EP0443456A1 - Support - Google Patents

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Publication number
EP0443456A1
EP0443456A1 EP91102171A EP91102171A EP0443456A1 EP 0443456 A1 EP0443456 A1 EP 0443456A1 EP 91102171 A EP91102171 A EP 91102171A EP 91102171 A EP91102171 A EP 91102171A EP 0443456 A1 EP0443456 A1 EP 0443456A1
Authority
EP
European Patent Office
Prior art keywords
support
axis
spring
frame
bearing axis
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.)
Withdrawn
Application number
EP91102171A
Other languages
German (de)
English (en)
Inventor
Gerd Schulz
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
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 Individual filed Critical Individual
Publication of EP0443456A1 publication Critical patent/EP0443456A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65D—CONTAINERS FOR STORAGE OR TRANSPORT OF ARTICLES OR MATERIALS, e.g. BAGS, BARRELS, BOTTLES, BOXES, CANS, CARTONS, CRATES, DRUMS, JARS, TANKS, HOPPERS, FORWARDING CONTAINERS; ACCESSORIES, CLOSURES, OR FITTINGS THEREFOR; PACKAGING ELEMENTS; PACKAGES
    • B65D90/00—Component parts, details or accessories for large containers
    • B65D90/12—Supports
    • B65D90/14—Legs, e.g. detachable

Definitions

  • the invention relates to a support with a support tube which is rotatably mounted about a bearing axis on a frame of interchangeable bodies which can be mounted on vehicles, and with a support leg which is attached at an angle to the support tube and which lies between a substantially horizontal rest position on the frame and a substantially vertical support position below of the frame is pivotable, the pivoting movement from the rest position to the support position being braked to reduce the influence of gravity.
  • Such a support is known.
  • the pivoting movement is braked.
  • the braked pivoting movement can be implemented, for example, by a joint, as is disclosed in DE-OS 35 00 213.
  • Such a joint has a bearing pin, at one end of which the support tube is axially attached.
  • the bearing journal is mounted in a housing sleeve that is attached to the frame.
  • the bearing pin has an eccentric which carries a support sleeve which is supported on the housing sleeve by a brake sleeve made of elastic material. If the bearing pin is rotated, the eccentric grinds along the inner wall of the support sleeve, as a result of which the latter is pressed radially outward in the region of the eccentric and the braking effect of the bearing pin occurs in this way.
  • the object of the invention is therefore to develop a support of the type mentioned in such a way that the pivoting of the support leg from the support to the rest position can be carried out without great effort.
  • Folding up the support leg is considerably simplified by the invention, since the spring element takes over all or part of the force required to raise the support leg. Due to the effect of the spring force, even particularly heavy support legs can be pivoted from the support to the rest position without great effort.
  • the spring element must be tensioned in order to achieve the required spring force. This takes place during the opposite pivoting movement of the support leg from the rest position to the support position. During this pivoting movement, the spring element is tensioned so that the support leg has to be folded down against the spring force. In this way, the spring element also acts as a brake.
  • the spring force can be such that the support leg can still automatically reach the support position by the spring element not fully compensating for the gravitational influence acting on the support leg.
  • the advantage of the invention is that the spring element is the two for the movement of the support leg required functions combined, namely the braking function when folding down into the support position and the function of a drive for easier folding up into the rest position.
  • a particularly useful and effective embodiment of the invention is characterized in that the spring element is designed as a bar spring which is articulated with its first end at a first articulation point on the frame and in the direction of an angle to the bearing axis and through the two ends of the bar spring Spring axis acts on the support leg at a radial distance from the bearing axis.
  • This is a linear spring that is compressed between its two ends for tensioning.
  • Such a spring is particularly effective and can be used in particular to achieve higher spring forces.
  • the radial articulation of the bar spring preferably takes place in that the support tube is assigned a crank element, which extends radially to the bearing axis and has a second articulation point, on which the bar spring is articulated with its second end.
  • a further development of this embodiment is characterized in that during the pivoting movement of the support leg from the rest position into the support position, the bar spring is compressed against the spring pressure and the second articulation point of the bar spring describes a circular segment-shaped path which defines the first articulation point of the bar spring with the bearing axis radially connecting axis intersects and ends in an adjacent to this axis and between the first pivot point and the bearing axis end point.
  • the second articulation point i.e.
  • the articulation point of the bar spring on the crank element thus moves on a circular segment-shaped path that starts with the first articulation point of the bar spring on the frame Bearing axis radially connecting axis begins, this axis crosses at a right angle and ends in an end point lying adjacent to this axis.
  • the end point lies between the first articulation point and the bearing axis and has a shorter distance to the first articulation point than the starting point of the circular segment-shaped path.
  • the bar spring is relaxed a little. This ensures that the support leg actually remains in the support position by being pressed into this position by the bar spring.
  • This embodiment is particularly advantageous if the bar spring is designed so that the spring pressure of the bar spring fully compensates for the influence of gravity on the support leg before it reaches the support position and even outweighs it.
  • the angle between the axis radially connecting the end point with the bearing axis and the axis radially connecting the first articulation point with the bearing axis is approximately 5 °. To achieve the Such an effect as described above is sufficient between the end point and the dead center relative to the bearing axis.
  • crank element can abut against a stop attached to the frame in the rest position and in the support position of the support leg.
  • FIG. 1 Another embodiment, in which the support tube is displaceable along the bearing axis, is characterized in that an inner square is fastened within the support tube at its open end opposite the support leg, with which the support tube is axially inserted onto a square shaft which is attached to a Drive shaft is axially fixed, which is rotatably mounted on the frame, the support tube being telescopically displaceable between a first and a second end position along the square shaft.
  • This design results in a particularly simple construction in order to be able to pull out the support tube on the frame, the support tube not only being displaceable and rotatable directly on the frame, but also being rotatably mounted on the frame again via the non-rotatably connected cardan shaft.
  • a second pivot bearing is also formed with which the support tube is held on the frame. In this way, a particularly secure mounting of the support tube on the frame is formed.
  • crank element sits on the cardan shaft.
  • this embodiment is characterized in that at least one guide element is fastened to the frame, on which a holding plate is essentially horizontally displaceable but non-rotatably supported, which extends essentially transversely to the direction of displacement and on which the rod spring is articulated with its first end and the crank element is rotatable is fixed.
  • the entire arrangement on the guide element is thus held to be horizontally displaceable.
  • To attach the entire assembly to an interchangeable body (1) only the guide element has to be attached to the frame. This has the advantage that the bar spring with its first end and the crank element do not need to be held separately on the frame. This arrangement is particularly expedient for some applications, in particular when the space under the swap body is unfavorable. If you now want to move the support tube along the bearing axis, the holding plate with the rod spring articulated thereon and with the crank element rotatably fixed thereon is also displaced.
  • two parallel guide rods are provided as guide elements, which extend through bores in the holding plate. This construction results in a particularly simple displaceable mounting of the holding plate on the frame.
  • crank element can also be attached to the support tube in such a way that the spring axis of the bar spring only extends at a right angle to the bearing axis when the support tube is in a position between its two end positions.
  • the crank element is attached to the slidable support tube and thus slidable relative to the frame.
  • the bar spring can also be pivoted about its first articulation point, since its second articulation point can be moved along the bearing axis. Only when the support tube is in a certain position between its two end positions does the spring axis of the bar spring run at a right angle to the bearing axis. In this position, the bar spring is most compressed in comparison to the other positions of the support tube between its two end positions.
  • the bar spring is relaxed again in the direction of the two end positions. This makes it easier to pull out and push in the support on the frame.
  • the operator must overcome the spring force of the bar spring during the displacement of the support tube along the bearing axis on the first part of the displacement path, since it is tensioned.
  • the spring force - since it is now relaxed again - supports the displacement movement of the support tube.
  • the user does not have to use his full force over the entire displacement path of the support tube for pulling out or pushing in the support.
  • Another advantage of this design is that the bar spring always presses the support tube into the respective end position, whereby the support tube is locked.
  • the position of the support tube, in which the spring axis is perpendicular to the bearing axis, is preferably in the middle between the two end positions.
  • the two sections of the displacement path, during which the bar spring is tensioned and then relaxed again, are the same both when pulling out and when pushing in. In this way, the effort required to move the support tube is the same in both directions.
  • two bar springs opposite one another symmetrically to the bearing axis can be provided. This results in a better distribution of forces on the support tube.
  • the two bar springs can be of a smaller design than a single bar spring to achieve the same spring force.
  • the bar springs can be designed as commercially available gas pressure springs.
  • FIG. 1 shows a perspective view of an interchangeable body 1 which can be placed on interchangeable vehicles.
  • the interchangeable body 1 has a frame 2, on the undersides of which four supports 4 are mounted, of which only two supports 4 are visible in FIG. 1 due to the perspective view.
  • FIG. 1 shows the swap body 1 in a state removed from the swap vehicle (not shown), in which the swap body 1 is parked on its supports 4 on a stand area or the like. After placing the interchangeable body 1 on an interchangeable vehicle, the supports 4 are folded up into an essentially horizontal rest position on the frame 2. The supports 4 can thus be pivoted between this rest position and an essentially vertical support position below the frame 2, which is shown in FIG.
  • the support 4 has a support leg 6 and a support tube 8.
  • the support tube 8 is mounted on the frame 2 with the aid of a support bearing 10.
  • the support bearing 10 is designed so that the support tube is both rotatable about a bearing axis coinciding with its axis and also displaceable along the bearing axis.
  • the support leg 6 is attached to the support tube 8 at approximately a right angle. Due to the above-described design of the support bearing 10, the support 4 can be moved in the direction of movement 12 designated from the frame 2 and towards the frame 2 and the support leg 6 can be pivoted between the substantially horizontal rest position and the substantially vertical support position along the pivot path identified by 14 will.
  • the support leg 6 In the rest position, the support leg 6 is locked in a claw-shaped support bearing 16 on the frame 2. To fold down into the support position, the support is now first pulled out of the frame 2 along the direction of displacement 12, the support leg 6 being released from the support bearing 16. The support leg 6 can then be folded into the support position in the pulled-out position along the pivot path 14. As can also be seen from FIG. 2, there is a spring bolt 18 on the support bearing 10, which ensures that the support leg 6 is locked in the rest position and in the support position.
  • FIG. 3 shows a longitudinal section of the section of the support tube 8 opposite the support leg 6, with which the support 4 is held on the frame 2.
  • the support bearing 10 has a bearing sleeve 20 fastened to the frame 2, in which the support tube 8 is rotatably and displaceably mounted. It goes without saying that the inner cross section of the bearing sleeve 20 and the outer cross section of the section of the support tube 8 shown in FIG. 3 are circular are.
  • An inner square 24, which has a square sleeve 26, is inserted into the open end 22 of the support tube 8 opposite the supporting leg 6 (cf. FIG. 2).
  • a square shaft 28 extends through the square sleeve 26, the outer cross-sectional dimensions of which roughly match the inner cross-sectional dimensions of the square sleeve 26.
  • the square shaft 28 is axially attached to a pivot pin 32.
  • the hinge pin 32 is rotatably mounted in a hinge sleeve 34 which is attached to the frame 2.
  • a collar 38 is formed which projects beyond the square sleeve 26 in the radial direction.
  • the support tube 8 is rotatably mounted on the square shaft 28, but slidably along this.
  • the support tube 8 can thus be telescopically extended relative to the square shaft 28 and thus relative to the frame 2 in the direction of displacement 12.
  • FIG. 3 shows it in the pushed-together position, its end 22 abutting against that part of the frame 2 in which the pivot pin 32 is supported by means of a pivot sleeve 34.
  • the square sleeve 26 of the inner square 24 attached to the support tube 8 abuts against the collar 38 at the outer end 36 of the square shaft 28, so that the collar 38 serves as a stop in the extended position.
  • a further pivot bearing is provided formed for the support tube 8.
  • the axes of the support tube 8, the square sleeve 26, the square shaft 28, the hinge pin 32 and the hinge sleeve 34 coincide with one another and form a common bearing axis 40.
  • crank disk 42 As can be seen in FIG. 3, a crank disk 42, the radius of which is larger than that of the articulated pin 32 and the articulated sleeve 34, is axially fixed to the free end of the articulated pin 32. As FIG. 3 shows, the crank disk 42 is arranged on the side of the part of the frame 2 opposite the support tube 8 in which the joint sleeve 34 is seated.
  • FIG. 4 shows the crank disk 42 in plan view.
  • the crank disk 42 is connected to the frame 2 via two gas pressure springs 44a, b.
  • Each gas pressure spring 44a, b is articulated with a ball joint 46a, b to a first articulation point 48a, b lying on the associated joint axis on the frame 2.
  • the ball joint 46a, b is seated on a cylinder 50a, b from which a movable piston rod 52a, b protrudes, with which each gas pressure spring 44a, b is articulated on a second articulation point 54a, b on the associated joint axis on the crank disk 42.
  • Both gas pressure springs 44a, b are arranged point-symmetrically to the bearing axis 40, which also runs simultaneously through the pivot point of the crank disk 42.
  • the first articulation points 48a, b of both gas pressure springs 44a, b lie on an axis 56 which intersects the bearing axis 40 at a right angle.
  • the second articulation points 54a, b of both gas pressure springs 4a, b lie on an axis 58, which also intersects the bearing axis 40 at a right angle, and are at the same distance from the Bearing axis 40 arranged on the circumference of the crank disk 42.
  • the first and second articulation points 48a, 54a and 48b, 54b of each gas pressure spring 44a, b lie on a spring axis 60a, b, along which the piston rods 52a, b are displaceable for tensioning and relaxing the gas pressure springs 44a, b.
  • a block 62 projecting over the circumference is attached to the peripheral edge of the crank disk 42 and abuts a first stop 63 in the rest position of the support leg 6 and a second stop 64 in the support position.
  • the two stops 63, 64 are arranged on the frame 2 so that the crank disk 42 can make about a quarter-circle rotation with the block 62.
  • FIG. 4 shows the position of the crank disk 42 and the gas pressure springs 44a, b in the rest position of the support leg 6. In this position, the angle between the axis 58 and the spring axis 60 is 90 °. Thus, axes 56 and 58 and spring axis 60 together form a right triangle, the angle between axis 58 and axis 56 being less than 90 °.
  • the angle is preferably in the range from approximately 5 ° to 10 °.
  • the circular segment-shaped tracks 66a, b continue behind the points 68a, b lying on the axis 56 and end in an end point 70a, b lying adjacent to the axis 56. Between the points 68a, b and the end points 70a, b, the two gas pressure springs 44a, b are relaxed again somewhat. The points 68a, b can thus also be referred to as so-called dead points.
  • an angle ⁇ is formed between the axes 56 and 58, which is preferably in the range from approximately 5 ° to 10 °. If the swivel angle of the support leg 6 and thus the angle of rotation of the crank disk 40 is exactly 90 °, the angles and ⁇ are identical.
  • the angle ⁇ should be chosen small and the end point 70a, b should be close to the axis 56, so that the pivoting movement from the support position into the rest position only has to take place briefly against the pressure of the gas pressure springs 44a, b and after the dead centers 68a have been exceeded , b the gas pressure springs 44a, b relax and fold up the support legs 6 can support in the rest position.
  • FIG. 5 shows a further embodiment, which differs from the embodiment previously described with reference to FIGS. 3 and 4 in that the crank disk 42 'is fastened radially on the support tube 8, the two gas pressure springs 44a', b 'on the Crank rails 42 'are articulated by means of further ball joints 47a', b 'and the square shaft is omitted. Since the support tube 8 can be displaced along the bearing axis 40 in the direction of displacement 12, the gas pressure springs 44a ', b' are also additionally pivoted in the direction of displacement 12. As in the exemplary embodiment described above, the first articulation points 48a ', b' lie on a common axis 56 'which intersects the bearing axis 40 at a right angle.
  • crank disc 42 ' is attached to the support tube 8 so that the spring axes 60a', b 'of both gas pressure springs 44a', b 'only run at a right angle to the bearing axis 40 when the support tube 8 is in a central position between its two end positions .
  • the spring axes 60a ', b' also coincide with the axis 56 'and the gas pressure springs 44a', b 'are most compressed.
  • the gas pressure springs 44a ', b' are most relaxed in the two end positions of the support tube 8.
  • Figure 5 shows the support tube 8 in its inserted position.
  • the arrangement described above ensures that the gas pressure springs in addition to their previously described braking and drive function when pivoting the support leg 6 also for ensure a secure locking of the support tube 8 during its displacement in one of its two end positions.
  • the two gas pressure springs 44a ', b' are first compressed until their spring axes 60a ', b' have reached the axis 56 '. Then the gas pressure springs 44a ', b' can relax again, so that the pulling out of the support tube 8 on this part of the displacement path 12 is supported by the spring force of both gas pressure springs 44a ', b'. In the fully extended position, the spring axes of both gas pressure springs 44a ', b' lie at the same angle to axis 56 'as in the fully inserted position of support tube 8, but on the other side of axis 56'. This position is indicated by the dashed lines 60a ′′, b ′′ in FIG. 5.
  • FIG. 6 a further embodiment is shown in Figure 6, which differs from the previously described embodiments in that two guide rods 80a, b are provided, on which a holding plate 84 is essentially horizontally displaceable but non-rotatably mounted, which is essentially transverse to Movement direction 86 extends and on which two rod springs 44a ', 44b' are articulated with a first ball joint 46a 'and 46b' and the crank disc 42 'is rotatably fixed.
  • Both guide rods 80a, b run horizontally and parallel to each other and are u. a. attached to the frame 2 via a support bearing 82.
  • the holding plate 84 contains two bores, not shown in FIG. 6, through which the guide rods 80a, b extend.
  • a hinge pin 87 with a smaller diameter is attached to the free end of the support tube 8 and extends through a further bore in the holding plate 84.
  • the crank disk 42 ' is fastened, which in turn has a larger diameter than the bore and the pivot pin 87 inserted through it. In this way, the holding plate 84 is held immovably on the guide rods 80a, b relative to the support tube 8.
  • both gas pressure springs 44a 'and 44b' are articulated on the crank disk 42 'in the same way as was carried out using the previously described embodiments.
  • the stop in contrast to the embodiment shown in FIG. 4, in this embodiment the stop consists of a pin 90 which projects into a groove 91 which extends in a quarter circle on the crank disk 42 ′, as can be seen in FIG. 6b.
  • the guide rods 80a, b run close to the surface of the support tube 8, as can be seen in FIG. 6b.
  • the guide rods can also be at a greater distance from the support tube 8 and be arranged from each other, as outlined in Figure 6b by the reference numerals 80a 'and 80b'.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
EP91102171A 1990-02-17 1991-02-15 Support Withdrawn EP0443456A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4005140 1990-02-17
DE19904005140 DE4005140A1 (de) 1990-02-17 1990-02-17 Stuetze

Publications (1)

Publication Number Publication Date
EP0443456A1 true EP0443456A1 (fr) 1991-08-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91102171A Withdrawn EP0443456A1 (fr) 1990-02-17 1991-02-15 Support

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EP (1) EP0443456A1 (fr)
DE (1) DE4005140A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677623A1 (fr) * 1991-06-17 1992-12-18 Bulle Jean Marie Conteneur a bequilles escamotables dans les longerons lateraux.
EP0706912A1 (fr) * 1994-10-10 1996-04-17 ACKERMANN-FRUEHAUF GmbH Benne interchangeable
DE19607945A1 (de) * 1995-03-02 1996-10-10 Horst J Prof Dr Ing Roos Wechselbehälter mit Stützbeinen
FR2754223A1 (fr) * 1996-10-07 1998-04-10 I M C G Conteneur pour le transport combine "rail-route" de marchandises, a bequilles escamotables
EP3623319A1 (fr) * 2018-09-12 2020-03-18 Trailers Sp. z o.o. Gniotpol Conteneur interchangeable léger

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4223951A1 (de) * 1992-07-21 1994-01-27 Peter Dr Ing Boese Stützeinrichtung für Wechselbehälter
DE4231221A1 (de) * 1992-09-18 1994-03-24 Peter Suhrbier Container mit Stützeinrichtungen
DE4318029C2 (de) * 1993-05-29 1997-07-10 Schneider Fahrzeug Und Contain Für Wechselbehälter bestimmtes Stützbein mit Hebehilfe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7626625U1 (de) * 1976-08-25 1976-12-16 Fa. Albert Schnetz, 8000 Muenchen Vorrichtung zur Dämpfung bzw. Regulierung der Bewegungsgeschwindigkeit von Maschinenteilen, Schiebetoren o.dgl
DE3407390A1 (de) * 1984-02-29 1985-08-29 Wihag Nutzfahrzeugtechnik Gmbh & Co Kg, 4800 Bielefeld Winkelfoermiger stuetzfuss fuer wechselaufbauten von lastkraftwagen
DE3500213A1 (de) * 1985-01-05 1986-07-17 Gerd Schulz Fahrzeug- und Container Technik, 3549 Wolfhagen Lagervorrichtung fuer abzubremsende drehbare oder schwenkbare teile

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7626625U1 (de) * 1976-08-25 1976-12-16 Fa. Albert Schnetz, 8000 Muenchen Vorrichtung zur Dämpfung bzw. Regulierung der Bewegungsgeschwindigkeit von Maschinenteilen, Schiebetoren o.dgl
DE3407390A1 (de) * 1984-02-29 1985-08-29 Wihag Nutzfahrzeugtechnik Gmbh & Co Kg, 4800 Bielefeld Winkelfoermiger stuetzfuss fuer wechselaufbauten von lastkraftwagen
DE3500213A1 (de) * 1985-01-05 1986-07-17 Gerd Schulz Fahrzeug- und Container Technik, 3549 Wolfhagen Lagervorrichtung fuer abzubremsende drehbare oder schwenkbare teile

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2677623A1 (fr) * 1991-06-17 1992-12-18 Bulle Jean Marie Conteneur a bequilles escamotables dans les longerons lateraux.
WO1992022481A1 (fr) * 1991-06-17 1992-12-23 Bulle Jean Marie Conteneur a bequilles escamotables dans les longerons lateraux
US5368179A (en) * 1991-06-17 1994-11-29 Bulle; Jean-Marie Container having props which can be folded away into the lateral structural members
EP0706912A1 (fr) * 1994-10-10 1996-04-17 ACKERMANN-FRUEHAUF GmbH Benne interchangeable
DE19607945A1 (de) * 1995-03-02 1996-10-10 Horst J Prof Dr Ing Roos Wechselbehälter mit Stützbeinen
DE19607945C2 (de) * 1995-03-02 1999-11-04 Horst J Roos Wechselbehälter mit Stützbeinen
FR2754223A1 (fr) * 1996-10-07 1998-04-10 I M C G Conteneur pour le transport combine "rail-route" de marchandises, a bequilles escamotables
WO1998015475A1 (fr) * 1996-10-07 1998-04-16 I.M.C.G. S.A.R.L Conteneur pour le transport combine 'rail-route' de marchandises, a bequilles escamotables
EP3623319A1 (fr) * 2018-09-12 2020-03-18 Trailers Sp. z o.o. Gniotpol Conteneur interchangeable léger

Also Published As

Publication number Publication date
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