EP0385188A1 - Vérin à fluide sous pression - Google Patents

Vérin à fluide sous pression Download PDF

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Publication number
EP0385188A1
EP0385188A1 EP90102920A EP90102920A EP0385188A1 EP 0385188 A1 EP0385188 A1 EP 0385188A1 EP 90102920 A EP90102920 A EP 90102920A EP 90102920 A EP90102920 A EP 90102920A EP 0385188 A1 EP0385188 A1 EP 0385188A1
Authority
EP
European Patent Office
Prior art keywords
piston
brake
pressure medium
cylinder
braking
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.)
Ceased
Application number
EP90102920A
Other languages
German (de)
English (en)
Inventor
Gunnar Lundqvist
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.)
Hygrama AG
Original Assignee
Hygrama AG
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 Hygrama AG filed Critical Hygrama AG
Publication of EP0385188A1 publication Critical patent/EP0385188A1/fr
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type

Definitions

  • the invention relates to a pressure medium cylinder with a tube-like housing which is closed at the end and has a sealed longitudinal slot and in the cylindrical interior of which a sealed piston is guided so as to be longitudinally displaceable and has a lateral force take-off extension which extends through the longitudinal slot.
  • Pressure medium cylinders of this type which are also referred to as rodless pressure medium cylinders, have the advantage of requiring little space.
  • a pressure medium cylinder of this type is already known (EP-A1-190 760), which has a parking brake.
  • This contains two brake elements which engage the housing in the area of the longitudinal slot, in each case at the axial ends of the working piston. This way the length of the power take-off approach is greater than the length of the working piston, so that the range of motion of the pressure medium cylinder is reduced overall.
  • the invention has for its object to provide a pressure medium cylinder of the type mentioned, which enables precise braking with a simple structure. Existing constructions should remain largely unchanged.
  • a braking device is attached to the power take-off of a pressure medium cylinder, which has a braking element which is movable in the direction of the surface of the working cylinder and engages with a braking surface on the surface of the working cylinder.
  • the invention creates a possibility of how it can be provided with a simple and safe-acting brake without design changes to the pressure medium cylinder. There is no need to additionally attach a brake profile since the brake engages the housing itself.
  • the braking device has a brake piston which can be moved by fluid pressure. This can be actuated by hydraulic fluid or by air pressure. The same fluid that is used to drive the working piston can preferably be used.
  • the brake piston can be moved approximately radially to the pressure medium cylinder. In this way it is possible to avoid intermediate elements which are susceptible to malfunction or reduce the internal combustion power.
  • the invention further proposes that the brake piston has on its side facing the cylinder a brake pad forming the braking surface. This can be glued on, for example. It is possible that the brake device is very simple, since it has only one movable brake piston in a recess and a brake pad. Of course, auxiliary devices can be provided, for example a spring, which presses the brake piston into a normal position releasing the brake.
  • the braking surface is adapted to the cross-sectional shape of the cylinder or corresponds to it.
  • the braking device proposed by the invention can be used for a wide variety of cylinder shapes, both for sections with a straight cross section and for sections with a curved cross section.
  • the invention proposes that the side of the brake piston facing the surface of the cylinder extends approximately over the entire axial length of the working piston. In this way, since the extent of the displacement of the working piston is determined by the length of the cylinder, reduced by the length of the working piston, a large braking surface is obtained without the extent of the displacement of the working piston being reduced.
  • the braking device has a bracket which can be attached to the power take-off of the working piston, in particular can be screwed on.
  • the decrease in force of the working piston serves to decrease the movement of the piston.
  • the possibility of attaching the braking device to the power take-off, for example screwing it on, by means of the bracket makes it possible to fit existing systems to attach the braking device later. With the exception of attaching a pressure hose, no further action is required.
  • the bracket has approximately the same axial length as the working piston and the brake piston.
  • the bracket itself has a flat recess forming the brake cylinder for the brake piston.
  • the piston surface can advantageously have an elongated shape with parallel sides and semicircular rounded ends. This makes it possible to manufacture the brake piston from an extruded profile that only has to be cut to the appropriate length and milled to produce the semicircular ends.
  • the parallel side edges may need further treatment.
  • the piston has a circumferential groove in its outer surface for receiving an O-ring as a seal.
  • the bracket can advantageously extend, for example, about half the circumference of the working cylinder.
  • the braking device engages at a point diametrically opposite the longitudinal slot of the working cylinder.
  • the cylinder it is also possible, particularly when the cross-sectional shape of the cylinder housing is round, for the cylinder to have two braking devices, preferably of identical design, arranged symmetrically to a plane passing through the longitudinal slot. Both brake devices then act on the housing on another side, so that no transverse forces also have an effect on the power take-off when braking.
  • the directions of attack of the two braking devices enclose an angle of less than 180 ° with one another.
  • the pressure medium cylinder 11 can be seen in cross section in FIG. 1. It contains a circular bore 12 which extends in the longitudinal direction of the pressure medium cylinder 11 and in which a piston 13 is guided so as to be longitudinally displaceable.
  • the piston is sealed against the wall of the bore 12 by two seals arranged in the region of its longitudinal ends, which are not shown for reasons of simplification.
  • the piston 13 engages with a lateral extension 14 through a longitudinal slot 15 running in the longitudinal direction. Outside the pressure medium cylinder 11, the side extension 14 is connected to the power take-off 16. In the longitudinal direction of the pressure medium cylinder 11, this is approximately the same length as the piston 13.
  • the power take-off has holes to which the element to be moved with the aid of the piston is attached.
  • the longitudinal slot 15 is sealed from the outside of the cylinder and from its inside by a band-like seal, which is not shown in FIG. 1 for reasons of simplification.
  • a bracket 17 is screwed to the power take-off 16 and is approximately L-shaped. This bracket 17 also has an axial length that is approximately the axial length of the Piston 13 corresponds. It is shaped so that it corresponds approximately to the outer shape of the pressure medium cylinder 11 and extends over approximately half the circumference of the cylinder 11. The lower free end of the bracket 17 in FIG. 1 therefore runs approximately parallel to the corresponding outer side 18 of the pressure medium cylinder 11.
  • the bracket 17 has a braking device 19. This is intended to engage approximately centrally on the outside 18 of the pressure medium cylinder 11. This point of attack is approximately diametrically opposite in the longitudinal slot 15.
  • the bracket has in its somewhat thickened leg 20 opposite the longitudinal slot 15 a recess 21.
  • This recess 21 is connected via a stepped bore 22 to a connecting nipple 23 for connecting a pressure medium hose, not shown. Compressed air or hydraulic fluid can therefore be introduced into the recess 21 via this pressure medium hose.
  • the recess 21 is cylindrical, so that its side walls 24 run parallel to each other.
  • a brake piston 25 is inserted in the recess 21 and moves in the recess 21 depending on the pressure of the liquid.
  • the direction of movement of the brake piston 25 is upward or vice versa in FIG. 1, this direction of movement extending approximately radially to the pressure medium cylinder 11.
  • a brake lining 27 is attached to the side 26 facing the outside 18 of the pressure medium cylinder 11.
  • the brake pad is glued on, for example. 1 runs centrally to the outside 26 of the brake piston 25 and therefore also also centrally to the outside 18 of the pressure medium cylinder 11.
  • the pressure hose can also be connected to the second connection nipple 28 shown in FIG. 1.
  • Fig. 2 shows a side view of the brake bracket 17 of Fig. 1.
  • the brake bracket In the region of its upper end 29, the brake bracket is provided with a number of mounting holes 30 which correspond to the existing mounting holes of the power take-off 16 in arrangement and size. In this way, the bracket can be retrofitted to existing pressure medium cylinders so that the existing pressure medium cylinder systems can be retrofitted.
  • the large axial length of the brake bracket 17 also results from FIG. 2. This great length leads to a stable braking device and prevents that torques are transmitted to the piston 13 about its transverse axis.
  • Fig. 3 now shows a view of the brake bracket 17 of FIG. 1 from above. It can be seen that the brake bracket 17 extends below its upper end 29 first outwards and then inwards again, so that the lower leg 20 is visible from above.
  • the cylindrical recess 21 is arranged, which forms the cylinder for the brake piston 25.
  • This recess 21 has an elongated shape with parallel to each other the side walls 24. The ends are rounded in a semicircle. In the area of the ends, a threaded bore 31 is arranged next to the recess, the meaning of which will be explained later.
  • FIG. 4 schematically shows a longitudinal side view of the brake piston 25.
  • the brake piston 25 has the shape of a flat, in plan view, see FIG. 5, an oval disk.
  • the brake piston 25 On its outside 26 intended for contact with the outside 18 of the pressure medium cylinder 11, the brake piston 25 according to FIG. 4 contains two ribs 34, between which the brake lining 27 shown in FIG. 1 is inserted and glued.
  • the ribs 34 are only intended as an assembly aid, they are not required for the function.
  • FIGS. 4 and 5 show the top view of the brake piston 25. It can be seen that the brake piston 25 has two parallel longitudinal edges 35 which are connected to one another by semicircular arcs 36 in the region of the ends.
  • the brake piston shown in FIGS. 4 and 5 can be produced from extruded strand material, for example from aluminum, provided that no value is placed on the ribs 34. This profile already contains the groove 33. The brake pistons are produced in that the profile is cut to the correct length and the semicircular bends 36 are milled with the groove 33 provided there.
  • FIG. 6 now shows a section corresponding to FIG. 1 in a second embodiment in which the pressure medium cylinder 41 has an externally circular cross section.
  • the braking device of the embodiment according to FIG. 1. This would also lead to braking without lateral force.
  • the embodiment of FIG. 6 contains two brackets 42, each with a braking device 19.
  • the brackets 42 have a different cross-sectional shape than the bracket 17 of FIG Embodiment of FIG. 1, but otherwise they are constructed in the same way, ie they extend over the axial length of the piston 13 and have recesses 21 for receiving brake pistons 25.
  • the shape of the brake pistons 25 is essentially identical to that of the embodiment 1 to 5, with the only difference that the outer surface 43 of the brake piston 25 facing the outside of the pressure cylinder 11 is circular-cylindrical and concentric to the shape of the pressure cylinder 41. Brake pads 44 are also stuck here, the shape of the outer shape of the Pressure cylinder 41 corresponds. Both brackets 42 are of identical design, but are arranged symmetrically to a plane indicated by the dashed line 45, which passes through the longitudinal axis 46 of the piston 13 and in the middle through the longitudinal slot 15. The force occurring during braking thus falls into the bisector, which lies in plane 45. As a result, this arrangement is also free of lateral forces.
  • FIG. 7 shows a view of the stirrups 42 in the direction of the arrow VII in FIG. 6.
  • the shape of the recess 21 corresponds completely to the shape in the embodiment according to FIG. 3.
  • the stirrups 42 of the embodiment according to FIG. 6 can also be added subsequently the power take-off 16 of existing systems.
  • FIG. 8 shows an enlarged section through a longitudinal end of a bracket 17 or 42 in order to illustrate the function of the threaded bores 31.
  • a tongue spring 47 which is fastened to the bracket 17 with the aid of a screw 48.
  • Such a tongue spring 47 is fastened to both longitudinal ends of each piston 25 and is used to push the brake piston 25 back into its starting position in which the brake lining 27 is not in contact with the pressure medium cylinder 11 or 41 when the pressure in the recess 21 is released. The brake is released when there is no pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Actuator (AREA)
EP90102920A 1989-02-28 1990-02-15 Vérin à fluide sous pression Ceased EP0385188A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3906211 1989-02-28
DE3906211 1989-02-28

Publications (1)

Publication Number Publication Date
EP0385188A1 true EP0385188A1 (fr) 1990-09-05

Family

ID=6375103

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90102920A Ceased EP0385188A1 (fr) 1989-02-28 1990-02-15 Vérin à fluide sous pression

Country Status (3)

Country Link
US (1) US5022499A (fr)
EP (1) EP0385188A1 (fr)
JP (1) JPH02278003A (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4023058C2 (de) * 1990-07-17 1994-08-18 Mannesmann Ag Kolbenstangenloser Arbeitszylinder, insbesondere für kompressible Medien, mit einer Bremseinrichtung
DE4192710T1 (de) * 1990-11-01 1997-07-31 Ckd Corp Bremsvorrichtung für Zylinder
TW396249B (en) * 1998-01-20 2000-07-01 Someya Mitsuhiro Rodless cylinder

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104364A1 (fr) * 1982-08-05 1984-04-04 Knorr-Bremse Ag Vérin sans tige de piston avec frein
EP0280309A1 (fr) * 1987-02-27 1988-08-31 Tol-O-Matic, Inc. Cylindre pneumatique et son mécanisme de blocage

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221610A (en) * 1964-01-13 1965-12-07 Hewitt Clutch type piston locking means
US3665812A (en) * 1969-07-01 1972-05-30 Chukyo Electric Co Apparatus for controlling rectilinear motion
US3893378A (en) * 1973-11-23 1975-07-08 Delbert C Hewitt Double acting fluid cylinder
US3871267A (en) * 1974-01-18 1975-03-18 Hansen Mfg Co A L Fluid operated piston and cylinder means
US4137827A (en) * 1977-05-18 1979-02-06 Hewitt Delbert C Double acting fluid operated piston cylinder assembly
US4234060A (en) * 1977-07-01 1980-11-18 Coal Industry (Patents) Limited Brake equipment
DE7931576U1 (de) * 1979-11-08 1981-06-25 P-H-matic Ges. für pneumatische und hydraulische Antriebe und Steuerungen mbH, 8000 München Bremseinrichtung für kolbenstangenlose Arbeitszylinder
DE2945133C2 (de) * 1979-11-08 1983-09-01 Robert Bosch Gmbh, 7000 Stuttgart Bremseinrichtung für fluidgetriebene, kolbenstangenlose Arbeitszylinder
DE3328292A1 (de) * 1983-08-05 1985-02-21 Robert Bosch Gmbh, 7000 Stuttgart Arbeitszylinder mit bremseinrichtung
DE3464406D1 (de) * 1984-04-10 1987-07-30 Reinhard Lipinski Linear transporter
DE3504269A1 (de) * 1985-02-08 1986-08-21 ORIGA GmbH Pneumatik, 7024 Filderstadt Druckmittelzylinder
DE8511577U1 (de) * 1985-04-18 1985-06-05 Herion-Werke Kg, 7012 Fellbach Kolbenstangenloser Zylinder
JPH0765602B2 (ja) * 1987-01-30 1995-07-19 豊和工業株式会社 ロツドレスシリンダ
SE464534B (sv) * 1987-11-11 1991-05-06 Bo Granbom Bromsanordning vid en anordning foer linjaer roerelse
US4825746A (en) * 1988-03-16 1989-05-02 Mosier Industries, Incorporated Universal power cylinder

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0104364A1 (fr) * 1982-08-05 1984-04-04 Knorr-Bremse Ag Vérin sans tige de piston avec frein
EP0280309A1 (fr) * 1987-02-27 1988-08-31 Tol-O-Matic, Inc. Cylindre pneumatique et son mécanisme de blocage

Also Published As

Publication number Publication date
US5022499A (en) 1991-06-11
JPH02278003A (ja) 1990-11-14

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