US3274819A - Forging presses - Google Patents

Forging presses Download PDF

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Publication number
US3274819A
US3274819A US270705A US27070563A US3274819A US 3274819 A US3274819 A US 3274819A US 270705 A US270705 A US 270705A US 27070563 A US27070563 A US 27070563A US 3274819 A US3274819 A US 3274819A
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Prior art keywords
peel
manipulator
press
carriage
forging
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Expired - Lifetime
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US270705A
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English (en)
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Knowles Keith
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British Iron and Steel Research Association BISRA
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British Iron and Steel Research Association BISRA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J13/00—Details of machines for forging, pressing, or hammering
    • B21J13/08—Accessories for handling work or tools
    • B21J13/10—Manipulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/34—Drives for hammers; Transmission means therefor for power hammers operating both the hammer and the anvil, so-called counter-tup

Definitions

  • This invention is concerned with improvements in or relating to forging presses and manipulators therefor, and it is amongst the objects of the invention to provide a construction of forging press and of ancillary equipment whereby a group of specified products can be processed, including for example plain cogged bars, rounds, shafts, collars and rolls, and whereby more efficient operation and greater productivity can be achieved through more rapid manipulation and control and co-ordination of the press and the manipulator movements.
  • FIGURE 1 is an elevation of the forging press
  • FIGURE 2 is a plan view of the press
  • FIGURE 3 is a section on the line A-A of FIGURE 1;
  • FIGURE 4 is a section on the line BB of FIGURE 3;
  • FIGURE 5 is a section of the press showing in elevation the manipulator;
  • FIGURE 6 is a plan view of the tor
  • FIGURE 7 is a section of the press on the line BB of FIGURE 6 showing the central workpiece support
  • FIGURE 8 is a section of the press on the line A-A of FIGURE 5 showing the tool changing mechanism
  • FIGURE 9 is an elevation of the master manipulator
  • FIGURE 10 is a plan view of the master manipulator
  • FIGURES 11 and 12 are sections on the lines A--A and BB respectively of FIGURE 10';
  • FIGURE 13 is an end elevation of the .tor.
  • FIGURE 14 illustrates schematically a hydraulic control arrangement for the peel drive.
  • FIG- URES l to 4 shows the principal components of the press.
  • Two fixed crossheads 1 are separated by two tie bars 2.
  • Two movable crossheads 3 are positionedand supported relative to the fixed crossheads by the tie bars and are moved along them each by a matrix of hydraulic cylinders and pistons 4, or alternatively the more conventional three ram drive.
  • each matrix is arranged as twelve cylinders 5 and nine pistons 6 on the fixed cr-osshead with the complementary grouping of nine cylinders and twelve pistons on the movable crosshead, the complete assembly forming a five-by-five matrix with each corner cylinder removed.
  • a return cylinder and piston 7 is located at each of the four corner positions.
  • the three ram configuration may comprise either three pistons of equal size, or be such that the effective ram area of the central piston is equal to four times that of each of the two outer pistons.
  • Hydraulic oil supplies can be directed through the fixed crossheads with the cylinders in the movable crossheads receiving their supply through special hollow pistons 8, thus eliminating any external pipes to the movable crosshead.
  • the tie bars may be either round (as shown) or rectangular in cross-section and are positioned so that the vertical distance between them is sufiicient to allow free passage for manipulator jaws holding a workpiece.
  • Each has a solid centre to withstand the complex stresses imposed during forging, and a series of cooling water passages 2a on the outside of this solid centre.
  • the water cooled area of each tie bar extends only between the fixed crossheads.
  • a compound, dual motion drive is provided for longitudinal workpiece positioning .and comprises a manipulator drive for longitudinal positoning of the manipulator which drive is in the form of a. rack and pinion drive as shown at 22, 23, or a hydraulic cylinder drive, say, and a peel drive for longitudinal positioning of the peel relative to the manipulator which drive is in the form of a short stroke hydraulic cylinder 30 to provide rapid movement of a workpiece held by the manipulator peel when forging and also to function as a shock absorber when planishing.
  • the cylinder 30' which has a stroke larger than the maximum bite width is attached to the main frame of the manipulator, its piston rod 300: being connected to the end of the moving peel.
  • the whole manipulator runs on guide rails which restrain it both laterally and vertically.
  • the master manipulator 9 which grips one end of the workpiece provides all the necessary controlled movements while the slave manipulator .10 which follows the master manipulator peel movements provides support for the other end of the workpieces.
  • both manipulators are railbound allowing their weight to be reduced by a lighter construction.
  • the master manipulator includes a peel comprising an outer tube 11 inside which slides the reciprocating peel 12.
  • the jaws for holding the workpiece 13 are located at the free end of the peel.
  • To the other end of the peel is attached the piston rod of the peel actuating cylinder 30 which is secured to the outer tube.
  • a gear drive 15 rotates the outer tube which is mounted in bearings 16 capable of withstanding the moments induced by the workpiece overhang.
  • the rotational drive is transmitted to the inner tube, or peel by means of splines 17.
  • the housings of the rotational bearings are carried on four trunnions 18 which run in bearings 19 integral with the main manipulator chassis. The trunnions allow the peel assembly to be moved bodily sideways under the action of hydraulic rams 20.
  • the motor 21 for the rotational drive is rigidly mounted between the two bearing housings and this mounting is movable sideways together with the peel assembly.
  • Two pinion drives 22 are included to enable the racks 23 to be positioned so that scale falling from the ingot falls between the racks and does not impair their operation.
  • manipulator operation for longitudinal workpiece positioning is as follows: the pinion drive propels the manipulator forward at a constant linear velocity, along the fixed rack.
  • the peel drive is controlled so that the peel is propelled in an opposite direction, at a velocity equal to the sum of the manipulator linear velocity and the velocity caused by ingot extension, with the net results that the manipulator peel remains stationary.
  • the peel drive 3 is controlled so that the peel is driven rapidly, in the same direction as the manipulator drive, to its starting position relative to the manipulator. This results in a velocity of workpiece longitudinal advance, or bite, equal to the sum of the manipulator and peel drives at the time in which they are both effective in the same direction.
  • FIGURE 14 illustrates one form of control arrangement for the above double-motion operation.
  • the peel drive is illustrated schematically as a doubleacting piston-and-cylinder assembly 30 having a piston rod 30a connected to the peel (not shown) at one end and its casing 30d connected to the main frame of the manipulator, and having ports at 30b and 300 for individual hydraulic lines 31 and 32.
  • Hydraulic lines 31 and 32 are connected to individual ports on one side of a 2-position 4-way valve 33 which provides straightthrough fluid flow in the operative position 33a shown, or cross-over fluid flow in its other operative position 33b, relative to two hydraulic fluid lines 34 and 35 connected to two ports on the other side of valve 33.
  • Valve 33 may be of any suitable known form and arranged for switching between its two positions in any convenient manner, mechanically or electrically, say.
  • Hydraulic lines 34 and 35 are arranged for connection through a 2-position Z-way solenoid operated valve 36.
  • Valve 36 may be operated to the position 36a shown, in which lines 34 and '36 are connected, by energisation of solenoid 360 against the spring pressure of spring 36d. On de-energisation of solenoid 360, the pressure exerted by spring 36d switches valve 36 to become effective in position 36b, whereby the connection between lines 34 and 35 is broken.
  • Hydraulic lines 34 and 35 are also connected to individual ports on one side of a 2-position 4-way valve 37 normally held by spring 37d in position 37a, as shown, or alternatively held in position 37b by energisation of solenoid 37c.
  • the associated ports on the other side of valve 37 are respectively connected to a hydraulic fluid line 38 for supplying fluid at predetermined pressure on the one hand, and to drain 39 on the other hand.
  • valve mechanisms are positioned as shown during squeezes with the peel positioned in a fixed relation to the manipulator at initiation of a squeeze.
  • This position of the peel has been re ferred to above as the starting position but is perhaps better regarded as a datum position which will normally be such that the piston is centrally disposed within its cylinder as indicated in broken outline.
  • the press tools commence separation and as soon as the tools clear the workpiece solenoid 360 is energised to change valve 36 to position 36b.
  • the result of this is to cut off the supply to cylinder 30 at 30c whereby the piston is driven from right to left by the supply at 30b with the left hand side of cylinder 30 exhausting to drain 39 through lines 32 and 35.
  • the pressure of fluid supply to line 38 will be so chosen that the piston is driven rapidly back to its datum position at least by the time of initiation of the next squeeze.
  • solenoid 360 of valve 36 is de-energised so that the valve returns to position 36a whereby the piston floats within cylinder 30 once more, that is to say, the peel then remains stationary relative to the manipulator.
  • the actual workpiece longitudinal advance or bite is determined by the constant velocity of the manipulator drive and the squeeze repetition rate or so-called press cycle time.
  • the press cycle time and required bite are substantially constant so that the corresponding constant velocity for the manipulator drive can be readily predetermined.
  • a control signal generated in response to equality between the above compared signals can be employed to initiate energisation of solenoid 360.
  • control signal for causing energisation of solenoid 360 may be derived by comparison of the press tool position signal with the initial thickness representation stored at the beginning of a forging pass, the solenoid control signal being generated when these compared representations are equal.
  • the control signal is required only during tool separation. Since in the above-mentioned proposals use is also made of a relay operated to different states in accordance with tool closure or separation, then clearly selection of the correct alternate instants of equality between the compared signals can be readily effected. Again, such an indication of tool separation is available from the increase or decrease of the tool position signal itself.
  • electrical circuits are in any event readily available, which circuits are responsive to alternate ones of input signals to generate an output signal.
  • a further control signal may be obtained for this purpose by way of a limit switch having a first contact fixed relative to the manipulator and a second contact fixed relative to the peel and movable therewith, these contacts being positioned for engagement to produce the further control signal when the peel is in its datum position.
  • This further control signal is employed to de-energise solenoid 360.
  • this limit switch is effective to generate the further control signal just before the peel reaches its datum position, so that account is taken of the inertia of the peel drive. This may be achieved by making one of the limit switch contacts of appropriate width in the direction of peel travel, this width being equally spaced on both sides of the theoretically ideal datum position location for that contact.
  • solenoid 360 is required to be energised in response to a control signal, which will be of pulse form, and retained energised until de-energised in response to a further control signal.
  • a control signal which will be of pulse form
  • a further control signal This may be effected by application of the control and further control signals as the two inputs of a bi-stable device, or so-called flip-flop, that is an electrical circuit arranged to produce a first continuous output signal when set to one stable state by the control signal, and to produce a second continuous output signal when set to its other stable state by the further control signal.
  • valve 36 With the form of valve 36 shown in FIGURE 14, position 36a is automatically obtained upon de-energisation of solenoid 360 by the action of spring 36d, and this position will be maintained until solenoid 36c is energised once more.
  • the above flip-flop control allows other forms of valve 36 to be employed in which positions 36a and 36b are obtained by energisation of a common solenoid in different senses, or even by use of individual solenoids.
  • FIGURE 14 operation and its control has dealt with longitudinal workpiece advance in one direction.
  • a similar operation is appropriate to such advance in the opposite direction simply by making valve 33 effective in position 33b instead of position 33a.
  • the necessary change-over of valve 33 for this purpose will, of course, only be required between successive forging passes.
  • valve 37 when in position 37b, and it will be seen that this is effective to lock the peel drive.
  • Such locking is desirable in association with forging operations in which the workpiece is required to remain in a fixed longitudinal position for a succession of squeezes, for example, as in the case with cutting and knifing operations when the workpiece is, at most, only rotated between successive squeezes.
  • the above compound drive system can be both rapid acting and accurate, since the accuracy depends on the longitudinal positioning of the manipulator relative to the press by the manipulator drive over a long length, and to the final positioning of the workpiece relative to the manipulator by the hydraulic peel drive over a relatively short stroke. Due to the fact that the force exerted by the workpiece on the manipulator is absorbed by the hydraulic cylinder of the peel drive, the peel can stop under momentary overload without damage.
  • the various motions on the manipulator are operated by a number of hydraulic motors which are supplied from a common hydraulic pump unit which in turn is driven by an electric motor.
  • a single oil reservoir and accumulator assembly can be used.
  • Independent hydraulic motors or actuators and relevant valves are required for each of the following motions:
  • the hydraulic pumping unit selected for the manipulator should be capable of accommodating the maximum demand possible, bearing in mind that all motions cannot be operated simultaneously.
  • Fabrication of the manipulator chassis is such as to assure maximum economy in weight and size to Withstand the complex stresses induced by the forces required to accelerate the peel and to withstand the overturning moments and deadweight loads.
  • Rigidity of the side members is essential to enable the loads to be transmit-ted from the trunnions to the manipulator track.
  • the function of the slave manipulator is to support the workpiece, and to position it on the same axis as that of the master manipulator to ensure correct workpiece presentation to the press and also to facilitate forging on the advance and retreat.
  • a small hydraulic power pack only is required for the three motions which include gripping, transverse positioning and longitudinal drive for movement of the slave manipulator.
  • the longitudinal drive equipment could be positioned on the floor rather than on the slave manipulator chassis, as it is only required to enable the manipulator to be positioned to accept the ingot. Thereafter, at least the transverse and longitudinal drives will be disengaged during the forging operation and the slave manipulator will be positioned by the wonkpiece.
  • a further item of manipulation equipment may be included which is located at the intersection of the railbound manipulator and press forging axis. This takes the form of a central workpiece support and the main functions of this will be:
  • the support comprises a flat-horizontal roller table 25 capable of supporting the full weight of the workpiece.
  • Means are incorporated for driving the rolls, rotating the table about a vertical axis and adjusting the whole support vertically to receive workpieces of varying diameters. Preferably it is completely retractable beneath the floor level when not in use.
  • a tool changing mechanism for each movable crosshead includes two hinged plates 26 normally forming part of the floor between the fixed crossheads but which can be opened into the vertical position directly beneath the tools.
  • a slide on the underside of each plate interconnects the tool slide on the adjacent movable crosshead and a tool changer mechanism beneath the floor.
  • a vertical ram assembly 27 which forms part of each tool changer can be raised to engage the tool and extracts the tool from the crosshead.
  • the tool is then lowered into a magazine 28 which can be indexed so that the next selected tool is positioned beneath the crosshead for insertion by the vertical ram assembly.
  • a system of spring loaded locking devices retains the tool on the crosshead. It will be seen that the tool changing operation can be effected with the workpiece within the press structure.
  • the system of control for the integrated forging unit will require initially, a complete forging schedule .to be determined and fed into the control unit.
  • the forging unit When initiated, the forging unit will perform the calculated pass sequences until the whole programme has been completed.
  • Information such as workpiece size and length, and datum positions of both manipulators can be set and stored in digital form so that together with the original forging schedule it can be fed back to the control system during the forging operation.
  • Manual control of all motions should be available to enable the initial setting up and the determination of datum positions of the ingot to be made.
  • the forging press described and shown presents various advantages.
  • the press will be more accessible for maintenance work much of which should be accomplished from floor level.
  • the crosshead can be readily withdrawn from the backing plate along the tie bars to reveal the pistons and cylinders for easy maintenance work and hydraulic seal renewals.
  • Tool changing becomes simplified with a horizontal press; all tools can be extracted and replaced from a tool magazine located directly beneath the axis of operation of the tools and this operation can be speedly effected whilst the ingot remains within the press on its fixed forging axis.
  • Stability is increased because the centre of gravity of the press is beneath the tool axis and the press covers a relatively large bearing surface.
  • Double-acting feature (a) The centre line axis of the ingot remains constant during the entire forging operation; this simplifies the manipulator design and saves valuable forging time by eliminating the vertical motion.
  • Two-column feature A two column press where the tie-bars are positioned on an axis oflset from the vertical allows the manipulator a greater degree of accessibility into the working area of the press tools. This should enable very short ingots to be forged and also enable all ingots to be forged to their full extremity in length.
  • the use of two columns permits a saving in size of both fixed and movable crossheads with an attractive economy in the overall size and weight of the press.
  • Multi-cylinder high pressure hydraulic drive results in smaller piston diameters for corresponding thrust values.
  • a more even load distribution can be obtained behind the press tool, and any combination of cylinders symmetrical about the central axis of the tools can be used to provide a variety of press capacity ratings.
  • Support is provided for the ingot at both ends, so that it will always be presented to the tools on a fixed horizontal axis.
  • the ingot can be moved transversely during initial setting up.
  • a workpiece manipulator for a forging press comprising a carriage (9, 10), carriage drive means (22-23) for continuously driving said carriage during a forging pass, a peel (12) mounted on said carriage, and peel drive means (30-39) for driving said peel longitudinally relative to said carriage
  • said peel drive means comprising a double-acting piston-and-cylinder assembly (30) one element (30a) of which is connected to said peel and V the other of which is connected to said carriage and comprising valve means (33, 36, 37) operable in a first state in which fluid supplied to both ends of the cylinder for equal and opposite drive forces on the piston whereby said piston eflectively floats within said cylinder to permit, during a squeeze, relative movement of said peel and said carriage from a datum position, and operable in a second state in which fluid is supplied to one end of the cylinder and is exhausted from the other end thereof to return, between squeezes, said peel and said carriage to said datum position.
  • a manipulator according to claim 1 comprising two fluid lines (31, 32) respectively connected to the two ends of said cylinder, a common fluid supply line (38, 34) connected to a first one of said two fluid lines, a fluid drain line (35, 39) connected to the second one of said two fluid lines, and wherein said valve means includes a first valve mechanism (36) operable to open and closed states and connected between said common fluid supply line and said second fluid line.
  • valve means further comprises a second valve mechanism (33) connected in said two fluid lines, and operable in first and second states for straight-through and crossover connections of said two lines, respectively, relative to said common fluid supply line and said fluid drain line.
  • valve means additionally comprises a third valve mechanism (37) connected in said common fluid supply line and said fluid drain line, and operable to open and closed states.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
US270705A 1962-04-04 1963-04-04 Forging presses Expired - Lifetime US3274819A (en)

Applications Claiming Priority (1)

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GB12840/62A GB1015711A (en) 1962-04-04 1962-04-04 Improvements in and relating to forging presses

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US3274819A true US3274819A (en) 1966-09-27

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US (1) US3274819A (xx)
AT (1) AT260658B (xx)
CH (1) CH402568A (xx)
DE (1) DE1296596B (xx)
FR (1) FR1358689A (xx)
GB (1) GB1015711A (xx)
SE (1) SE303078B (xx)

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US3349601A (en) * 1963-06-19 1967-10-31 Adamson Alliance Company Ltd Manipulators
US3402592A (en) * 1965-03-02 1968-09-24 Davy & United Eng Co Ltd Manipulators
US3435650A (en) * 1965-04-07 1969-04-01 Davy & United Eng Co Ltd Forging control
US3444718A (en) * 1966-01-03 1969-05-20 Davy & United Eng Co Ltd Manipulators
US3447349A (en) * 1965-08-02 1969-06-03 Paul Lippke Method of and system for operating a high-speed forging press
US3468154A (en) * 1964-09-01 1969-09-23 Hydraulik Gmbh Fa Manipulator for forging press
US3472058A (en) * 1966-12-30 1969-10-14 Black Clawson Co Forging apparatus
US3473364A (en) * 1966-02-25 1969-10-21 Davy & United Eng Co Ltd Forging
US3504512A (en) * 1965-02-12 1970-04-07 British Iron Steel Research Apparatus for controlling a manipulator in association with a forging press
US3523444A (en) * 1968-01-05 1970-08-11 Cameron Iron Works Inc Hydraulic press
US3523445A (en) * 1968-04-30 1970-08-11 Cameron Iron Works Inc Press and ram type actuators for moving the platens thereof
US3523443A (en) * 1967-08-30 1970-08-11 Cameron Iron Works Inc Hydraulic press
US3590616A (en) * 1967-04-22 1971-07-06 Schloemann Ag Means for controlling the movements of a manipulator
US3603126A (en) * 1969-04-24 1971-09-07 Charles W Newman Method and apparatus for riveting with titanium alloys
US3712096A (en) * 1969-07-28 1973-01-23 O Hein Gripping head for gripping a workpiece to be swaged
DE1777380B2 (de) * 1967-08-30 1973-02-08 Cameron Iron Works Inc Hydraulische Presse
US3841139A (en) * 1971-03-16 1974-10-15 Langenstein & Schemann Ag Method and apparatus for the forming of a long workpiece
DE2423503A1 (de) * 1974-05-15 1975-11-27 Kautex Werke Gmbh Vorrichtung zum herstellen von hohlkoerpern aus thermoplastischem kunststoff
FR2385466A1 (fr) * 1977-04-01 1978-10-27 Gfm Fertigungstechnik Machine a forger de gros tubes sur un mandrin long
US4947673A (en) * 1989-04-13 1990-08-14 Connell Limited Partnership Removable slide presses
CN101456059B (zh) * 2007-12-12 2011-11-23 中冶京诚工程技术有限公司 专用自由锻造液压机组及其使用方法
CN112024816A (zh) * 2020-09-15 2020-12-04 安徽理工大学 一种用于旋锻成型的弹性送料装置
CN113680941A (zh) * 2021-08-03 2021-11-23 戴颖航 一种双向锤击式锻压机
CN113828728A (zh) * 2021-10-25 2021-12-24 北京机电研究所有限公司 应用于叶片精密锻造自动化生产线的多适应性叶片上料转台
CN114289669A (zh) * 2022-01-12 2022-04-08 襄阳丰正汽车配件制造有限公司 一种汽车轮毂轴管锻造用工作平台及其使用方法
CN114558966A (zh) * 2022-03-10 2022-05-31 江苏扬力锻压机床有限公司 一种细长类零件端部自动化锻造装置以及方法
CN117000937A (zh) * 2023-08-15 2023-11-07 江苏海达管件集团有限公司 一种带颈法兰锻件锻造模具

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DE2225528A1 (de) * 1972-05-26 1973-12-06 Schloemann Ag Vorrichtung zum verschieben und arretieren von schmiedesaetteln an waagerecht arbeitenden schmiedemaschinen
EP0258696B1 (de) * 1986-08-21 1993-07-21 SMS Hasenclever GmbH Schmiedemanipulator
CN113070442B (zh) * 2021-01-22 2022-07-12 重庆金凯特殊钢制品有限公司 一种抗拉高强度勾头锻件锻造装置

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US2114302A (en) * 1936-11-10 1938-04-19 Babcock & Wilcox Tube Company Method of making round billets
US2519900A (en) * 1948-12-10 1950-08-22 Hpm Dev Corp Control circuit for multiple hydraulic press systems
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US2741374A (en) * 1952-11-12 1956-04-10 Salem Brosius Inc Material handling machine
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US3504512A (en) * 1965-02-12 1970-04-07 British Iron Steel Research Apparatus for controlling a manipulator in association with a forging press
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US3473364A (en) * 1966-02-25 1969-10-21 Davy & United Eng Co Ltd Forging
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US3841139A (en) * 1971-03-16 1974-10-15 Langenstein & Schemann Ag Method and apparatus for the forming of a long workpiece
DE2423503A1 (de) * 1974-05-15 1975-11-27 Kautex Werke Gmbh Vorrichtung zum herstellen von hohlkoerpern aus thermoplastischem kunststoff
US3989437A (en) * 1974-05-15 1976-11-02 Kautex-Werke Reinold Hagen Gmbh Moulding apparatus
FR2385466A1 (fr) * 1977-04-01 1978-10-27 Gfm Fertigungstechnik Machine a forger de gros tubes sur un mandrin long
US4947673A (en) * 1989-04-13 1990-08-14 Connell Limited Partnership Removable slide presses
CN101456059B (zh) * 2007-12-12 2011-11-23 中冶京诚工程技术有限公司 专用自由锻造液压机组及其使用方法
CN112024816A (zh) * 2020-09-15 2020-12-04 安徽理工大学 一种用于旋锻成型的弹性送料装置
CN113680941A (zh) * 2021-08-03 2021-11-23 戴颖航 一种双向锤击式锻压机
CN113680941B (zh) * 2021-08-03 2024-01-12 新余市本通特锻有限公司 一种双向锤击式锻压机
CN113828728A (zh) * 2021-10-25 2021-12-24 北京机电研究所有限公司 应用于叶片精密锻造自动化生产线的多适应性叶片上料转台
CN113828728B (zh) * 2021-10-25 2023-10-27 中国机械总院集团北京机电研究所有限公司 应用于叶片精密锻造自动化生产线的多适应性叶片上料转台
CN114289669A (zh) * 2022-01-12 2022-04-08 襄阳丰正汽车配件制造有限公司 一种汽车轮毂轴管锻造用工作平台及其使用方法
CN114558966A (zh) * 2022-03-10 2022-05-31 江苏扬力锻压机床有限公司 一种细长类零件端部自动化锻造装置以及方法
CN114558966B (zh) * 2022-03-10 2024-04-09 江苏扬力锻压机床有限公司 一种细长类零件端部自动化锻造装置以及方法
CN117000937A (zh) * 2023-08-15 2023-11-07 江苏海达管件集团有限公司 一种带颈法兰锻件锻造模具
CN117000937B (zh) * 2023-08-15 2024-01-30 江苏海达管件集团有限公司 一种带颈法兰锻件锻造模具

Also Published As

Publication number Publication date
GB1015711A (en) 1966-01-05
AT260658B (de) 1968-03-11
CH402568A (fr) 1965-11-15
DE1296596B (de) 1969-06-04
SE303078B (xx) 1968-08-12
FR1358689A (fr) 1964-04-17

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