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EP0450501B1 - Kolben-Zylinder-Aggregat - Google Patents

Kolben-Zylinder-Aggregat Download PDF

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Publication number
EP0450501B1
EP0450501B1 EP91104945A EP91104945A EP0450501B1 EP 0450501 B1 EP0450501 B1 EP 0450501B1 EP 91104945 A EP91104945 A EP 91104945A EP 91104945 A EP91104945 A EP 91104945A EP 0450501 B1 EP0450501 B1 EP 0450501B1
Authority
EP
European Patent Office
Prior art keywords
stop
ring
stop ring
piston
rings
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
EP91104945A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0450501A1 (de
Inventor
Walter Neumeister
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0450501A1 publication Critical patent/EP0450501A1/de
Application granted granted Critical
Publication of EP0450501B1 publication Critical patent/EP0450501B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/24—Other details, e.g. assembly with regulating devices for restricting the stroke
    • 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
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/16—Characterised by the construction of the motor unit of the straight-cylinder type of the telescopic type

Definitions

  • the invention relates to a hydraulic piston-cylinder unit with a plurality of sealed and slidably arranged cylinder elements, such as an outer cylinder tube, telescopic tubes and pistons, which serve as a limit stop in the inner wall 21 of the respective larger part in the region of at least the front end in a part-circular groove have a front outer part stop ring and in the outer wall of the smaller element in the region of the rear end in a part-circular annular groove have a rear inner part stop ring which abut each other when the cylinder elements extend and limit the relative movement between the two parts in the axial direction.
  • cylinder elements such as an outer cylinder tube, telescopic tubes and pistons
  • Limit stops with spring washers which have a circular cross section and are embedded in the cylinder walls, have long been known and are described, for example, in DE-A 3320 464. In many cases, however, they are also held stationary in an annular groove that has the same radius as the profile of the spring ring. Such rings must have a certain diameter to absorb the stop forces so that the groove shoulder can also absorb the forces that occur. It has hitherto been customary to provide the arrangement with such differences in diameter or gap widths that the line of the resulting forces of axial force and radial force extends at an angle of approximately 30 ° to the cylinder axis. A suitable space is left between the two cylinders, which is bridged by guide and sealing rings.
  • a radial force occurs which is approximately 58% of the axial force.
  • a stop ring arrangement with inclined shoulders is known, which provides trapezoidal stop rings for receiving the forces, which lie loosely in their grooves, the two rings being intended to dampen the impact by elastic deformation.
  • the rings are expensive to manufacture, the sharp-edged grooves lead to notch effects. This requires correspondingly strong cylinder walls.
  • the invention has for its object to design a piston-cylinder unit, preferably with telescopic cylinders, in such a way that the wall thickness of the cylinder parts can be reduced without impairing the function by suitable design of the stop rings.
  • At least one intermediate stop ring is arranged between the stop rings which support one another when the stop is limited, with a diameter which is approximately the difference in radii or the gap width between a smaller and a larger part, possibly plus Depth corresponds to an associated intermediate ring holding groove or an intermediate ring holding and storage groove.
  • the support points of the stop forces to be transmitted are shifted such that the angle between the line of action of the resulting force and the cylinder axis is reduced compared to the angle in known arrangements without such intermediate stop rings.
  • an angle between the axial direction and the resulting direction of force of about 20 ° to 13 ° can be maintained. That corresponds to a radial force of only about 36% to 23% of the axial force, so that about 38% to 60% can be saved compared to the radial force in constructions without an intermediate stop ring.
  • the wall thickness of the cylinder tubes can be reduced considerably, which contributes to great material and weight savings for the entire cylinder and thus for the entire construction in which it is installed.
  • the additional effort for the few, inexpensive to produce round wire rings per unit is insignificant in relation to the material and weight savings.
  • smooth pipes can also be used. As a result, the use of raw materials and processing costs are low.
  • the intermediate stop rings and stop rings made of round wire according to the invention with the associated part-toroidal ring grooves have the great advantage that they can all be produced inexpensively from round wire and that the grooves do not cause any particular peak effects and that this enables correspondingly small wall thicknesses.
  • the intermediate stop ring lies in an intermediate ring holding groove adjacent to the stop ring groove. This makes it easier to hold the intermediate stop ring in position. Its size can be dimensioned according to needs and the force distribution can also be adapted to the circumstances in a more variable manner.
  • the piston-cylinder unit 10 has an outer cylinder tube 11 with a screwed-on end and connecting base 12 of a conventional type. There, the line 13 is provided for the hydraulic connection. Telescopic tubes 14 and 15 and a piston 16 can be slid into each other with smaller diameters. The piston 16 has a connecting ball 17. The axis is designated 18. The displaceable components are guided and sealed into one another in the usual way with the aid of guide rings 19 and seals 20. A stop ring arrangement 25V or 25H is provided in the area of each end of each tube or the piston.
  • annular groove 22 is provided in the inner wall 21 - lying within the seals.
  • This has a semicircular cross section and thus forms a partial torus.
  • a front outer part stop ring 23 which consists of a round spring steel wire and has a separation gap 24 (Fig. 2).
  • annular grooves 27.1 and 27.2 spaced apart from one another in the region of the rear end H.
  • These also have a semicircular cross section.
  • the rear inner part stop rings 28.1 and 28.2. also have a circular cross section and each have a separation gap. They are also made of round steel spring wire.
  • the radius difference 29 between the outer radius 31 of the smaller part and the inner radius 32 of the larger part forms a free space or gap. As can be seen, this is bridged in the usual way with the guide rings 19 and suitably sealed with the seals 20.
  • the radius difference 29, ie the gap width of the gap 33 is as large as the radius of the cross section of the stop rings 23 or 28, since the ring grooves 22 or 27 are usually designed as semicircular grooves.
  • annular groove 22 of semi-circular cross-section is also formed for the inner stop in the respective inner wall 21, in which a stop ring 23H, which is also circular in cross section and made of spring steel, is inserted - as is the case with it 1 and 3 show.
  • the intermediate stop ring 35 in the gap 33, namely between the two stop rings 23V and 28.1, which are supported on each other in the respective stop position, on the one hand, and 23H and 28.2, on the other hand, that is to say in the telescopic tubes 14 and 15 both in the area of the front end V and in the area of the rear end H - as can be clearly seen from FIG. 3.
  • the intermediate stop rings 35 are each assigned to the stop ring of the larger part and can be expediently installed with a preload to the outside. Their reference numerals are supplemented with the additional letters 'V' and 'H' to indicate their assignment, where it makes sense in the text.
  • FIG. 3 shows in more detail how the stop ring 28.2 assigned to the smaller sliding part is supported on the rear intermediate stop ring 35H at the support point 39.
  • the intermediate stop ring 35H is in turn supported on the support point 41 on the outer rear stop ring 23H assigned to the larger part.
  • the diameters are chosen so that the center points 45.1 and 45.2 of the two stop rings 28H and 23H lie on a straight line with the support points 39 and 41. This takes an angle 49 to the axis 18.
  • the axial force 51 and the radial force 52 together form the resulting force 50.
  • the angle 49 is 20 °, for example.
  • the length of the section 52 is 36% of the length of the section 51, which are proportional to the magnitudes of the forces occurring.
  • FIG. 3 In the upper part of FIG. 3 it is shown how the stop ring 28.1 assigned to the smaller part - here telescopic tube 14 - in the front extended stop position, in which it is designated 28.12, rests on its upper side at the support point 39.1 on the intermediate stop ring 35V of the front outer part stop ring 23 V is supported accordingly.
  • the relationships in terms of angles and forces are the same as at the rear.
  • FIG. 5 shows a variant in which the intermediate stop rings 35H and 35V are each located in an intermediate ring holding groove 55. These each directly adjoin the ring grooves 22 and are designed in such a way that the respective intermediate stop ring 35 is securely held on the stop ring 23 to which it is associated even when it is displaced.
  • the intermediate ring holding grooves 55 are only a few mm deep into the inner wall 21 of the larger part. As a result, each intermediate stop ring 35 is somewhat larger in cross section and the centers of the three adjoining rings are no longer on a straight line, but on a line which is slightly bent in the center of the cross section of the intermediate stop ring 35.
  • the angle 49.2 between the resultant 50 of the forces passing through the support point 39 and the axis 18 is significantly further reduced and is approximately 13 ° with practically feasible dimensions.
  • the radial force 52 is then only 23% of the axial force 51. This leads to a reduction of the radial force compared to the previously known solution shown in FIG. 4 of 60%.
  • the intermediate stop ring does not need to be installed with a correspondingly large tension and is included Security kept in place. Since the associated shoulder of the annular groove 22 is not loaded, a corresponding recess can be worked in right next to it. This advantageous solution seems particularly practical.
  • a further intermediate stop ring is provided in a corresponding intermediate ring holding groove for each stop.
  • a further intermediate stop ring 35H2 is now also provided in the smaller part 15 between the rear stop ring 28.2 and the rear intermediate stop ring 35H. This lies in a further intermediate ring holding groove 55.2, which adjoins the annular groove of the stop ring 28.2 in the outer wall 26 of the rear end H of the smaller part 15.
  • a further intermediate stop ring 35H3 is assigned to the rear stop ring 28.1 for striking the intermediate stop ring 35V of the front stop ring 23V.
  • the radial force here is only 23% of the axial force.
  • This solution can be provided in particular on the ends of thin tubes that are subject to high loads. As can be seen, it is designed as a double design, so that a rear guide ring 19.1 is also provided between the two stop rings of the smaller part. It is rectangular and rounded at the edges. It can consist of bronze and has the strength of the radius difference 29 of the gap 33.
  • FIG. 7 shows a further advantageous embodiment of the invention.
  • the design is similar to that in FIGS. 5 and 6 with two rear stop rings 28.1 and 28.2 on the smaller part 15 and an intermediate guide ring 19.1 of the thickness of the gap 33.
  • the intermediate stop ring is no longer designed with approximately the thickness 29 of the gap 33 as in the first exemplary embodiment, but with the same thickness as the stop rings 23H and 23V or 28.1 and 28.2.
  • the groove recess is correspondingly larger and it lies in its own part-circular intermediate ring retaining groove 55.3, which has the function of a storage groove because of the expansion and circumferential reduction of the intermediate stop ring.
  • the intermediate stop ring 35.5 is biased outwards in the direction of the larger part 14 so that it detaches from the intermediate ring holding groove 55.3 for striking and rests against the support surface 57 of the inner wall of the larger part and arrives in the position suitable for supporting the stop forces .
  • the support surface 57 is offset to the outside against the inner wall 21 of the larger part 14 by such an amount that the center point of the cross section of the intermediate stop ring 35.4 in the stop position shown in FIG. 7 again on a straight line through the centers of the two abutting support rings 23 and 28, on which the support points 39 and 41 are located.
  • a run-up bevel 58 is provided which smoothly adjusts the diameter difference between the inner wall 21 and the supporting surface 57 compensates and by means of which the intermediate stop ring 35.5 between its rest position and the stop position is shifted radially and thereby stretched or reduced. Since the stop rings are only loaded on the shoulder facing away from the support point 41, corresponding grooves can be provided, as in the exemplary embodiments in FIGS. 5, 6 and 7. In this embodiment too, the cost of additional rings and incorporation of appropriately designed grooves is so low that it is worthwhile in any case for the considerable savings in material, wall thickness and weight of the overall arrangement in which the piston-cylinder unit is used.
  • the piston-cylinder unit has the usual stop rings (23, 28) made of round spring steel to limit its sliding parts, in particular the telescopic tubes (14, 15) and the piston (16).
  • stop rings 23, 28
  • intermediate stop rings (35) are provided between them in the stop position.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Eye Examination Apparatus (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
EP91104945A 1990-04-06 1991-03-28 Kolben-Zylinder-Aggregat Expired - Lifetime EP0450501B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4011119 1990-04-06
DE4011119A DE4011119A1 (de) 1990-04-06 1990-04-06 Kolben-zylinder-aggregat

Publications (2)

Publication Number Publication Date
EP0450501A1 EP0450501A1 (de) 1991-10-09
EP0450501B1 true EP0450501B1 (de) 1993-05-19

Family

ID=6403880

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91104945A Expired - Lifetime EP0450501B1 (de) 1990-04-06 1991-03-28 Kolben-Zylinder-Aggregat

Country Status (7)

Country Link
EP (1) EP0450501B1 (fi)
AT (1) ATE89650T1 (fi)
CZ (1) CZ282174B6 (fi)
DE (2) DE4011119A1 (fi)
DK (1) DK0450501T3 (fi)
ES (1) ES2042320T3 (fi)
FI (1) FI92348C (fi)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2834318B1 (fr) * 2002-01-03 2004-10-29 Gerard Leray Verin telescopique
EP1947351A1 (de) * 2007-01-17 2008-07-23 Carl Freudenberg KG Hydraulikzylinderanordnung
EP2466156A1 (en) * 2010-12-16 2012-06-20 Hyva Holding BV Telescopic hydraulic cylinder
EP2584203A1 (en) * 2011-10-20 2013-04-24 Hyva Holding BV A telescopic hydraulic cylinder
GB2511745B (en) * 2013-03-11 2017-05-03 Jonic Eng Ltd Telescopic hydraulic piston arrangement
EP3786462A1 (en) * 2019-09-02 2021-03-03 Hyva Holding BV A telescopic cylinder

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2649524C2 (de) * 1976-08-20 1983-01-20 Telehoist Ltd., Cheltenham, Gloucesterhire Teleskopartige Vorrichtung
DE3320464A1 (de) * 1983-06-07 1984-12-13 Otto 7106 Neuenstadt Neumeister Ein- oder mehrstufiger hydraulikzylinder

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB812313A (en) * 1956-04-18 1959-04-22 Bendix Aviat Corp Fluid pressure motor
GB1001045A (en) * 1962-03-02 1965-08-11 Heinz Teves Improvements in or relating to piston and cylinder devices
DE2004117A1 (de) * 1969-02-14 1970-09-03 Nummi Oy Anordnung an einem Teleskopzylinder
DE1907689C2 (de) * 1969-02-15 1971-02-18 Otto Neumeister Ein- oder mehrstufiger Hydraulikzylinder mit Verdrehsicherung
FR2290613A2 (fr) * 1974-11-08 1976-06-04 Protomatic Perfectionnements aux verins telescopiques
FR2308028A1 (fr) * 1975-04-14 1976-11-12 Luchaire Sa Procede pour assurer la lubrification des pistons de verins pneumatiques
FR2484031A1 (fr) * 1980-06-05 1981-12-11 Leray Jules Verin telescopique
FR2505943A1 (fr) * 1981-02-10 1982-11-19 Faucheux Butee de fin de course amovible pour piston plongeur

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2649524C2 (de) * 1976-08-20 1983-01-20 Telehoist Ltd., Cheltenham, Gloucesterhire Teleskopartige Vorrichtung
DE3320464A1 (de) * 1983-06-07 1984-12-13 Otto 7106 Neuenstadt Neumeister Ein- oder mehrstufiger hydraulikzylinder

Also Published As

Publication number Publication date
CZ282174B6 (cs) 1997-05-14
FI911451L (fi) 1991-10-07
ATE89650T1 (de) 1993-06-15
FI92348C (fi) 1994-10-25
DE4011119A1 (de) 1991-10-10
ES2042320T3 (es) 1993-12-01
CS9100942A2 (en) 1991-11-12
EP0450501A1 (de) 1991-10-09
DK0450501T3 (da) 1993-11-08
DE59100116D1 (de) 1993-06-24
FI911451A0 (fi) 1991-03-26
FI92348B (fi) 1994-07-15

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