US3393635A - Independently operable press brakes having tandem coupling means - Google Patents

Independently operable press brakes having tandem coupling means Download PDF

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Publication number
US3393635A
US3393635A US575146A US57514666A US3393635A US 3393635 A US3393635 A US 3393635A US 575146 A US575146 A US 575146A US 57514666 A US57514666 A US 57514666A US 3393635 A US3393635 A US 3393635A
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United States
Prior art keywords
rams
machines
machine
ram
synchronism
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.)
Expired - Lifetime
Application number
US575146A
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English (en)
Inventor
Rolland A Richardson
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.)
Pacific Press and Shear Corp
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Pacific Press and Shear Corp
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
Application filed by Pacific Press and Shear Corp filed Critical Pacific Press and Shear Corp
Priority to US575146A priority Critical patent/US3393635A/en
Priority to JP42021330A priority patent/JPS5010032B1/ja
Priority to GB17762/67A priority patent/GB1128716A/en
Priority to BE697303D priority patent/BE697303A/xx
Priority to DE1627855A priority patent/DE1627855C3/de
Priority to SE6908/67A priority patent/SE344170B/xx
Application granted granted Critical
Publication of US3393635A publication Critical patent/US3393635A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam
    • 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
    • B21D5/00—Bending sheet metal along straight lines, e.g. to form simple curves
    • B21D5/02—Bending sheet metal along straight lines, e.g. to form simple curves on press brakes without making use of clamping means

Definitions

  • My invention relates to machines such as press brakes or the like employing rams, and more particularly to the tandem operation of such machines.
  • FIGURE 1 is a schematic view depicting the system of the present invention as applied to a pair of press brakes in tandem
  • FIGURE 2 is a circuit diagram depicting the pertinent portion of the electrical circuit involved in converting press brakes of FIGURE 1 from operation as independent machines to operation in tandem,
  • FIGURE 3 is a front view in elevation of a free coupling between rams to be operated in tandem
  • FIGURE 4 is a side view in elevation of the free coupling illustrated in FIGURE -3.
  • FIGURE 5 is a view depicting an extension of the invention to encompass an indefinite number of machines operating in tandem.
  • Such machine includes a ram 1 reciprocally mounted for cooperation with a suitable die (not shown).
  • the ram is driven or powered by a pair of hydraulic motors 3 and 5, one at each end of the ram and including a cylinder 7 mounted on the frame of the machine, and a piston 9 coupled to the ram at a proximate point thereof.
  • the hydraulic motors are supplied hydraulically by a pair of pumps 11 and 13.
  • the particular hydraulic systems whereby these pumps supply the hydraulic motors are of little moment insofar as the present invention is concerned, but in the specific embodiment illustrated, and for purposes of explaining the present invention, a flow line 15 from each pump is divided into two flow line branches 17 and 19.
  • One branch -17 extends to the upper end of the cylinder of one of the hydraulic motors, and includes a normally closed valve assembly 23 controlled by a normally closed pilot valve 24 which, in turn, is electrically actuated by a solenoid winding 25.
  • this flow line is adapted to be flow connected to tank 26 through a normally closed valve assembly 27 controlled by a normally open pilot valve 29, which in turn, is electrically actuated by a solenoid winding 31.
  • the other branch 19 which leads to the lower end of the cylinder of the other hydraulic motor, includes a normally closed valve assembly 33 controlled by a normally closed pilot valve 35 which is electrically actuated by a solenoid winding 36. Downstream of this valve assembly as viewed from the pump, the branch flow line 19 is adapted to be flow connected to tank 26 through a normally closed valve assembly 37 controlled by a normally open pilot valve 38 which is electrically actuated by a solenoid winding 39.
  • each pump is adapted to be directly flow connected to tank 26 through a normally closed overload relief valve assembly 41, adapted to be opened by a normally open pilot valve 43 which is electrically actuated by a solenoid winding 45.
  • each overload relief valve assembly 41 being a normally open valve, both pumps will be flow connected to tank, thus shunting the hydraulic motors, and the machine under these conditions cannot function.
  • the pilot valves 38 controlling. the valve assemblies 37 in the discharge to tank from the branch lines 19, are de-energized to establish such -flow connection.
  • the pilot valves 43 associated with the overload relief valves 41 are energized to block discharge to tank from the pumps, except under overload conditions. Also, the pilot valves 24 controlling the valve assemblies 23 in the branch lines 17 to the upper ends of the cylinders, are energize-d to unblock these flow lines.
  • each pump will be connected to the upper end of one of the cylinders, with liquid flow provided from the lower end of such cylinder to tank, thereby directing hydraulic power to the upper ends of the pistons, which will cause downward travel thereof and a resulting work stroke of the ram.
  • pilot valves 24 are de-energized to block the lines 17 at these points.
  • pilot valves 29 associated with the valve assemblies 27 which place these lines in flow connection with tank, are de-energized to establish such flow connections.
  • the pilot valves 38 which control discharge to tank from such lines are re-energized to block such discharge.
  • the pilot valves associated with the valve assemblies 33 included in such lines are energized to unblock these lines to establish flow therethrough. The net efiect of all this is to reverse the branch lines 17 and 19 in respect to flow therethrough, with each pump flow connected to the lower end of the other cylinder and establishing connections for an upstroke.
  • pilot valves 43 controlling the overload relief valves 41 are maintained in their energized conditions to permit such upstroke, until such upstroke has been completed, at which time, these pilot valves are tie-energized to place the pumps in flow communication with tank.
  • each machine is controlled through a foot operated switch 49.
  • a foot operated switch 49 in its normal rest position, connects in circuit across a pair of power lines, 51 and 53, the solenoid windings 39 of the valve assemblies 37.
  • the solenoid windings 39 of the valve assemblies 37 When depressed, such foot switch opens this circuit to solenoid windings 39, and closes another circuit through solenoid windings 25 of valve assemblies 23 and solenoid windings of the overload relief valv assemblies 41, all of which winding-s are in parallel.
  • the net result of depressing the foot switch of a machine will therefore be the initiation of a work stroke of the ram of such machine.
  • I provide a pair of relays 55 and 57, one of which includes at least one pair of normally closed contacts 59 and two pairs of normally open contacts 61 and 63, while the other relay includes at least two pairs of normally closed contacts 65 and 67, and one pair of normally open contacts 69.
  • the foot switch circuits of the one machine are so connected through the contacts of these two relays, to the circuits of the other foot switch, that upon energization of the relays, the windings 39, 26 and 45 associated with the operation of one foot switch are connected in parallel with the corresponding windings associated with the other foot switch, whereby all such windings will be under control of the one foot switch.
  • a paralleling connection 71 is installed between the lines leading to the corresponding windings energized through the normally closed contacts of the foot switches, and in this paralleling connection are the normally open contacts 63 of the relay 55.
  • a paralleling connection 73 is installed between the lines leading to the windings which are energized through the normally open contacts of the foot switches, and in this paralleling connection are a pair of normally open contacts 69 associated with the other relay 57.
  • the pair of normally closed contacts 65 are connected in the power lead to the normally closed contacts of the foot switch of the other machine, and a similar pair of normally closed contacts 67 in the line leading from said contacts to the solenoid windings 39 normally connected thereto.
  • a pair of normally closed contacts 59 are connected in the line leading from the normally open contacts of said foot switch, to the parallel connected windings 25 and 45, while a pair of normally opened contacts 61 of relay 55 are connected in circuit between a point 75 of said line to a point on the paralleling connection 73 below the contacts 69.
  • the relays 55 and 57 controlling the aforementioned contacts are connected in parallel across the power leads through a normally open manually controlled switch 79, whereby upon closing of such switch. both machines will be placed under control of one foot switch, this assuring that both machines will start operating simultaneously.
  • a flow line 31 from the output of each pump of a machine joins in a common line 83 which leads to the tank of such machine, and installed in such common line is a continuously variable valve assembly 85 or 86.
  • Such valve assembly may be of the type known as a proportional valve assembly involving a housing 89 with a cylindrical bore in which is slidably installed a spool valve 91 having a control stem 93 emerging from the housing and terminating in a roller 94.
  • the spool is biased in one direction by a spring 95.
  • the lines from both machines include corresponding valve sections of a normally closed multiple valve assembly 99, which is preferably controlled by a solenoid winding 101 and capable of unblocking such lines by energizing the solenoid winding.
  • a check valve 103 in each bleeder flow line from a pump will serve to isolate such pump from the hydraulic system serviced by the other pump in a machine.
  • valve assemblies 85, 86 In controlling the bleeder valve assemblies 85, 86 to bring about synchronization of the rams, such valve assemblies are made responsive to the relative positions of such rams.
  • I provide a cam bar 107 adjacent the proximate edge of one of the rams, such cam bar having an intermediate sloping cam surface 109.
  • both valve assemblies Carried by a bracket affixed to the adjacent ram and extending across the intervening space between the two rams, are the bleeder valve assemblies 85, '86, with their respective surface engaging rollers 94 held in light pressure contact with the cam bar by the valve springs 95-.
  • both valve assemblies are to be thus mounted on the same ram and on a common bracket in line with one another, they are constructed to function in reverse with respect to each other, and are so adjusted that each will shutoff when its roller is midway of the sloping cam surface.
  • one bleeder valve assembly will open when one ram is leading the other rarn, while the other valve assembly will remain closed to permit the other ram to catch up.
  • the bleeder valve assembly associated with the leading ram will gradually approach its shut off position, which it will reach when the roller thereof arrives at the mid-point of the sloping cam surface. At this point, both rams will be in synchronism and will complete the work stroke together.
  • both valve assemblies may be incorporated into a single unit, discharging to the same tank, but in such event, some means, such as an interconnecting pipe between tanks, must be provided to assure that the supply of hydraulic fluid for any individual machine shall not be diminished.
  • I provide a pair of limit switches, one for each machine, and adapt it to prevent operation of the lead machine until the lagging ram of the other machine approaches sufficiently close to synchronism as to enable the bleeder valve assemblies to function and to bring the two rams into synchromism before the work stroke can be completed.
  • I provide another cam surface 111 similar to the first, and preferably on the same cam bar, and on the other ram, in association with the added cam surface, are a pair of micro switches 113, 115.
  • micro switches are preferably slightly displaced vertically with respect to each other, and like the bleeder valves, will preferably be designed to function in reverse, one with respect to the other.
  • rams When the rams are sufficiently close to synchronism that these micro-switches will be symmetrically located with respect to their associated cam surface, both will be open, but each is adapted to close when the ram of the machine with which the switch is electrically associated, is leading to such a degree that the switches are not symmetrically disposed on the cam surface.
  • either micro-switch When closed, either micro-switch will render its associated machine inoperable and thus cause it to stay put until the ram of the lagging machine approaches synchronism with the other ram and the bleeder valves can take over to complete the job of establishing synchronism before completion of a work stroke by both rams.
  • each micro-switch 6 113 controls a circuit through a relay 119, 121 respectively, such circuits including in common, the manually operable switch 79.
  • the solenoid winding 101 which controls the multiple valve assembly 99 in the bleeder lines to the bleeder valves.
  • Each of the micro-switch controlled relays includes a pair of normally closed contacts 125 in circuit with the solenoid windings 45 of the pilot controlled overload release valve assemblies 41 of a machine, which when energized, serve to hydraulically couple both pumps of the pertinent machine to tank, and thereby render that machine inoperable so long as such condition prevails.
  • the micro-switch associated with the relay of the lead machine will close, to energize such relay and cause its normally closed contacts to open and de-energize the solenoid windings 45 of the overload relief valve assemblies associated with the pumps of the lead machine. This will cause such pumps to deliver directly to tank and thus render that machine inoperable so long as such condition exists. Since this machine cannot function, its ram will stay put until the ram of the lagging machine approaches synchronism, which means that the microswitches are riding the cam surface 111 and approaching their position of symmetry with respect to said cam surface.
  • the functioning micro-switch will open its contacts to de-energize its associated relay, which in turn will permit its contacts to close and reenergize the solenoid windings 45.
  • bleeder valves are preferably so mounted that they do not reach the mid-point of their cam surface 109 until just slightly after the functioning micro-switch opens.
  • At least two independently operable machines each having a movable component capable of moving in synchronism with the other, means adapted to apply power simultaneously to said movable components, and control means responsive to a prevailing non-synchronous relationship between said components for unbalancing power to said components in the direction of establishing synchronism, and adapted upon arriving at synchronism, for establishing a synchronous rate of travel of said components.
  • a combination as recited in claim 1 characterized by said movable components including the rams of independently operable press brakes or like machines, said machines being so disposed as to place said rams adjacent one another and substantially end to end in a common plane.
  • a combination as recited in claim 2 characterized by said means for applying power simultaneously to said rams as including a pair of hydraulic motors for each ram, a pump for each said hydraulic motor and having a normally inactive flow connection to said hydraulic motor, and means for simultaneously activating said flow connections to said hydraulic motors.
  • a combination as recited in claim 4 characterized by said flow modulating means including bleeder valve means in said by-pass flow lines, and means controlled by the relative positions of adjacent rams with respect to each other, for adjusting said bleeder valve means in the direction of establishing synchronism between said rams.
  • control means as also including means responsive to an out of synchronous condition beyond a point approaching synchronism, for rendering the lead machine inoperable until the ram of the lagging machine approaches synchronism and permits said bleeder valve means to function.
  • bleeder valve means as including a pair of bleeder valve assemblies mounted one ram adjacent the other ram, said bleeder valve assemblies being operable in reverse with respect to each other and having cam actuable 8 means, and cam means on said other ram with a cam surface symmetrically disposed in contact with said cam actuable means when said rams are in synchronism, and said means for rendering the lead machine inoperable until the lagging machine approaches synchronism includes a pair of microswitches mounted on one ram and cam means on the other ram having a cam surface symmetrically engageable with said micro-switches when said rams are in synchronism.
  • a pair 'of press brakes each having a movable ram, said press brakes being located with their rams disposed in a common plane in slight spaced end to end relationship, and a variable coupling mounted on said rams across the space between them, said coupling being adapted to vary with change in out-of-synchronism relationship between said rams and permitting free and independent movement of each ram for individual machine operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Press Drives And Press Lines (AREA)
US575146A 1966-08-25 1966-08-25 Independently operable press brakes having tandem coupling means Expired - Lifetime US3393635A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US575146A US3393635A (en) 1966-08-25 1966-08-25 Independently operable press brakes having tandem coupling means
JP42021330A JPS5010032B1 (en:Method) 1966-08-25 1967-04-05
GB17762/67A GB1128716A (en) 1966-08-25 1967-04-18 Tandem coupling means for rams of independently operable machines
BE697303D BE697303A (en:Method) 1966-08-25 1967-04-20
DE1627855A DE1627855C3 (de) 1966-08-25 1967-05-05 Gleichlaufsteuerung fur eine Reihe hydraulischer Pressen
SE6908/67A SE344170B (en:Method) 1966-08-25 1967-05-17

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US575146A US3393635A (en) 1966-08-25 1966-08-25 Independently operable press brakes having tandem coupling means

Publications (1)

Publication Number Publication Date
US3393635A true US3393635A (en) 1968-07-23

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Application Number Title Priority Date Filing Date
US575146A Expired - Lifetime US3393635A (en) 1966-08-25 1966-08-25 Independently operable press brakes having tandem coupling means

Country Status (6)

Country Link
US (1) US3393635A (en:Method)
JP (1) JPS5010032B1 (en:Method)
BE (1) BE697303A (en:Method)
DE (1) DE1627855C3 (en:Method)
GB (1) GB1128716A (en:Method)
SE (1) SE344170B (en:Method)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3680339A (en) * 1969-06-25 1972-08-01 Amada Co Ltd Work start synchronizer in plural press brakes coupling operation
US3757641A (en) * 1971-12-15 1973-09-11 Dreis & Krump Manuf Co Control system for synchronizing movement of driven machine members
US3892122A (en) * 1971-08-27 1975-07-01 Mannesmann Meer Ag Hydraulic presses
FR2507941A1 (fr) * 1981-06-19 1982-12-24 Mercier J Perfectionnements aux machines-outils, en particulier aux machines a cintrer
FR2641212A1 (fr) * 1988-12-29 1990-07-06 Amada Co Ltd Machine a cintrer
US5573366A (en) * 1992-03-30 1996-11-12 Meijer; Sjoerd Hydraulic device with synchronously operating jacks
US5636432A (en) * 1993-10-20 1997-06-10 General Electric Company Tandem press system for manufacture of stator and rotor cores
NL1004820C2 (nl) * 1996-12-18 1997-12-23 Delem B V Werkwijze voor het besturen van een buigpers en buigpers voorzien van besturingsmiddelen voor het besturen van de buigpers volgens de werkwijze.
EP3612328A4 (en) * 2017-04-21 2020-02-26 Durmazlar Makina Sanayi Ve Ticaret Anonim Sirketi SINGLE-HOUSED TANDEM PRESS

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8513955D0 (en) * 1985-06-03 1985-07-03 Samco Strong Ltd Cutting press

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US604364A (en) * 1898-05-24 -brown
US722676A (en) * 1901-01-04 1903-03-17 Peete B Clarke Compensating valve for hydraulic rams.
US1900050A (en) * 1931-02-24 1933-03-07 Hydraulic Press Mfg Co Hydraulic press platen travel equalizer
US1947253A (en) * 1932-06-29 1934-02-13 Waterbury Tool Co Reciprocating drive mechanism
US2400685A (en) * 1941-12-18 1946-05-21 Baldwin Locomotive Works Equalizing system
US2764869A (en) * 1954-08-19 1956-10-02 Origins Inc Means for synchronizing the travel of two or more traveling work elements
US2851860A (en) * 1954-07-15 1958-09-16 American Steel Foundries Movement coordinating device
US3199443A (en) * 1964-03-26 1965-08-10 Danly Mach Specialties Inc Automatic transfer mechanism for press line
USRE26236E (en) * 1967-07-18 Level control for press brakes and the like

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US604364A (en) * 1898-05-24 -brown
USRE26236E (en) * 1967-07-18 Level control for press brakes and the like
US722676A (en) * 1901-01-04 1903-03-17 Peete B Clarke Compensating valve for hydraulic rams.
US1900050A (en) * 1931-02-24 1933-03-07 Hydraulic Press Mfg Co Hydraulic press platen travel equalizer
US1947253A (en) * 1932-06-29 1934-02-13 Waterbury Tool Co Reciprocating drive mechanism
US2400685A (en) * 1941-12-18 1946-05-21 Baldwin Locomotive Works Equalizing system
US2851860A (en) * 1954-07-15 1958-09-16 American Steel Foundries Movement coordinating device
US2764869A (en) * 1954-08-19 1956-10-02 Origins Inc Means for synchronizing the travel of two or more traveling work elements
US3199443A (en) * 1964-03-26 1965-08-10 Danly Mach Specialties Inc Automatic transfer mechanism for press line

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3680339A (en) * 1969-06-25 1972-08-01 Amada Co Ltd Work start synchronizer in plural press brakes coupling operation
US3892122A (en) * 1971-08-27 1975-07-01 Mannesmann Meer Ag Hydraulic presses
US3757641A (en) * 1971-12-15 1973-09-11 Dreis & Krump Manuf Co Control system for synchronizing movement of driven machine members
FR2507941A1 (fr) * 1981-06-19 1982-12-24 Mercier J Perfectionnements aux machines-outils, en particulier aux machines a cintrer
FR2641212A1 (fr) * 1988-12-29 1990-07-06 Amada Co Ltd Machine a cintrer
US5573366A (en) * 1992-03-30 1996-11-12 Meijer; Sjoerd Hydraulic device with synchronously operating jacks
US5636432A (en) * 1993-10-20 1997-06-10 General Electric Company Tandem press system for manufacture of stator and rotor cores
US5915750A (en) * 1993-10-20 1999-06-29 General Electric Company Method of manufacturing stator and rotor cores
NL1004820C2 (nl) * 1996-12-18 1997-12-23 Delem B V Werkwijze voor het besturen van een buigpers en buigpers voorzien van besturingsmiddelen voor het besturen van de buigpers volgens de werkwijze.
EP3612328A4 (en) * 2017-04-21 2020-02-26 Durmazlar Makina Sanayi Ve Ticaret Anonim Sirketi SINGLE-HOUSED TANDEM PRESS

Also Published As

Publication number Publication date
JPS5010032B1 (en:Method) 1975-04-17
DE1627855C3 (de) 1973-11-08
SE344170B (en:Method) 1972-04-04
DE1627855A1 (de) 1969-10-30
BE697303A (en:Method) 1967-10-02
DE1627855B2 (de) 1973-04-05
GB1128716A (en) 1968-10-02

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