US3841125A - Control device with hydraulic synchronising control for forging machines - Google Patents

Control device with hydraulic synchronising control for forging machines Download PDF

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Publication number
US3841125A
US3841125A US00333378A US33337873A US3841125A US 3841125 A US3841125 A US 3841125A US 00333378 A US00333378 A US 00333378A US 33337873 A US33337873 A US 33337873A US 3841125 A US3841125 A US 3841125A
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United States
Prior art keywords
forging
cylinder
piston
pump
operating
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Expired - Lifetime
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US00333378A
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English (en)
Inventor
R Guse
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Maschinenfabrik Sack GmbH
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Maschinenfabrik Sack GmbH
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Publication of US3841125A publication Critical patent/US3841125A/en
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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
    • 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
    • B21J7/28—Drives for hammers; Transmission means therefor for power hammers 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
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/46—Control devices specially adapted to forging hammers, not restricted to one of the preceding subgroups

Definitions

  • The'invention relates to a control'device with hydraulic synchronising control for forging machines having a plurality of pressure cylinders which are associated with forging saddles surrounding the workpiece,
  • the drive proper of the operating cylinder of the forging machine consists of piston pumps disposed in pairs for respective pairs of" forging saddles, these pumps having pistons of different diameters, the pistons of larger'diameter serving for loading the pressure side and the pistons of smaller diameter serving for loading the retraction .side of the operating pistons.
  • the preselected nominal values can be attained during forging by the control pump in conjunction with the electrical control but the expense involved is very high, since, apart from the control pumps, which have a reversible feed direction and which are therefore very expensive, and the additional filling pumps for loading the retraction side of the operating cylinders, an overpressure valve must additionally be present in each system. Furthermore, in the known machine the forging saddles cannot be stopped without the driving arrangement being disconnected. .Although a certain interchange of pressure liquid is effected by the control pump in the event of leakage lossesthis interchange is so small that an effective cooling of the operating liquid is not obtained-The most important disadvantage of the known machine, however, is that the stroke posifor forging machines'of the kind referred to above,.
  • the hydraulic servo-device comprises, for each forging saddle, a reversible compensating cylinder which is connected to the connecting pipe which extends'between the pressure side of the operating cylinder and the pump cylinder.
  • a reversible compensating cylinder can be produced considerably more economically than a'control pump with a two directional feed and at the same time the advantage is ob-.
  • the compensating cylinder comprises an adjustable piston which separates twoworking spaces from one another, and which has a piston rod which extends into a control chamber connected to the connect ing pipe.
  • the quantity of liquid located in the connecting pipe between the operating cylinder and the pump cylinder can be controlled very accurately by means of this piston rod, in that the piston carrying the piston rod is adjusted appropriately,'so that either pressure liquid is pressed into the connecting pipe or a larger space is made available in the control space for the quantity of liquidlocated in' the pipe by a return of the piston rod so that a corresponding relief occurs.
  • the operating piston is displaced into its new stroke position under the effect of the substantially constant retraction force. 1 v
  • the control of the compensating cylinder can-be realised. very simply in that the two operating spaces thereof can be selectively connectedto a control pump by means of a control valve.
  • the piston can thus be ad- 1 justed within the compensatingcylinder inaccordance with the desired pressure adjustment in the connecting pipe-Preferably the control valve is electrically connected to the controller, which in turn is connected directly'to the transmitter disposed at the forging saddle. Owing to this direct sensing of the position of the forging saddle, and exact displacement of the servo valve is ensuredby'means of the electrical control and thus a change of the pressure'means supply in the connect ing pipe is ensured which depends exactly upon the forging saddle, i.e., the forging-dimension.
  • the transmitter co-operates with a pinion which engages in a tooth rack located at the free end of a lever attached to the pivot pin -of the forging saddle.
  • the controller may be connected to afurther actual value transmitter which co-operates with a position indicator which is disposed on a further piston rod located opposite the piston rod of the compensating cylinder'and projecting from the latter.
  • This actual value transmitter constitutes a position monitor for the piston in the compensating cylinder and thus acts as a correcting device for incorrect quantities.
  • the controller moreover, is connected'to, further.
  • the transmitters i.e. to a transmitter indicating the forward end position of the driving arrangement, constructed as' a crankdrive, and a transmitter determining the liquid pressure in the connecting pipe between the operating cylinder and the pressure cylinder.
  • the first mentioned transmitter ensures that the comparison between the nominal value and the actual value takes place only when the crank drive has attained its forward end positon, that is to say the full pressure is present in the connecting pipe and thus the forging saddle is located in its farthest possible forging position, whereas, the second transmitter can deliver the impulse for the servo valve only, when the pressure in'the connecting pipe is low, i.e., has dropped substantially to zero, since only then a simple displacement of the piston in the compensating cylinder is possible, because otherwise the piston would have to be displaced against the high pressure in the connecting pipe.
  • FIG. 1 is a diagrammatic representation of a forging saddle and associated hydraulic control device of a forging machine having, for example, four forging saddles which are displaced by 90 relatively to each other and which enclose on all sides a workpiece to be deformed, the other forging saddles and their associated control devices being constructed in an identical manner.
  • a forging saddle l is pivotally mounted on a pin 2 of a machine frame (not illustrated) of a forging machine, the axis of the pin 2 being parallel to the feed direction of a workpiece and extending perpendicular to the plane of the drawing.
  • the forging saddle 1 is actuated by a hydraulic piston and cylinder drive comprising an operating piston 4 displaceable in a driving cylinder 3'and engaging the rear side of the forging saddle l.
  • the piston 4 is limited in itsrearward end position, illustrated in the drawing, by an adjustable abutment device 5.
  • the abutment device 5 consists of a doubleacting piston and cylinder device having a hydraulic cylinder 6 and a piston 7 which is displaceable in the cylinder 6 and has two oppositely directed piston rods 8 and 9.
  • the lower piston rod 8 projects from the hydraulic cylinders 6 to form the abutment proper since the operating piston 4 rests in its rearward end position on the piston rod 8.
  • Non-return valves 13, 14, which permit fluid flow into the hydraulic cylinder 6 are disposed in two control pipes ll, 12. connected to the hydraulic cylinder 6 and to a source (not shown) of fluid under pressure.
  • a piston rod 16 is connected to a piston displaceable in a retraction cylinder 17 engages'a bearing eye 15 of the-forging saddle l, the retraction cylinder 17 serving to return the operating piston 4 after each forging stroke into its starting position in which the piston abuts the pistonrod 8 of the abutment device 5.
  • the retraction cylinder 17 is connected through a feed pipe 18 to a source 19 of fluid under pressure, which maintains a constant pressure in the retraction cylinder 17.
  • the operating piston 4 of the operating cylinder 3 can be subjected to fluid pressure by a pump cylinder 22 to which it is connected through a connecting pipe 21.
  • a piston 23 which is displaceably mounted in the cylinder 22 is attached to a yoke 24 which is connected to a driving arrangement 26 by means of a connecting rod 25.
  • the driving arrangement 26 consists of a single throw crank drive which is driven through a gear (not shown) by a motor (not shown).
  • the crank drive 26 comprises a rotating shaft 27attached to a control element 28, the purpose of which is described in detail below.
  • a pressure store 31 isconnected to a branch pipe 29 of the connecting pipe 21, and anon-"return valve 32, which is controllable by the crank drive 26 and which opens towards the connecting pipe 21, is disposed between the pressure store 31 and connecting pipe 21.
  • a further branch pipe 33 of the connecting pipe 21 terminates in a control space 34 of a compensating cylinder 35.
  • the compensating cylinder 35 accommodates a displaceable piston 36 with oppositely directed piston rods 37 and 38 attached thereto.
  • the lower piston rod 38 extends to the exterior of the compensating cylinder 35 and the other piston rod 37 projects into the control] space 34 and seals the latter in a fluid tight manner from the adjacent operating space of the compensating cylinder 35.
  • the two operating chambers of the compensating cylinder 35 are connected through respective control pipes 39, 41 to a servo-valve 42 .which is constructed as a multiple path valve and which is connected to a fluid tank 43 and a control pump 44.
  • the servo-valve 42 is controllable by means of a controller-46 which can deliver an impulse thereto via an electrical conductor 45 dependently upon an actual valve/nominal valve comparison.
  • the controller 46 is connected to a transmitter 48 which co-operates with a pinion 49 engaging a toothed rack 51.
  • the rack 51 is disposed at the free end of a lever 52 the other end of which is rigidly connected to the pin 2 of the forging saddle l.
  • a conductor 53 leads from the controller 46 to a further actual value transmitter 54 which co-operates with a position indicator 55 disposed on the free end of the piston rod 38 projecting from the compensating cylinder 35.
  • Further conductors 56, 57, lead to further actual value transmitters 58 and 60.
  • the actual value transmitter 58 delivers an impulse to the controller 46 when the crank drive 26 assumes its forward end posi' tion, whereas the actual value transmitter 60 delivers an impulse to the controller 46' when the pressure in the connecting pipe 21 is low or nearly zero.
  • the crank drive 26 starts its return, so thatthe piston 23 is moved back again towards the right.
  • the fluid pressure prevailing in the pump cylinder 22 as well as in the connecting pipe 21 is thereby reduced so that the operating piston 4 can be moved back by the retraction cylinder 17 engaging the forging saddle 1.
  • the operating piston 4 rests on the piston rod 8 of the abutment device 5.
  • the individual forging saddles of the forging machine thus move towards and away from each other with a sinosoidal speed characteristic and thereby effect the deformation of the workpiece.
  • an impulse is sent by the actual value transmitter 58 and the conductor 56 to the controller 46 when the crank drive 26 is located in its forward end position in which maximum pressure prevails in the connecting pipe and the operating piston 4 is in its extended forging position.
  • the measurement is then made in this position by the actual value transmitter 48.
  • the servovalve 42 can be controlled by the controller 46 only when an impulse is delivered through the conductor 57 to the controller 46 by the other actual value transmitter 59 which is controlled by the control element 28 on the shaft 27 of the crank drive 26, the impulse indicating that the pressure in the connecting pipe 21 is nearly zero.
  • the pressure fluid in the connecting pipe 21 the operating cylinder 3 and the pump cylinder 22 can be changed by the pressure store 31 so that undesirable heating of the pressure liquid is avoided.
  • a control device with hydraulic synchronising control for a forging machine having a plurality of forging saddles which act upon a workpiece to reduce the cross section thereof by lateral pressure respective operating piston and cylinder devices associated with the forging saddles, each piston being subjected on the one hand to the effect of a substantially constant return force and on the other hand being connected to a respective pump cylinder, a driving arrangement for periodically reciprocating the pistons of the pump cylinders, a transmitter which measures the actual position of each forging saddle, an electrical controller for comparing the measured values with a nominal value, a controllable filling pump associated with each; forging saddle and adapted to be controlled by the electrical controller to adjust the dead position of the operating cylinders so as to correspond to the farthest extension of each forging saddle, said filling pump being connected to the conduit system associated with the respective op erating cylinder and effecting the variation of the filling capacity in the conduit system in response to a comparison between the measured value and the nominal value only when the pressure in the conduit system is approximately zero upon
  • a control device wherein the two operating chambers of the compensating cylinder are selectively connectable to a control pump by a multiple path control valve actuated by the controller.
  • Acontrol device wherein the transmitter which measures the actual position of arespective forging saddle cooperates with a pinion which engages into a toothed rack secured to the free end of a lever attached to a pivot pin mounted on the forging saddle.
  • a control device wherein the controller is electrically connected to a further actual value transmitter which co-operates with a position indicator which is disposed on a further piston rod located opposite the piston rod determining the filling capacity of the compensating cylinder and projecting from the latter.
  • a control device wherein the controller is electrically connected to a transmitter which indicates the pump cylinder rear dead positions of the driving arrangement constructed as a crank drive.
  • a control device according to claim 5 wherein the controller is electrically connected to a transmitter which determines the fluid pressure in the connecting pipe between the operating cylinder and the pump cylinder.
  • connection pipe is adapted to be connected to'a pres-' sure store by a nonretum valve which opens towards the connecting pipe and is controllable by the crank drive.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Control Of Presses (AREA)
US00333378A 1972-02-18 1973-02-16 Control device with hydraulic synchronising control for forging machines Expired - Lifetime US3841125A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2207717A DE2207717C3 (de) 1972-02-18 1972-02-18 Steuereinrichtung mit hydraulischer Gleichlaufsteuerung für Schmiedemaschinen

Publications (1)

Publication Number Publication Date
US3841125A true US3841125A (en) 1974-10-15

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US00333378A Expired - Lifetime US3841125A (en) 1972-02-18 1973-02-16 Control device with hydraulic synchronising control for forging machines

Country Status (7)

Country Link
US (1) US3841125A (enrdf_load_stackoverflow)
JP (1) JPS5725294B2 (enrdf_load_stackoverflow)
AT (1) AT322327B (enrdf_load_stackoverflow)
DE (1) DE2207717C3 (enrdf_load_stackoverflow)
FR (1) FR2172431B3 (enrdf_load_stackoverflow)
GB (1) GB1365654A (enrdf_load_stackoverflow)
IT (1) IT979232B (enrdf_load_stackoverflow)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4831864A (en) * 1986-01-02 1989-05-23 Sms Hasenclever Machinenfabrik Gmbh Forging machine
US4905495A (en) * 1988-01-07 1990-03-06 Pahnke Engineering Gmbh & Co. Kg Long forging machine for the forging of round or sharp-edged bars
US5231859A (en) * 1992-03-03 1993-08-03 Trimble House Corporation Fluting machine
US5732588A (en) * 1994-12-24 1998-03-31 Pahnke Engineering Gmbh & Co. K.G. Double press
US5894755A (en) * 1996-09-17 1999-04-20 Gfm Holding Aktiengesellschaft Forging machine
EP1093871A3 (de) * 1999-10-07 2002-06-26 GFM Beteiligungs- und Management GmbH & Co KG Schmiedemaschine

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3607737C1 (de) * 1986-03-08 1987-10-29 Pahnke Eng Gmbh & Co Kg Hydraulisch angetriebene Schmiedemaschine
CN109248981B (zh) * 2018-10-16 2024-05-24 南京迪威尔高端制造股份有限公司 蓄势器流量和压力动态补偿控制系统

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3031903A (en) * 1958-05-12 1962-05-01 Schloemann Ag Control of hydraulic forging presses
US3196647A (en) * 1960-07-21 1965-07-27 Schloemann Ag Control of hydraulic forging presses
US3222912A (en) * 1963-09-09 1965-12-14 Cincinnati Milling Machine Co Swaging machine with adjustable stroke
US3224244A (en) * 1963-05-20 1965-12-21 Kralowetz Bruno Swaging machine
US3246502A (en) * 1960-04-12 1966-04-19 Brignoli Silvio Speed hammer swaging machine
US3415105A (en) * 1966-04-19 1968-12-10 Bliss E W Co Apparatus for forming sheet metal containers
US3478565A (en) * 1966-09-30 1969-11-18 Sack Gmbh Maschf Forging machine
US3613432A (en) * 1968-12-02 1971-10-19 Sack Gmbh Maschf Forging machine
US3657916A (en) * 1969-02-20 1972-04-25 Sack Gmbh Maschf Forging machine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3031903A (en) * 1958-05-12 1962-05-01 Schloemann Ag Control of hydraulic forging presses
US3246502A (en) * 1960-04-12 1966-04-19 Brignoli Silvio Speed hammer swaging machine
US3196647A (en) * 1960-07-21 1965-07-27 Schloemann Ag Control of hydraulic forging presses
US3224244A (en) * 1963-05-20 1965-12-21 Kralowetz Bruno Swaging machine
US3222912A (en) * 1963-09-09 1965-12-14 Cincinnati Milling Machine Co Swaging machine with adjustable stroke
US3415105A (en) * 1966-04-19 1968-12-10 Bliss E W Co Apparatus for forming sheet metal containers
US3478565A (en) * 1966-09-30 1969-11-18 Sack Gmbh Maschf Forging machine
US3613432A (en) * 1968-12-02 1971-10-19 Sack Gmbh Maschf Forging machine
US3657916A (en) * 1969-02-20 1972-04-25 Sack Gmbh Maschf Forging machine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4831864A (en) * 1986-01-02 1989-05-23 Sms Hasenclever Machinenfabrik Gmbh Forging machine
US4905495A (en) * 1988-01-07 1990-03-06 Pahnke Engineering Gmbh & Co. Kg Long forging machine for the forging of round or sharp-edged bars
US5231859A (en) * 1992-03-03 1993-08-03 Trimble House Corporation Fluting machine
US5732588A (en) * 1994-12-24 1998-03-31 Pahnke Engineering Gmbh & Co. K.G. Double press
US5894755A (en) * 1996-09-17 1999-04-20 Gfm Holding Aktiengesellschaft Forging machine
EP1093871A3 (de) * 1999-10-07 2002-06-26 GFM Beteiligungs- und Management GmbH & Co KG Schmiedemaschine

Also Published As

Publication number Publication date
DE2207717A1 (de) 1973-08-23
JPS5725294B2 (enrdf_load_stackoverflow) 1982-05-28
JPS4893564A (enrdf_load_stackoverflow) 1973-12-04
FR2172431A1 (enrdf_load_stackoverflow) 1973-09-28
IT979232B (it) 1974-09-30
DE2207717C3 (de) 1975-10-16
GB1365654A (en) 1974-09-04
AT322327B (de) 1975-05-12
DE2207717B2 (enrdf_load_stackoverflow) 1975-02-13
FR2172431B3 (enrdf_load_stackoverflow) 1976-02-13

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