US3756145A - Hydraulic press - Google Patents

Hydraulic press Download PDF

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Publication number
US3756145A
US3756145A US00191417A US3756145DA US3756145A US 3756145 A US3756145 A US 3756145A US 00191417 A US00191417 A US 00191417A US 3756145D A US3756145D A US 3756145DA US 3756145 A US3756145 A US 3756145A
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United States
Prior art keywords
pressing
press
compression chamber
surface area
effective surface
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Expired - Lifetime
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US00191417A
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English (en)
Inventor
A Amacker
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AMACKER AND SCHMID AG
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AMACKER AND SCHMID AG
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    • 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
    • B30B1/32—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 plungers under fluid pressure

Definitions

  • Cl means are provided for admitting pressure fluid in a 1 1 Field Sfllrch 269 269 first phase of each pressing operation, into the pressing 450 unit having the smaller effective surface area to effect the approach stroke, and for then locking this unit and 1 1 References Cited admitting pressure fluid into the pressing unit having UNITED STATES PATENTS the greater effective surface area to effect the pressing 1,062,289 5 1913 Maxwell 91/167 x Stroke- B a high Speed during the aPProach Stroke 512,790 1/1894 Bachman 100 269 R x and a high POWer during the Pressing Stroke y thus 1,955,278 4/1934 Ferris et a1...
  • 100/269 R X be achieved with a relatively reduced output from the 2,786,409 3/1957 Claire 100/269 R X pressure fluid pumping means.
  • a pressure fluid is fed to the cylinder to displace the piston.
  • the maximum force which the piston can exert is proportional to the pressure of the fluid and to the effective surface area of the piston.
  • the maximum volume of fluid to be fed per unit of time is determined as a product of the surface area of the piston and the rate of stroke required.
  • the pump used for the fluid feed must be designed for an output equal to the product of the volume of fluid per unit time multiplied by pressure, or rate of stroke multiplied by maximum force required.
  • presses which are required to apply a powerful force over a relatively short pressing stroke only, but are to be able to perform a larger degree of approach travel under much lower power.
  • Known hydraulic presses are not satisfactory in uses of this kind because the pump for the pressure fluid has to be designed for an output which is very much greater than that which is necessary during the approach stroke (with its requirement of small power only) and also very much greater than the output required during a large pressure pressing stroke (with the requirement of small length and rate of stroke).
  • the subject of the present invention is a hydraulic press comprising two hydraulic pressing units arranged in tandem between a machine frame and a movable pressing member and each comprising a compression chamber and a transfer member which closes the compression chamber and is movable relatively to a fixed wall thereof, characterized by the fact that to cater for the performance of an approach stroke at high speed and under low power and a pressing stroke at a lower speed but greater power in each pressing operation with a reduction in output required from a hydraulic pumping means, the effective surface area of the transfer member defming the compression chamber is substantially greater, and preferably at least five times greater, in one of the pressing units than in the other pressing unit.
  • pressure fluid can be supplied to the pressing unit with the transfer member of smaller effective surface area.
  • the compression chamber of this pressing unit can then be closed and as a result the transfer member concerned will, in practice, be locked to the fixed wall.
  • the actual pressing stroke can then be performed under the agency of the other pressing unit, the effective surface area of the transfer member of this unit being dimensioned in accordance with the maximum pressing force required.
  • the supply of pressure fluid to the two pressing units can of course be automatically controlled very simply, as is explained below.
  • the pressing units may each comprise a piston which is movable in a cylinder and constitutes the transfer member. It is possible, however, to use a diaphragm instead of a piston as a transfer member, at least in the case of that unit which has the transfer member with the larger effective surface area.
  • Hydraulic presses with two pressing units arranged in tandem are per se known. In these, however, the two pressing units have effective pressure surfaces of approximately the same size and they are used for purposes which are completely different from those visualized in the present invention.
  • Swiss Patent Specification No. 409,634 one pressing unit is only operated when there is a change of tool, with the object of varying the length of the press plunger.
  • British Patent Specification No. 1,086,477 the second pressing unit is not disposed between the first pressing unit aud the movable pressing member, but between the first unit and a table which carries the workpiece, the aim being to apply this resiliently against a workpiece.
  • the press illustrated in the drawing comprises a frame 1 supporting a lower, fixed, press platen 2 with which cooperates an upper movable platen 3.
  • Platen 3 is held on a press ram 4 which is vertically displaceable in frame 1.
  • Platen 3 and ram 4 together form a pressing member.
  • the frame 1 takes the form of a thick solid steel plate which is such that no thickening thereof is necessary at that part where the press ram is guided through the plate. This means that the fabrication of the plate can be carried out simply and inexpensively.
  • the press illustrated may for example be intended for glueing of workpieces. This means that it must exert a powerful force on the workpiece but the latter will be compressed only to a very small extent. This means that there must be only a small length of stroke under heavy pressure. In contrast, to cater for a change in workpiece, provision must be made for a comparatively long approach stroke of the press platen 3 and press ram 4, under very small force.
  • the press has two pressing units which are operable in tandem, and one of these is intended for operation under relatively small power but with a relatively long stroke, namely to perform the aforemen tioned approach stroke.”
  • this first pressing unit can, in practice, be locked in any chosen position and the actual pressing stroke performed by the second pressing unit.
  • the first pressing unit referred to comprises a cylinder 5 in which is displaceable a piston 6 formed as part of the upper end of the press ram 4. Surrounding piston 6 in cylinder 5 is a sealing ring 7 which is pressed between two slip rings 8.
  • the inner chamber of cylinder 5 closed by piston 6 represents the compression chamber 9 which is connected through a duct with a shutoff valve 10.
  • This valve 10 to which pressure fluid can be fed through a conduit 1 1 is attached directly to cylinder 5 so that high pressures which may be set up in compression chamber 9, as described below, can not become effective in feed ducts and discharge ducts.
  • the second pressing unit which is designed only to produce the short actual pressing stroke, in lieu of a pressing piston has a diaphragm 12 as a transfer member.
  • a pressure chamber 14 is incorporated between this diaphragm 12 and a fixed plate 13 which is rigidly connected to the frame 1 of the machine through posts la. Pressure fluid can be introduced into chamber 14 through a conduit 15.
  • a diaphragm plate 16 is arranged as a thrust transmission member between the free upper surface of diaphragm l2 and the upper side of cylinder of the first pressing unit.
  • An automatic control unit 21 is used in performance of a pressing operation. This first connects a pump 23 through a valve 22 to the conduit 24 and connects this conduit through a valve 25 with conduit 11. The shutoff valve is simultaneously opened. Pump 23 therefore pushes pressure fluid into compression chamber 9 of the first pressing unit and forces piston 6, and consequently ram 4 and platen 3, downwards. A small force only is required in this first stage of the operation so that, with an effective surface area of piston 6 of say about 50 cm, the maximum pressure output of the pump, which may be for example about 20 atmospheres, is not fully utilized. In this way an approach stroke of press platen 3, of up to about 3 cm for example, can be brought about, In which case a volume of pressure fluid of a maximum of 50 cm X 3 cm 150 cm would be needed.
  • control unit 21 is so designed for this purpose that it responds to a pressure increase in chamber 9 when platen 3 meets resistance.
  • This control unit 21 may for instance be connected to a manometer or pressure switch (not shown) which is coupled to compression chamber 9.
  • control unit 21 When control unit 21 has detected contact between platen 3 and the workpiece, it first closes valve 10 and changes over control valve 25. Closure of valve 10 has a practical effect of locking piston 6 to cylinder 5 and this, as mentioned above, is possible at any position of piston 6 relatively to cylinder 5.
  • the control unit the opens valve 26 so connecting conduit 24 with conduit and allowing pressure fluid to flow into the compression chamber 14 of the second pressing unit.
  • the area of the surface of diaphragm l2 defining compression chember 14 is substantially greater than the effective piston surface area of piston 6 of the first pressing unit.
  • the diaphragm 12 may have an effective surface area of about 1600 cm.
  • the pressure fluid can drive down the diaphragm 12, and thus through diaphragm plate 16 and cylinder 5 the press ram 4 connected to the latter, with a force of up to about 30,000 kg.
  • With a very small pressing stroke in the order of 1 mm the volume of pressure fluid required for this is of the same order as that required previously for the approach stroke.
  • very high pressures are set up in compression chamber 9 when forces of this order are to be transmitted. For example up to somewhere about 30,000 50 600 atmospheres or more. These pressures are readily tolerable, however, when the valve 10 is arranged directly on cylinder 5 as described. In addition it should be noted that valve 10 is not operated at these high transmission pressures.
  • conduit 11 is connected through the valve 25 and a discharge conduit (not shown) to a sump 27.
  • control unit 21 When the pressing operation has been performed, which may be determined for example by the expiry of a predetermined time interval from the opening of valve 26, the control unit 21 operates valve 26 to separate conduit 15 from conduit 24 and connect it through an overflow conduit (not shown) to sump 27. Shortly thereafter, when the transmission pressure in chamber 9 has dissipated, control unit 21 opens shut-off valve 10. Springs 17 return ram 4 to the starting position, the pressure fluid from chambers 4 and 9 discharging into the sump, the valve 25 being changed over.
  • One or more bolts 19 may additionally be secured to cylinder 5 and arranged to enter openings in plate 18 attached to press ram 4 so as to limit the stroke of ram 4 relatively to cylinder 5. Furthermore the lower ends or heads of bolts 19 are guided in holes in a plate 20 rigidly connected to frame 1. In this way the bolts 19 inhibit rotation of cylinder 5. Projecting lugs 16a are provided at the periphery of diaphragm plate 16 for cooperation with the upper ends of posts 1a to limit the travel of diaphragm 12.
  • valves 22, 25 and 26 may be combined in a single control member.
  • the two valves 10 and 25 could be replaced by a single valve.
  • a simple pressure relief valve could be employed in a more modest and less expensive construction.
  • control unit 21 may be so designed that it initiates the changeover from the first to the second pressing unit when a predetermined volume of fluid has passed into the compression chamber 9 or when the piston 6 has moved a predetermined distance relatively to cylinder 5, or again if a predetermined period of time has elapsed since pressure fluid was first admitted to compression chamber 9.
  • the automatic control described above could be completely dispensed with and the supply of pressure fluid to compression chambers 9 and 14 be manually controlled by the operation of appropriate valves.
  • a press having a high speed, low power approach stroke and a higher power, lower speed pressing stroke which comprises:
  • a first pressing unit comprising a first compression chamber which is displaceable relative to said stationary machine frame and a first transfer member moveable in said first compression chamber having a first effective surface area and connected at one end to said pressing member;
  • a second pressing unit comprising a second compression chamber which is sealed off from said first compression chamber, having a wall which is rigidly secured to said stationary machine frame, and second transfer means moveable in said second compression chamber having a second effective surface area, said first compression chamber being rigidly secured to said second transfer means and operative to move with said second transfer means, said second effective surface area being greater than said first effective surface area;
  • means for supplying and withdrawing pressurized fluid to said compression chambers including means for fluidly locking said first transfer member at any point of its travel during said approach stroke, said first transfer member, when fluidly locked, being operative to move with said first compression chamber.
  • said means for supplying and withdrawing pressurized fluid comprise a plurality of pressure fluid conduits to said compression chambers, at least one valve in each of said pressure fluid conduits, and a control unit for operating said valves, said control unit being operable first to open at least one valve in a conduit to said first pressing unit, to close this valve again after an approach stroke 6 has been carried out by said pressing member, and then to open a valve in a conduit to said second pressing unit.
  • a press as claimed in claim 4, wherein at least one spring is provided between a part: rigidly connected to said pressing member and a part rigidly connected to said machine frame for the purpose of returning the pressing member to its starting position.
  • a press as claimed in claim 4 wherein said at least one valve to said conduit to said first pressing unit may be closed when said first transfer member is at any point of its travel during said approach stroke.
  • said first compression chamber comprises a cylinder in which is displaceably arranged said first transfer member, said first transfer member being a press piston.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)
US00191417A 1970-12-02 1971-10-21 Hydraulic press Expired - Lifetime US3756145A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1781070A CH517586A (de) 1970-12-02 1970-12-02 Hydraulische Presse

Publications (1)

Publication Number Publication Date
US3756145A true US3756145A (en) 1973-09-04

Family

ID=4428259

Family Applications (1)

Application Number Title Priority Date Filing Date
US00191417A Expired - Lifetime US3756145A (en) 1970-12-02 1971-10-21 Hydraulic press

Country Status (7)

Country Link
US (1) US3756145A (de)
AT (1) AT309224B (de)
CH (1) CH517586A (de)
DE (1) DE2147306A1 (de)
FR (1) FR2117059A5 (de)
GB (1) GB1339934A (de)
IT (1) IT939034B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3940930A (en) * 1975-01-20 1976-03-02 Package Machinery Company Hydraulic system for injection molding machine
US3982417A (en) * 1975-01-20 1976-09-28 Promecam Sisson-Lehmann Device for controlling a movable member on a machine tool
US4214357A (en) * 1978-02-16 1980-07-29 Purpose Engineers Limited Punching device
WO1987002309A1 (en) * 1985-10-18 1987-04-23 Universal Engineering Development Co. Pty. Ltd. Improvements to punch presses
US20040244617A1 (en) * 2003-06-03 2004-12-09 Reefdale Pty Ltd Transfer heat press
WO2017129397A1 (de) * 2016-01-29 2017-08-03 Siempelkamp Maschinen- Und Anlagenbau Gmbh Presse zum herstellen eines bauteils aus einem faserverbundwerkstoff

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE468177B (sv) * 1990-09-18 1992-11-16 Volvo Ab Laasbar kulled
CN114673703A (zh) * 2022-03-23 2022-06-28 北京天玛智控科技股份有限公司 截止阀

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US512790A (en) * 1894-01-16 Cotton-press
US1062289A (en) * 1911-01-09 1913-05-20 Liquid Forged Steel Company Apparatus for making castings.
US1937007A (en) * 1930-12-30 1933-11-28 Maschf Augsburg Nuernberg Ag Hydraulic press control mechanism
US1955278A (en) * 1930-02-24 1934-04-17 Oilgear Co Hydraulic press
US2786409A (en) * 1953-06-15 1957-03-26 Robert W Claire Pneumatic dental press
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3315594A (en) * 1964-10-13 1967-04-25 Herbert H Simshauser Machine for crushing cans, bottles and the like

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US512790A (en) * 1894-01-16 Cotton-press
US1062289A (en) * 1911-01-09 1913-05-20 Liquid Forged Steel Company Apparatus for making castings.
US1955278A (en) * 1930-02-24 1934-04-17 Oilgear Co Hydraulic press
US1937007A (en) * 1930-12-30 1933-11-28 Maschf Augsburg Nuernberg Ag Hydraulic press control mechanism
US2786409A (en) * 1953-06-15 1957-03-26 Robert W Claire Pneumatic dental press
US3290919A (en) * 1963-12-18 1966-12-13 Cincinnati Milling Machine Co High pressure hydraulic forming press
US3315594A (en) * 1964-10-13 1967-04-25 Herbert H Simshauser Machine for crushing cans, bottles and the like

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3940930A (en) * 1975-01-20 1976-03-02 Package Machinery Company Hydraulic system for injection molding machine
US3982417A (en) * 1975-01-20 1976-09-28 Promecam Sisson-Lehmann Device for controlling a movable member on a machine tool
US4214357A (en) * 1978-02-16 1980-07-29 Purpose Engineers Limited Punching device
WO1987002309A1 (en) * 1985-10-18 1987-04-23 Universal Engineering Development Co. Pty. Ltd. Improvements to punch presses
US20040244617A1 (en) * 2003-06-03 2004-12-09 Reefdale Pty Ltd Transfer heat press
US6983690B2 (en) * 2003-06-03 2006-01-10 Reefdale Pty Ltd Transfer heat press
CN100398316C (zh) * 2003-06-03 2008-07-02 雷夫达勒私人有限公司 垫版臂和转印机的组合结构及热转印机
WO2017129397A1 (de) * 2016-01-29 2017-08-03 Siempelkamp Maschinen- Und Anlagenbau Gmbh Presse zum herstellen eines bauteils aus einem faserverbundwerkstoff
US10843418B2 (en) 2016-01-29 2020-11-24 Siempelkamp Maschinen-Und Anlagenbau Gmbh Press for making a part from fiber composite

Also Published As

Publication number Publication date
CH517586A (de) 1972-01-15
DE2147306A1 (de) 1972-06-08
GB1339934A (en) 1973-12-05
IT939034B (it) 1973-02-10
AT309224B (de) 1973-08-10
FR2117059A5 (de) 1972-07-21

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