EP2466156A1 - Cylindre hydraulique télescopique - Google Patents

Cylindre hydraulique télescopique Download PDF

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Publication number
EP2466156A1
EP2466156A1 EP10195427A EP10195427A EP2466156A1 EP 2466156 A1 EP2466156 A1 EP 2466156A1 EP 10195427 A EP10195427 A EP 10195427A EP 10195427 A EP10195427 A EP 10195427A EP 2466156 A1 EP2466156 A1 EP 2466156A1
Authority
EP
European Patent Office
Prior art keywords
groove
tube
hydraulic cylinder
telescopic hydraulic
piston
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Withdrawn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
EP10195427A
Other languages
German (de)
English (en)
Inventor
Michiel Petrus Celina Omère Moorthamer
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.)
Hyva Holding BV
Original Assignee
Hyva Holding BV
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=43902643&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2466156(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hyva Holding BV filed Critical Hyva Holding BV
Priority to EP10195427A priority Critical patent/EP2466156A1/fr
Priority to EP11193278.6A priority patent/EP2466157B1/fr
Priority to BRPI1106869-8A priority patent/BRPI1106869B1/pt
Priority to CN201110414287.9A priority patent/CN102588381B/zh
Priority to TR2018/02819T priority patent/TR201802819T4/tr
Publication of EP2466156A1 publication Critical patent/EP2466156A1/fr
Withdrawn legal-status Critical Current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
    • F15B15/14—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 concerns a telescopic hydraulic cylinder in accordance with the preamble of claim 1.
  • a sideways force on an extended piston or tube that results in a bending moment in the lower end of an inner tube and a similar bending moment in the adjacent top end of a concentric outer tube.
  • This bending moment leads to bending stress in the tube and stress concentration in a sharp corner of the inner groove might lead to rupture of the tube.
  • High fluid pressure in the telescopic hydraulic cylinders increases the risk of rupture as the high fluid pressure also leads to stress in the tubes and this adds to the bending stress.
  • the stress concentration in the inner groove also applies to this added stress.
  • the telescopic hydraulic cylinder is according to claim 1. In this way, stress concentration in a high loaded part of the tubes is avoided and the resistance against bending increases.
  • the telescopic hydraulic cylinder is according to claim 2. In this way, the resistance against bending is further increased.
  • the telescopic hydraulic cylinder is according to claim 3.
  • the inner relief groove and/or the outer relief groove are not subjected to the axial load on the tubes but only to the bending moment in the tubes.
  • the telescopic hydraulic cylinder is according to claim 4.
  • the relief grooves are most effective for relieving the stress without reducing the minimum section surface of the tube.
  • the telescopic hydraulic cylinder is according to claim 5.
  • the minimum section surface of the tubes gradually increases thereby avoiding sudden increases that might lead to stress concentrations.
  • the telescopic hydraulic cylinder is according to claim 6. In this way, the contact area between the stop rings in extended position is large so that surface stress between the stop rings is reduced.
  • the telescopic hydraulic cylinder is according to claim 7.
  • the inner stop ring groove and/or the outer stop ring groove are smaller, less deep and give less stress concentration.
  • the telescopic hydraulic cylinder is according to claim 8 or 9.
  • the tube has a small wall thickness so that the weight of the telescopic hydraulic cylinder is reduced.
  • FIG. 1 shows a kipper 1 comprising a tractor 4 and a trailer 5.
  • a hinge 8 connects a frame of the trailer 5 and a tipping body 2 and a telescopic hydraulic cylinder 3 can lift the tipping body 2 to a tilted position for unloading the tipping body 2.
  • the trailer 5 has axles with wheels to support the frame of the trailer 5 on the terrain.
  • the terrain might have mounds 6, so that a rear axle 7 and with that the hinge 8 can be slightly inclined whereby the trailer 5 has a slight twist.
  • the inclination of the hinge 8 can cause sideways movement of the tipping body 2 relative to the trailer 5 and in extreme situations this might lead to rolling over of the kipper 1 during lifting of the tipping body 2.
  • the telescopic hydraulic cylinder 3 can reduce the sideways movement of the tipping body 2 relative to the trailer 5 during tipping.
  • FIG. 2 and figure 3 show the telescopic hydraulic cylinder 3.
  • Two chassis brackets 13 are mounted on the trailer 5 and support two chassis trunnions 12 that support a base tube 14.
  • the base tube 14 can swivel around a base tube swivel axis 28 in the chassis brackets 13; the base tube swivel axis 28 is mounted parallel to the axis of hinge 8.
  • the base tube 14 has a centreline 24, a bottom plate 29, and a high-pressure connection 15.
  • a tube 23 can slide in the direction of the centreline 24 in the base tube 14.
  • a tube 22 can slide in the direction of the centreline 24 in the tube 23.
  • a tube 21 can slide in the direction of the centreline 24 in the tube 22.
  • a tube 20 can slide in the direction of the centreline 24 in the tube 21.
  • the bottom plate 29 can support the tubes 20, 21, 22, and 23.
  • a piston 19 can slide in the tube 20 in the direction of the centreline 24.
  • the shown embodiment has four tubes that can slide relative to the piston 19 and the base tube 14, in other embodiments, this number of tubes can have any value above zero.
  • the piston 19 is made from a tube and is closed at the underside by a plate 30 and at the top by a plug 17.
  • the plug 17 and a top plate 18 are connected and the top plate 18 is connected to a cover tube 9.
  • a spherical ring 27 that is coupled to the cover tube 9 supports a lifting ring 16 with lifting trunnions 11 that swivably connect the lifting ring 16 to lifting brackets 10.
  • the lifting ring 16 can rotate around a top swivel axis 25.
  • the lifting brackets 10 couple the telescopic hydraulic cylinder 3 to the tipping body 2, whereby the top swivel axis 25 and the base tube swivel axis 28 are parallel to the axis of the hinge 8.
  • a spherical bearing 27 between the lifting ring 16 and the spherical ring 27 compensates for alignment errors between the top swivel axis 25, the base tube swivel axis 28 and the axis of the hinge 8.
  • the tipping body 2 and the piston 19 are coupled and the position of the tipping body 2 determines the position of the piston 19 in the telescopic hydraulic cylinder 3.
  • the base tube 14 and the tubes 20, 21, 22, and 23 have near the top end of their inside surface a groove into which a seal 37 is mounted to seal the gap between the base tube 14, the tubes 20, 21, 22, or 23 or the piston 19.
  • Each seal 37 can slide over an outside surface of an adjacent tube 20, 21, 22, or 23 or the outside surface of the piston 19 and the seals 37 are suitable for the high pressure in the telescopic hydraulic cylinder 3 and seal the area inside the telescopic hydraulic cylinder 3 from the surroundings.
  • the wipers 40 mounted in a groove at the top end of the inside surfaces of the base tube 14 and the tubes 20, 21, 21, 22, and 23, remove contaminations from the outside surfaces of the tubes 20, 21, 22, and 23 and the piston 19 and prevent dirt entering the gaps.
  • the inside surfaces have an upper wear ring 39 mounted at the top in grooves, under the upper wear ring 39 a lower wear ring 38, and at the bottom mounted in grooves in the outside surfaces a slider 33.
  • the upper wear rings 39 and the lower wear rings 38 are mounted between the seal 37 and the wiper 40.
  • Inner lift rings 31 that interact with outer lift rings 32 or with a slider 33 ensure that the tubes 20, 21, 22 and 23 move together with the piston 19 in outward direction.
  • the inner lift rings 31 are mounted in grooves in the inside surface of the tubes 20, 21, 22, and 23.
  • the outer lift rings 32 are mounted in grooves in the outside surfaces of the piston 19 and the tubes 20 and 21.
  • the slider 33 in tube 22 acts in a similar manner as an outer lift ring 31.
  • the upward movement of the tube 23 stops when an outer stop ring 35 of the tube 23 interacts with an inner stop ring 36 of the base tube 14 and the tube 23 has reached its maximum extension.
  • the outer stop rings 35 are mounted in grooves in the outer surfaces of the piston 19 and the tubes 20, 21, 22, and 23.
  • the inner stop rings 36 are mounted in grooves in the inner surface of the base tube 14 and the tubes 20, 21, 22, and 23.
  • Figure 4 shows the transition between tube 22 and tube 23 when they are in extended position and the inner stop ring 36 and the outer stop ring 35 interact.
  • the shown transition is exemplary for the other transitions between the base tube 14, the tubes 20, 21, 22 and 23, and the piston 19 and the shown transition is similar between the other tubes 20, 21, the base tube 14, and the piston 19.
  • the telescopic hydraulic cylinder 3 stabilises the transversal movement of a lifted tipping body 2 by exerting a transverse force F H on the tipping body 2.
  • This transverse force F H causes a bending moment M in the extended telescopic hydraulic cylinder 3 and this bending moment M is highest near the trailer 5.
  • This bending moment M causes bending of the tubes 14, 20, 21, 22 and 23 in the longitudinal direction and deformation of the circular section of the tubes 14, 20, 21, 22 and 23 to a slightly oval section. This means that the bending moment M causes bending stress in the base tube 14 and the tubes 20, 21, 22, and 23.
  • the bending moment is indicated as bending moment M 22-23 .
  • the bending moment M 22-23 causes a force P between the upper wear ring 39 and the outer surface of tube 22 and a force Q between the slider 33 and the inner surface of tube 23.
  • the grooves of the outer stop ring 35 and the inner stop ring 36 reduce the strength of the tubes 22, 23 the grooves form the weakest part of the tubes, especially for the inside tube 22 that has the smallest diameter.
  • the grooves can have a depth of more than 20 % of the wall thickness of the tube 22,23 for the outer groove and more than 25% of the inner groove to make it possible that the stop rings 35,36 transmit the axial forces between the adjacent tubes 22,23.
  • a relief groove 41 reduces the stress in the bottom of the groove of the outer stop ring 35 and so reduces the risk of damages.
  • Figure 5 shows various embodiments of the relief groove 41 in an outer surface of a tube.
  • Figure 5a shows an embodiment wherein a small ridge limits the axial movement of the outer stop ring 35 and wherein the groove has a depth that is approximately equal to the depth of the groove for the outer stop ring 35.
  • Figure 5b shows an embodiment with a relief groove 41 with a large radius form the bottom of the groove for the outer stop ring 35 to the outside diameter with a width of at least the twice the width of the groove for the outer stop ring 35.
  • Figure 5c shows a similar embodiment with a relief groove 41 with a conical surface. The minimum diameter of the relief groove 41 is approximately equal to the diameter of the groove for the outer stop ring 35.
  • Figure 5d shows an embodiment of the relief groove 41 with a depth that is approximately equal to the depth of the groove for the outer stop ring 35 and that has a width that smaller than its depth and of which the bottom is a radius.
  • a second and possibly a third narrow relief groove is adjacent to the first relief groove 41 wherein the second groove and the third groove have a decreasing depth.
  • the relief grooves will have similar dimensions.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Forklifts And Lifting Vehicles (AREA)
EP10195427A 2010-12-16 2010-12-16 Cylindre hydraulique télescopique Withdrawn EP2466156A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP10195427A EP2466156A1 (fr) 2010-12-16 2010-12-16 Cylindre hydraulique télescopique
EP11193278.6A EP2466157B1 (fr) 2010-12-16 2011-12-13 Cylindre hydraulique télescopique
BRPI1106869-8A BRPI1106869B1 (pt) 2010-12-16 2011-12-13 cilindro hidráulico telescópico
CN201110414287.9A CN102588381B (zh) 2010-12-16 2011-12-13 可伸缩液压缸
TR2018/02819T TR201802819T4 (tr) 2010-12-16 2011-12-13 Teleskopik hidrolik silindir.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10195427A EP2466156A1 (fr) 2010-12-16 2010-12-16 Cylindre hydraulique télescopique

Publications (1)

Publication Number Publication Date
EP2466156A1 true EP2466156A1 (fr) 2012-06-20

Family

ID=43902643

Family Applications (2)

Application Number Title Priority Date Filing Date
EP10195427A Withdrawn EP2466156A1 (fr) 2010-12-16 2010-12-16 Cylindre hydraulique télescopique
EP11193278.6A Active EP2466157B1 (fr) 2010-12-16 2011-12-13 Cylindre hydraulique télescopique

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP11193278.6A Active EP2466157B1 (fr) 2010-12-16 2011-12-13 Cylindre hydraulique télescopique

Country Status (4)

Country Link
EP (2) EP2466156A1 (fr)
CN (1) CN102588381B (fr)
BR (1) BRPI1106869B1 (fr)
TR (1) TR201802819T4 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2584204A1 (fr) 2011-10-20 2013-04-24 Hyva Holding BV Cylindre hydraulique télescopique
GB2511745A (en) * 2013-03-11 2014-09-17 Jonic Engineering Ltd Telescopic hydraulic piston arrangement
EP2924300A1 (fr) * 2014-03-27 2015-09-30 Wipro Infrastructure Engineering Oy Vérin hydraulique télescopique et tube de revêtement d'un vérin hydraulique télescopique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015154856A2 (fr) * 2014-04-07 2015-10-15 Caterpillar Global Mining Europe Gmbh Support de manchon pour un vérin hydraulique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2004117A1 (de) * 1969-02-14 1970-09-03 Nummi Oy Anordnung an einem Teleskopzylinder
GB1590773A (en) * 1976-08-20 1981-06-10 Telehoist Ltd Telescoping mechanisms
EP0450501A1 (fr) * 1990-04-06 1991-10-09 Walter Neumeister Vérin

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3805681A (en) * 1972-11-22 1974-04-23 Towmotor Corp Lift cylinder assembly for lift truck mast and carriage
CN2937587Y (zh) * 2006-07-28 2007-08-22 中煤张家口煤矿机械有限责任公司 新型单作用伸缩液压缸
CN201326604Y (zh) * 2008-11-07 2009-10-14 山东临清迅力变压器有限公司 新型伸缩式套筒液压举升缸
CN201568395U (zh) * 2009-12-15 2010-09-01 东风汽车公司 无台阶伸缩式套筒液压缸缸筒

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2004117A1 (de) * 1969-02-14 1970-09-03 Nummi Oy Anordnung an einem Teleskopzylinder
GB1590773A (en) * 1976-08-20 1981-06-10 Telehoist Ltd Telescoping mechanisms
EP0450501A1 (fr) * 1990-04-06 1991-10-09 Walter Neumeister Vérin

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2584204A1 (fr) 2011-10-20 2013-04-24 Hyva Holding BV Cylindre hydraulique télescopique
US9371846B2 (en) 2011-10-20 2016-06-21 Hyva Holding B.V. Telescopic hydraulic cylinder
GB2511745A (en) * 2013-03-11 2014-09-17 Jonic Engineering Ltd Telescopic hydraulic piston arrangement
GB2511745B (en) * 2013-03-11 2017-05-03 Jonic Eng Ltd Telescopic hydraulic piston arrangement
EP2924300A1 (fr) * 2014-03-27 2015-09-30 Wipro Infrastructure Engineering Oy Vérin hydraulique télescopique et tube de revêtement d'un vérin hydraulique télescopique

Also Published As

Publication number Publication date
EP2466157B1 (fr) 2017-11-29
BRPI1106869A2 (pt) 2013-04-09
CN102588381B (zh) 2016-01-20
CN102588381A (zh) 2012-07-18
EP2466157A1 (fr) 2012-06-20
BRPI1106869B1 (pt) 2021-03-09
TR201802819T4 (tr) 2018-03-21

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