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WO1992001171A2 - Dispositif a ressort - Google Patents

Dispositif a ressort Download PDF

Info

Publication number
WO1992001171A2
WO1992001171A2 PCT/GB1991/001162 GB9101162W WO9201171A2 WO 1992001171 A2 WO1992001171 A2 WO 1992001171A2 GB 9101162 W GB9101162 W GB 9101162W WO 9201171 A2 WO9201171 A2 WO 9201171A2
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
spring device
piston
fluid
pressure
Prior art date
Application number
PCT/GB1991/001162
Other languages
English (en)
Other versions
WO1992001171A3 (fr
Inventor
Linval Rodney
Original Assignee
Linval Rodney
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 Linval Rodney filed Critical Linval Rodney
Publication of WO1992001171A2 publication Critical patent/WO1992001171A2/fr
Publication of WO1992001171A3 publication Critical patent/WO1992001171A3/fr
Priority to GB939300376A priority Critical patent/GB9300376D0/en

Links

Classifications

    • 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
    • B21D45/00—Ejecting or stripping-off devices arranged in machines or tools dealt with in this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/002—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising at least one fluid spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F5/00—Liquid springs in which the liquid works as a spring by compression, e.g. combined with throttling action; Combinations of devices including liquid springs

Definitions

  • the present invention is concerned with spring devices and especially but not exclusively to spring devices for presses used in the formation of profiled metal panels.
  • profiled metal panels such as car body panels are pressed from a flat sheet of metal.
  • the metal is placed on a profiled press plate.
  • An upper press plate with a complementary profile, is hydraulically or pneumatically lowered to form the profiled panel. Removing the newly formed panel from the press often proves difficult, especially when the shape of the profile is such that the panel tends to clasp the press-plate.
  • profiling of panels often requires shapes to be produced that cannot be conventionally provided within the press, for example apertures or small re-entrant formations.
  • a spring device comprising first and second pistons, a chamber between the pistons and containing compressible fluid, and resilient means operable to resist the second piston moving to increase the volume of the chamber, any movement of the first piston to reduce the said volume being resisted by a combination of the compression of the fluid and the resilience of the resilient means.
  • the resilient means is resiliently compressible.
  • the resilient means is a fluid, preferably a gas which may be pressurised.
  • the resilient means may be a mechanical spring.
  • the first piston may be operable within a first cylinder and, the second piston operable within a second cylinder.
  • the first cylinder is of smaller diameter than the second cylinder and the first cylinder is located wholly or partly within the second cylinder.
  • the second piston is preferably annular.
  • the annular piston preferably encircles and is movable along the first cylinder.
  • seal means is provided between the annular piston and the second cylinder whose sealing efficiency tends to increase with the pressures in the respective cylinders.
  • the seal means may comprise upper and lower plates and a resilient seal sandwiched therebetween such that as the pressure in the cylinders increase, the plates are urged together and squeeze the resilient seal so that its outer surface is urged against the second cylinder.
  • the resilient means encircles the first cylinder.
  • the resilient means is located in the second cylinder.
  • the first cylinder communicates with the second cylinder through at least one aperture formed in the wall of the said first cylinder, the said apertures allowing compressible fluid to pass therethrough during operation to provide communication between the pistons.
  • the or each aperture is so located as to maintain communication between the cylinders during the whole range of movement of the pistons.
  • the first and second cylinders may be remote from each other and interconnected by means of passages through which compressible fluid may pass.
  • valve means is provided to control communication of the first cylinder with a pressurised compressible fluid reservoir, so that the pressure of the fluid within the first cylinder may be controlled.
  • the valve means is preferably located in a wall or an end of the first cylinder.
  • the valve means comprises a pressure sensor which is operable to sense the pressure of the fluid within the first cylinder and to automatically control the communication between the cylinder " and the pressurised fluid in the reservoir by means of the valve, to maintain constant pressure within the first cylinder.
  • the aforementioned automatic control can be overridden to permit manual control of the pressure within the cylinder.
  • Valve means and fluid reservoir as hereinbefore described may be provided to control the pressure of fluid within the second cylinder.
  • a plurality of resilient means may be provided within the device.
  • the resilient means may comprise a plurality of springs, which may be arranged in parallel
  • each resilient means may be located outside the second cylinder and connected to the interior of each cylinder by means of one or more plungers, sealingly operable within the second cylinder.
  • a plurality of first cylinders as aforesaid may communicate with a common second cylinder.
  • Two devices as defined above may be connected together to provide fluid communication between the chambers of the devices.
  • the relative orientations of the first and second devices may differ such that the direction of movement of the pistons of the first device differs front that of the pistons of the second device.
  • the second piston may carry a punch or other shape forming means, whereby increased fluid pressure within the first device is conveyed to the second piston to move the punch or other shape forming means.
  • the compressible fluid is hydraulic fluid.
  • Fig. 1 is a partial cross-section of a spring device according to the present invention
  • Fig. 2 is a partial cross-section of an alternative spring device according to the present invention.
  • Fig. 3 is a partial cross-section of a further alternative spring device according to the present invention.
  • Fig. 4 is a partial cross-section of part of a still further alternative spring device according to the present invention.
  • Fig. 5 is a diagrammatic partial cross-section of another alternative spring device and a pressure regulating system according to the present invention
  • Fig. 6 is a schematic representation of an application of the devices of the present invention.
  • Fig. 7 is a schematic representation of a further application of the devices.
  • Fig. 1 shows a spring device 10 comprising a first piston 12 operable within a first cylinder 14, a second, annular piston 16 operable within a second annular cylinder 18, around and concentric with the first cylinder 14.
  • the interiors of the two cylinders 14, 18 are in communication through apertures 20 in the first cylinder.
  • a chamber 22 is thus formed between the first piston 12 and the second piston 16, and having two portions, one within the first cylinder and one within the second cylinder.
  • the chamber 22 contains compressible fluid, preferably hydraulic fluid.
  • a second chamber 28 is formed between the second piston 16 and the second cylinder 18 and is located around the first cylinder 14, and separated from the first chamber 22 by the second piston 16. Pressurised gas is provided in the second chamber 28.
  • a valve V is provided connecting the second chamber 28 to a gas supply and exhaust means (not shown)
  • a further valve V ? is provided to connect the first chamber 22 to a hydraulic fluid supply and exhaust means (see later) .
  • valves V.. and V shadow enable the amount and pressure of gas and hydraulic fluid in the respective chambers 28, 22 to be controlled. Such control may be effected manually when the device is not in use, enabling the pressures of the two chambers 28, 22 when the device is "at rest” to be finely controlled to provide a device with the desired spring characteristics. Conveniently the gas pressure is maintained at around 150 bar (see later).
  • the device described can therefore be installed in a press with the piston 12 under a sheet to be profiled, so that the piston 12 is depressed as the press closes, and pushes the profiled sheet off the press as the press opens.
  • the energy required to force the piston 12 into the cylinder 14 is at least partially stored within the device 10. Upon release of the force, the pressure of the gas and the fluid in the respective chambers 28, 22 relax to force the piston 12 out of the cylinder 14.
  • Fig 2 shows a second device 110, similar to that hereinbefore described, in which the second annular piston 116 comprises an upper annular plate 117 and a lower annular plate 119.
  • the second annular piston 116 comprises an upper annular plate 117 and a lower annular plate 119.
  • Two annular rubber seals 121,123 of different diameter are sandwiched between the plates 117,119 and held in position therebetween by the second cylinder 118 and a locating protrusion 125 extending from the upper plate 117, toward the lower plate 119.
  • the strength of the seal between the respective seals 121, 123 and the cylinder 118 increases as the pressures within the chambers 122,128 increase, as a result of the increased pressures urging the plates 117,119 together thereby squeezing and flattening the seals 112,123 and urging them against the cylinder 118.
  • Fig. 3 shows a third device 210 of generally similar structure as hereinbefore described, but in which the resilient means comprises a mechanical comp-ression spring 226 located in the second chamber 228.
  • the spring 226 functions in a similar way to the pressurised gas, and the characteristics of the spring can be altered to achieve the desired overall characteristics of the device.
  • Fig. 4 shows a second piston 316 and second cylinder 318 of a fourth device 310, which are remote, in use, from a first cylinder (not shown) housing a first piston (not shown).
  • the piston 316 of the device is not annular.
  • Passages 320 allow the first and second cylinders to be connected, so that a chamber is formed between the pistons partially within the passages 320.
  • the chamber is filled with compressible fluid.
  • Two mechanical compression springs 326 are located in parallel within the second cylinder 318, the springs 326 being maintained in position within the chamber 328 by pegs 330 over which the springs are located.
  • the device of Fig. 4 functions in a similar manner to that of Figs. 1, 2 and 3. That is, movement of the first piston to reduce the volume of the chamber between the pistons is resisted by compression of the fluid in the chamber, which in turn causes the piston 316 to move to increase the chamber volume against the resistance of the springs 326.
  • the overall spring characteristics can again be changed in various ways.
  • An advantage over the arrangement of Figs. 1,2 and 3 is that the direction of movement of the two pistons no longer need be parallel, and the two cylinders do not need to be close together.
  • the first piston can be located at the press, but the second piston can be located at a more convenient location remote from the first.
  • Fig. 5 shows a further arrangement in which the first piston 412 and cylinder 414 are remote from the second piston 416 and cylinder 418, and are interconnected by fluid lines 420 to be operable as hereinbefore described, particularly with reference to Fig. 4.
  • the second chamber 428 in the second cylinder 418 is filled with pressurised gas, similar to the devices of Figs. 1 and 2.
  • a relatively highly pressurised fluid reservoir R is connected to a control box C which in turn is connected by means of an output conduit C to the second cylinder 418, and by means of an input conduit C. to the output from the first cylinder 414.
  • the control box C comprises sensor (not shown) which detect the pressure of fluid from the first cylinder 414, through the input conduit C ⁇ .
  • the control box C also comprises a valve to control communication between the reservoir R and the second cylinder 418. If during operation of the spring device, a drop in pressure is detected by the sensor, the control box C opens the valve (not shown) to permit passage of pressurised fluid from the reservoir R to the second cylinder 418, through the output conduit C .
  • This automatic control ensures that the pressures within the device and hence the spring characteristics of the device remain constant even in the event of fluid leakage.
  • the reservoir R may be connected to a plurality of devices to simultaneously maintain the pressures in each. It is to be appreciated that a similar reservoir (not shown) may be provided to maintain the gas pressure in the second chamber 428. The control arrangement may be overridden so that the pressures within the system can be manually set.
  • a single second piston and cylinder arrangement as shown in Fig. 4 could be connected to a plurality of first cylinders located at various positions on the press.
  • any combination of mec'.anical spring(s), pressurised gas and compressible fluid according to any of the embodiments may be provided within the chambers.
  • Fig. 6 shows in more detail how devices 10 can be installed for use in a press plate P.
  • the first piston 12, protrudes out of the plate P in a direction parallel to the direction of the pressing action (indicated by the arrows A 1 ) parallel to the direction of the pressing action.
  • the first piston 12 is forced into the first cylinder 14.
  • the devices 10 store energy by compression of the fluid and the gas (and/or spring(s)).
  • the force exerted by the press is released.
  • the energy stored within the devices 10 is released as the gas (and/or spring(s)) and fluid decompress, and the first pistons 12 are forced up to push the profiled panel off the plate P.
  • FIG. 7 of the drawings A further application of the devices of the present invention is shown in Fig. 7 of the drawings.
  • the fluid chamber of a first de-vice A of a similar design to that described above in relation to Figs. 4 and 5, is connected to a piston operated punch T in a cylinder B by means of a hydraulic fluid passage H.
  • the device A and the cylinder B are incorporated into a press as described above. Compression of the first device A as the press closes causes a build up of pressure within the device A as described above. This pressure is transmitted to the cylinder B through the hydraulic fluid passages H.
  • the punch T is then forced into the sheet of metal M, thereby punching the sheet at the same time as it is profiled.
  • the tool T Upon release of the press force, the tool T is withdrawn from the sheet M, and the first piston in device A acts to force the sheet M off the press as described above.
  • the pressures within the system is maintained using the control arrangement of Fig. 5.
  • a hydraulic spring may replace the mechanical or pneumatic spring.
  • Various different configurations, including those described, can be adopted for the pistons and cylinders. Any suitable arrangement may be employed to maintain the pressure in the system.
  • the resilient means may be located outside the second chamber, but connected thereto by means of a plunger sealingly operable within the said chamber. Thus would allow easy access to and maintenance of mechanical springs.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

Un dispositif à ressort (10) comprend un premier piston (12) fonctionnant avec un premier cylindre (14) et un second piston (16) fonctionnant avec un second cylindre (18). Les intérieurs des deux cylindres (14, 18) communiquent entre eux, de sorte qu'une chambre (22) contenant du gaz pressurisé est ménagée entre le premier piston (12) et le second piston (16). Une seconde chambre (28) contenant du gaz pressurisé est ménagée entre le second piston (16) et le second cylindre (18). Lors de l'utilisation, lorsqu'une force est appliquée de manière à déplacer le premier piston (12) vers l'intérieur du premier cylindre (14), le fluide contenu dans la chambre (22) oppose une résistance au mouvement du premier piston (12). Ceci amène à son tour le second piston à se déplacer à l'encontre de la résistance produite par le gaz dans la seconde chambre (28). Il en résulte une résistance élastique opposée à la compression du premier piston (12) et un emmagasinage d'énergie dans le dispositif. Lorsque la force est réduite, l'élasticité du dispositif (10) repousse les pistons (12, 16) vers leur position de repos.
PCT/GB1991/001162 1990-07-12 1991-07-12 Dispositif a ressort WO1992001171A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB939300376A GB9300376D0 (en) 1990-07-12 1993-01-11 Spring device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB909015337A GB9015337D0 (en) 1990-07-12 1990-07-12 Spring device
GB9015337.0 1990-07-12

Publications (2)

Publication Number Publication Date
WO1992001171A2 true WO1992001171A2 (fr) 1992-01-23
WO1992001171A3 WO1992001171A3 (fr) 1992-06-11

Family

ID=10678982

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1991/001162 WO1992001171A2 (fr) 1990-07-12 1991-07-12 Dispositif a ressort

Country Status (2)

Country Link
GB (2) GB9015337D0 (fr)
WO (1) WO1992001171A2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2177284A1 (fr) * 2008-10-14 2010-04-21 Safan B.V. Procédé et dispositif pour l'étalonnage d'une presse plieuse
EP2487383A4 (fr) * 2009-10-09 2014-09-24 Toshiba Kk Amortisseur de mécanisme de commande pour dispositif d'ouverture et de fermeture et procédé de lubrification de celui-ci
US10549803B2 (en) 2017-06-30 2020-02-04 Sram, Llc Seat post assembly
US10668968B2 (en) 2017-06-30 2020-06-02 Sram, Llc Seat post assembly
EP3889428A2 (fr) 2020-04-03 2021-10-06 Commissariat à l'énergie atomique et aux énergies alternatives Système de compression passive à piston

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107598006B (zh) * 2017-10-24 2023-08-04 山西新环粉末冶金有限公司 一种具备成品收集功能的活塞阀线压型机

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB388203A (en) * 1932-02-18 1933-02-23 Rudolph William Glasner Improvements relating to sheet metal working presses
BE464563A (fr) * 1939-08-24
GB671925A (en) * 1948-07-23 1952-05-14 Electro Hydraulics Ltd Improvements in or relating to shock absorbers
US2925262A (en) * 1956-09-05 1960-02-16 George F Wales Liquid spring
GB881242A (en) * 1959-02-13 1961-11-01 Paul Hollis Taylor Liquid spring and shock-strut suspensions for aircraft and vehicles
US3202411A (en) * 1963-10-11 1965-08-24 Elmer F Heiser Fluid spring system
JPS5080685U (fr) * 1973-11-30 1975-07-11
DE3174727D1 (en) * 1980-11-25 1986-07-03 Bayerische Motoren Werke Ag Suspension system for vehicles
DE3803577C1 (en) * 1988-02-06 1989-06-29 Hermann Hemscheidt Maschinenfabrik Gmbh & Co, 5600 Wuppertal, De Hydraulic end stop

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2177284A1 (fr) * 2008-10-14 2010-04-21 Safan B.V. Procédé et dispositif pour l'étalonnage d'une presse plieuse
EP2487383A4 (fr) * 2009-10-09 2014-09-24 Toshiba Kk Amortisseur de mécanisme de commande pour dispositif d'ouverture et de fermeture et procédé de lubrification de celui-ci
US9136675B2 (en) 2009-10-09 2015-09-15 Kabushiki Kaisha Toshiba Buffering device for the operating mechanism of a switchgear, and method of lubrication thereof
US9142941B2 (en) 2009-10-09 2015-09-22 Kabushiki Kaisha Toshiba Buffering device for the operating mechanism of a switchgear, and method of lubrication thereof
US9178339B2 (en) 2009-10-09 2015-11-03 Kabushiki Kaisha Toshiba Buffering device for the operating mechanism of a switchgear, and method of lubrication thereof
US9570891B2 (en) 2009-10-09 2017-02-14 Kabushiki Kaisha Toshiba Buffering device for the operating mechanism of a switchgear, and method of lubrication thereof
US10549803B2 (en) 2017-06-30 2020-02-04 Sram, Llc Seat post assembly
US10668968B2 (en) 2017-06-30 2020-06-02 Sram, Llc Seat post assembly
US11987312B2 (en) 2017-06-30 2024-05-21 Sram, Llc Seat post assembly
EP3889428A2 (fr) 2020-04-03 2021-10-06 Commissariat à l'énergie atomique et aux énergies alternatives Système de compression passive à piston
FR3108954A1 (fr) 2020-04-03 2021-10-08 Commissariat A L'energie Atomique Et Aux Energies Alternatives Système de compression passive à piston

Also Published As

Publication number Publication date
GB9015337D0 (en) 1990-08-29
WO1992001171A3 (fr) 1992-06-11
GB9300376D0 (en) 1993-03-10

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