611235A (en) * 1994-01-25 1997-03-18 The Whitaker Corporation Power distribution mechanism in a stamping and forming machine and method
WO1996022846A1 (en) * 1995-01-27 1996-08-01 The Whitaker Corporation Stamping and forming machine with a power distribution mechanism
WO1999007493A1 (en) * 1997-08-06 1999-02-18 The Whitaker Corporation Assembly machine
EP0953438A1 (de) * 1998-04-30 1999-11-03 Bruderer Ag Stanzpresse, insbesondere Schnelläuferpresse
CN101462135B (zh) * 2008-07-31 2011-08-31 宁波澳玛特高精冲压机床股份有限公司 一种偏心曲轴冲床
CN104309148A (zh) * 2014-09-22 2015-01-28 沃得重型机床（中国）有限公司 三点机械压力机传动装置
CN104309148B (zh) * 2014-09-22 2016-04-20 沃得重型机床（中国）有限公司 三点机械压力机传动装置
CN104624777A (zh) * 2015-01-22 2015-05-20 安徽万嘉新能源科技有限公司 一种太阳能保温箱外罩冲孔装置

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