EP0133241A1 - Entraînement à piston coulissant - Google Patents

Entraînement à piston coulissant Download PDF

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Publication number
EP0133241A1
EP0133241A1 EP84108471A EP84108471A EP0133241A1 EP 0133241 A1 EP0133241 A1 EP 0133241A1 EP 84108471 A EP84108471 A EP 84108471A EP 84108471 A EP84108471 A EP 84108471A EP 0133241 A1 EP0133241 A1 EP 0133241A1
Authority
EP
European Patent Office
Prior art keywords
piston
rod
piston rod
thrust
piston drive
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.)
Granted
Application number
EP84108471A
Other languages
German (de)
English (en)
Other versions
EP0133241B1 (fr
Inventor
Alex K. Gebauer
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.)
Cessione inventio AG
Original Assignee
Ak Gebauer & Cie Spezialfabrik fur Aufzuge
Ak Gebauer & Cie Spezialfabrik fur Aufzuege
Gebauer & Cie
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 Ak Gebauer & Cie Spezialfabrik fur Aufzuge, Ak Gebauer & Cie Spezialfabrik fur Aufzuege, Gebauer & Cie filed Critical Ak Gebauer & Cie Spezialfabrik fur Aufzuge
Publication of EP0133241A1 publication Critical patent/EP0133241A1/fr
Application granted granted Critical
Publication of EP0133241B1 publication Critical patent/EP0133241B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B9/00—Kinds or types of lifts in, or associated with, buildings or other structures
    • B66B9/04—Kinds or types of lifts in, or associated with, buildings or other structures actuated pneumatically or hydraulically
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F3/00—Devices, e.g. jacks, adapted for uninterrupted lifting of loads
    • B66F3/24—Devices, e.g. jacks, adapted for uninterrupted lifting of loads fluid-pressure operated

Definitions

  • the invention relates to a thrust piston drive with a single-acting hydraulic cylinder, which has a piston in the hydraulic cylinder sealingly guided with a piston rod.
  • Thrust piston drives are used extensively in various areas of technology in order to move any loads over the stroke length.
  • the forces required for this are practically not limited by the pressure generators available or the strength of the material available for the parts exposed to pressure, nor by the seals. This is also the reason why the thrust piston drives offer many possible uses due to their high work and power density.
  • a limitation of the performance of the thrust piston drives does not result from the usually relevant criteria, but from the problem of kink resistance.
  • the free length, which is decisive for determining the buckling strength, of the thrust piston parts exposed to the pressure load limits the stroke of a thrust piston drive to a far greater extent than all other properties of the components used, which are used in the thrust piston drive. It is therefore also customary to use a plunger or plunger instead of a lifting element consisting of a piston and piston rod in the case of thrust piston drives for large stroke lengths which are designed to be single-acting.
  • the piston rod has a guide rod which extends in the same or a parallel axis and forms a guide on the inner circumference or on the outer circumference of the piston rod and by means of brackets with an outside of the push piston drive, the one in the push piston drive occurring kink loads not exposed support is firmly connected.
  • the thrust piston drive shown in FIGS. 1 and 2 is designed for a large stroke length and is used, for example, for lifting and lowering loads, in particular people and goods.
  • the large stroke length of the thrust piston drive is not readily apparent from FIG. 1 because of the interruptions U 1 and U 2 required for reasons of space.
  • the technology referred to collectively as "long-stroke hydraulics" is understood to mean push-piston actuators with stroke lengths of the order of 5 to 50 m.
  • Such a drive must take into account the risk of buckling in its design, which is included in the calculation with the square of the stroke length. 1 and 2
  • the solution shown allows the drive to be designed without taking the buckling into account. It is essential, however, that this design creates a clean solution that can be checked after installation and that can be used to carry out mechanical adjustments effectively.
  • the thrust piston drive shown in FIGS. 1 and 2 carries out vertical lifting movements, but such a drive could be used in the same way in an inclined or horizontal position.
  • the thrust piston drive shown in FIGS. 1 and 2 has a hydraulic cylinder with a cylinder 1 and a piston rod 2.
  • the cylinder 1 is closed at one end by a cylinder base 3 and provided with a line connection 4 to which a pressure source 5 is connected via a controller 6.
  • the controller 6 can be designed in various ways, but this is irrelevant in connection with the present invention.
  • the inner wall 7 of which is machined a piston 8 with a seal 9, e.g. made of piston rings or soft sealing rings, which is connected to the piston rod 2 via a coupling 10.
  • the clutch 10 is designed such that a relative movement between the piston 8 and the piston rod 2 is possible.
  • a base 11 ′ fastened to the lower end of the piston rod 2 serves to mount the clutch 10.
  • the piston rod 2 has a hollow profile formed as a polygon.
  • the profile is a pentagon, which is composed of several rod parts 11, 12, 13, 14.
  • the rod parts 11, 12 consist of the same angle profile, while the rods parts 13, 14 consist of a flat profile.
  • the rod parts 11, 12, 13, 14 are connected to one another by connecting straps 15, 16, which consist of angle profiles.
  • the connecting straps 15 are firmly connected to the rod parts 13, 14, for example by welding, while the other leg is screwed to the rod parts 11, 12.
  • the connecting strap 16 connects the two rod parts 13, 14 and is screwed to them.
  • the piston rod 2 can also be composed in a different way and also need not be designed as a pentagonal polygon.
  • the piston rod 2 has a longitudinal slot 17, the function of which will be described in more detail.
  • the polygon edges can be at least partially covered with a sliding coating 18, by means of which the piston rod 2 can be supported on the cylinder 1.
  • Fig. 1 only two connecting tabs are shown.
  • connecting lugs 15, 16 are provided over the length of the piston rod as are required for the formation of a stable piston rod.
  • a stable piston rod 2 can be put together with a relatively small number of connecting straps 15, 16 will.
  • a guide rod 19 is inserted, which also has a hollow profile designed as a polygon.
  • sliding pads 20 are applied on the outer surfaces of the guide rod 19, on which the piston rod 2 is guided.
  • the sliding linings 20 as well as the sliding linings 18 on the edges of the piston rod 2 can be designed in different ways, for example as metal or plastic shells, and in different ways on the Guide rod 19 or piston rod 2 may be attached, for example by screwing or gluing.
  • the guide rod 19 is fastened to a support 22 by means of brackets 21 which extend through the slot 17 of the piston rod 2.
  • the support 22 is located outside the thrust piston drive and is a component that is not subject to buckling.
  • the support 22 is a part which is supported on a wall 23 or anchored in the same.
  • the holder 21 is composed of a threaded bolt 24, a plate-shaped nut 25 lying against the inner wall of the guide rod 19, a lock nut 26 with an intermediate ring 27 and a lock nut 28 for fastening the holder 21 to the support 22. So that the connection between the brackets 21 and the guide rod 19 can be easily established, the guide rod 19 also has a longitudinal slot 29.
  • the cylinder base 3 is supported on a base 30 with its cylinder base 3. By one, not detailed the cylinder 1 is anchored in the wall 23.
  • the thrust piston drive shown in FIGS. 3-5 can also be used for long stroke lengths. For reasons of space, the thrust piston drive is also shown here with interruptions. Reference numerals which correspond to those in FIGS. 1 and 2 denote the same parts in FIGS. 3-5 and are therefore no longer described.
  • the difference between this embodiment and the push piston drive according to FIGS. 1 and 2 is that although a guide rod 31 is also used, it guides the piston rod 2 on its outer circumference.
  • the guide rod 31 is formed from two hollow profiles 31 ′, 31 ′′ which are provided with flat flanges on their longitudinal edges 34, 35, see FIG. 5.
  • the guide rod 31 forms a longitudinal slot with the longitudinal edges 35, which extends along the stroke of the piston rod 2.
  • the longitudinal slot 33 enables the arrangement of a support bracket 56 connected to the piston rod 2, which is fixedly connected to the piston rod 2 at the free end thereof.
  • the support bracket 56 is used to fasten the load to be raised and lowered by the thrust piston drive (not shown).
  • the guide rod 31 is encompassed by brackets 21, see FIG. 4, which are composed of two identical, concave parts 40.
  • the concave parts 40 are by screws 36, one of which is shown in Fig. 4, while pressing the hollow profiles 31 ', 31 '''held together and are connected to the support 22 by a strut 41.
  • the brackets 21 are provided in the area of the longitudinal slot 33 with adjusting means 53 in the form of a cap screw 54 with a lock nut 55. By means of the cap screws 54, pressure can be exerted on the longitudinal edges 35 of the hollow profiles 31 ′, 31 ′′, as a result of which the profiles at the interfaces can be precisely aligned in the case of several successive guide rods 31.
  • the thrust piston drives described are, as already mentioned, used for long stroke lengths. It may be necessary to use several parts for the cylinder 1 and for the piston rod 2. 3, two cylinder parts 43, 44 are held together by a pipe coupling 57.
  • the pipe coupling 57 is composed of two half-shells 45, which are placed over a sleeve 47 provided with sealing rings 46 and held together by tensioning wheels.
  • the pipe coupling 58 used for holding parts of the piston rod 2 together is simpler; it consists of a sleeve 48, through which the piston rod parts are held together by means of locking pins 49. Sealing is not necessary here, since the piston rod 2 does not come into contact with the hydraulic medium.
  • the thrust piston drives described make it possible to work with an optimal working pressure of the transmission medium regardless of the stroke length.
  • the piston rod 2 can be designed with a cross section that corresponds to the pressure force actually occurring during operation. This advantage is essential because, in particular in the case of controlled or regulated acceleration and deceleration processes during the lifting movement, these are used do not work satisfactorily in arbitrarily large pressure ranges without considerable complications and thus a substantial improvement is achieved if one can at least eliminate the kink-related factors. Even if the described thrust piston drive is only single-acting and could only be combined in a double-acting manner, on the other hand the advantages that can be achieved with it, in particular the large stroke length, are so great that it represents the most economical solution for a large number of applications.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Automation & Control Theory (AREA)
  • Actuator (AREA)
EP19840108471 1983-07-22 1984-07-18 Entraînement à piston coulissant Expired EP0133241B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4032/83 1983-07-22
CH403283 1983-07-22

Publications (2)

Publication Number Publication Date
EP0133241A1 true EP0133241A1 (fr) 1985-02-20
EP0133241B1 EP0133241B1 (fr) 1987-09-09

Family

ID=4268535

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19840108471 Expired EP0133241B1 (fr) 1983-07-22 1984-07-18 Entraînement à piston coulissant

Country Status (2)

Country Link
EP (1) EP0133241B1 (fr)
DE (1) DE3465968D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU574546B2 (en) * 1984-12-24 1988-07-07 Otis Elevator Company Holeless hydraulic elevator with improved car frame
EP0254840A3 (en) * 1986-06-11 1990-05-30 Gebauer Ag Method and device for lifting and lowering a load by a hydraulic linear motor
EP3436388A4 (fr) * 2016-03-31 2020-04-29 Saab Ab Système de levage hydraulique à câble à contre-poids

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE55607C (de) * O. KRELL in St. Peters. bui-g Unmittelbar wirkender Flüssig. keitsdruck-Aufzug
DE814085C (de) * 1950-01-31 1951-09-20 Walter Theobald Tauchkolbenfuehrung an Maschinen mit grossen Hublaengen, insbesondere an hydraulischen Hobelmaschinen
US2854952A (en) * 1954-12-29 1958-10-07 Wilson John Hart Threadless coupled, slender ratio, hydraulic cylinder-plunger assembly
CH436617A (de) * 1965-04-20 1967-05-31 Roethlin Albert Hydraulische bzw. pneumatische Fördereinrichtung
US4225014A (en) * 1978-11-28 1980-09-30 The Texacone Company Self-aligning elevator connection

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE55607C (de) * O. KRELL in St. Peters. bui-g Unmittelbar wirkender Flüssig. keitsdruck-Aufzug
DE814085C (de) * 1950-01-31 1951-09-20 Walter Theobald Tauchkolbenfuehrung an Maschinen mit grossen Hublaengen, insbesondere an hydraulischen Hobelmaschinen
US2854952A (en) * 1954-12-29 1958-10-07 Wilson John Hart Threadless coupled, slender ratio, hydraulic cylinder-plunger assembly
CH436617A (de) * 1965-04-20 1967-05-31 Roethlin Albert Hydraulische bzw. pneumatische Fördereinrichtung
US4225014A (en) * 1978-11-28 1980-09-30 The Texacone Company Self-aligning elevator connection

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU574546B2 (en) * 1984-12-24 1988-07-07 Otis Elevator Company Holeless hydraulic elevator with improved car frame
EP0254840A3 (en) * 1986-06-11 1990-05-30 Gebauer Ag Method and device for lifting and lowering a load by a hydraulic linear motor
EP3436388A4 (fr) * 2016-03-31 2020-04-29 Saab Ab Système de levage hydraulique à câble à contre-poids

Also Published As

Publication number Publication date
DE3465968D1 (en) 1987-10-15
EP0133241B1 (fr) 1987-09-09

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