EP1907708B1 - Cylindre d'actionnement - Google Patents

Cylindre d'actionnement Download PDF

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Publication number
EP1907708B1
EP1907708B1 EP06776415.9A EP06776415A EP1907708B1 EP 1907708 B1 EP1907708 B1 EP 1907708B1 EP 06776415 A EP06776415 A EP 06776415A EP 1907708 B1 EP1907708 B1 EP 1907708B1
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EP
European Patent Office
Prior art keywords
actuating cylinder
piston
guide
guiding
running surface
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.)
Active
Application number
EP06776415.9A
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German (de)
English (en)
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EP1907708A1 (fr
Inventor
Michael Ruopp
Christian Schweigl
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.)
Gustav Magenwirth GmbH and Co KG
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Gustav Magenwirth GmbH and Co KG
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Publication of EP1907708A1 publication Critical patent/EP1907708A1/fr
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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
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F15B15/1452—Piston sealings

Definitions

  • the invention relates to an actuating cylinder, for example for drive or braking devices of vehicles, comprising a cylinder housing with an enclosed by this interior, a piston arranged in the interior, which is guided in a guide direction by at least one tread of the cylinder housing and a piston head a pressure chamber limited in the cylinder housing, and held on the piston and arranged circumferentially around this sealing element for sealing the pressure space between the piston and the cylinder housing.
  • Such actuating cylinders are known from the prior art, for example from FR2855142 , In these, there is the problem that the piston experiences forces when operating the intended vehicle part, which act on the piston in the direction of a tilting movement.
  • the invention is therefore based on the object to improve an actuating cylinder of the generic type such that the occurring wear is minimized.
  • the sealing element is part of a sliding element comprising a guide element, that the guide element is guided movably in the guide direction with at least one guide surface on a first running surface of the cylinder housing and in that the guide element floatingly guides the piston relative to the first running surface.
  • the advantage of the solution according to the invention is the fact that with this the wear by friction of the piston is minimized at the first tread and thus a longer life of the actuating cylinder is achieved.
  • the guide element guides the piston essentially without contact to the first running surface, so that thereby no wear on the running surface caused by the piston occurs.
  • a particularly expedient solution provides that there is a gap of at least 1/10 mm between the outside of the piston facing the first running surface and the first running surface with the piston centered.
  • a particularly simple and cost-effective solution with regard to the arrangement of the sliding element provides that the sliding element is arranged in a receptacle in the region of an outer side of the piston.
  • the fixation of the sliding element in the receptacle can be made arbitrarily. It is particularly simple in terms of design if the sliding element is held positively fixed in the receptacle.
  • the slider is made as an annular body made of an elastic material, which can thus be inserted through this in the circumferential direction in the recording and fixed in this form-fitting manner.
  • fixation can also be done in different ways. It has proved to be expedient if the sliding element rests with a bearing surface on a contact surface of the receptacle and is thus supported in particular in the receptacle in the radial direction to a central axis.
  • the sliding element bears against a flange surface of the receptacle with a foot surface extending transversely to the guide direction.
  • a foot surface extending transversely to the guide direction.
  • sealing element With regard to the arrangement of the sealing element relative to the guide element so far no details have been made. Thus, it would be conceivable in principle to arrange sealing element and guide element in a different order relative to the pressure chamber.
  • sealing element is arranged on a pressure chamber facing side of the guide element.
  • an advantageous embodiment provides that the sealing element and the guide element form an integral part, so that the guide element and the sealing element can be produced in a simple manner as a one-piece continuous part.
  • a favorable variant provides in this case that the guide element has a support body, from which starting the sealing element extends.
  • the sealing element has an outer sealing lip and an inner sealing lip, which extend V-shaped to one another.
  • Such a constructed sealing element is particularly suitable to achieve a tight seal between the piston and the cylinder housing, even at a high pressure in the pressure chamber.
  • sealing lips are arranged on a side opposite the foot surface side of the support body.
  • the sealing lips are formed so that the outer sealing lip rests with a sealing lip edge on the first tread.
  • the inner sealing lip rests with a sealing lip edge on a contact surface of the piston.
  • an expedient solution provides that the at least one guide surface is arranged on a side of the sealing element which is opposite to the pressure chamber, thereby resulting in a particularly compact construction of the sliding element.
  • the at least one guide surface is arranged in the region of the support body.
  • the at least one guide surface is arranged on an elastically deformable region of the support body, so that it is possible to obtain a contact force in the region of the guide surface by deformation of the support body during installation of the guide element.
  • an elastic, acting on the at least one guide surface contact pressure has the advantage that so that the guide surface can be used not only for guiding the piston, but also at the same time in addition to the seal, in particular for sealing against partially resulting in the pressure chamber vacuum at a sealing element with sealing lips can only be controlled by structurally complex measures.
  • an advantageous embodiment provides that the at least one guide surface is arranged on a guide bead of the guide element and thus projects beyond the usual contour of the guide element.
  • a particularly favorable arrangement of the guide bead provides that it adjoins a foot surface of the support body.
  • the guide bead has an extent in the direction of the height H of the sliding element which corresponds to at least one fifth of the extent of the supporting body in the direction of the height H.
  • the guide bead extends in the direction of the height H of the sliding element over a maximum of half the extent of the support body in the direction of the height H.
  • a guide bead with one or more of the features described above has the advantage that thus a sufficiently large radially acting force acts on the support body and the support body in the region of a bearing surface of the sliding element to a corresponding contact surface of the recording applies, so that a tilting movement the entire sliding element can be largely avoided around an axis perpendicular to the cross-sectional area.
  • the guide element not only has a guide surface, but a plurality of guide surfaces.
  • each of the guide surfaces is arranged on a guide bead.
  • An expedient solution provides that the guide surface with the greatest radial extent is arranged next to the pressure chamber and that at least one further guide surface with a smaller radial extent is arranged on a side of the first guide surface opposite the pressure chamber.
  • the provision of the recesses has the advantage that in these can collect lubricant, which also serve to ensure the best possible lubrication and thus ease of movement of the guide element relative to the tread in the region of the guide surfaces.
  • depressions are formed annularly encircling and thus preferably form recessed grooves.
  • the ratio of an inner diameter of the receptacle to the outer diameter of the piston is greater than about 0.7, more preferably greater than about 0.8.
  • an advantageous solution provides that with an outer diameter of the piston of at least 20 mm, the height of the sliding element in the range of about 1.5 to about 4.5 mm, more preferably in the range of about 2 mm to about 3.5 mm.
  • a value for the height of the slider is between about 2.5 mm and about 3 mm.
  • the ratio of an outer diameter of the piston to the height of the sliding element is greater than about 8, more preferably greater than about 10, is.
  • the width B thereof is greater than half the height H.
  • the width B of the sliding element is greater than about 0.8 times the height H.
  • the height H of the slider is less than about 1.3 times the width B, even better, if the height H is less than about 1.2 times, even better the 1 , 1 times the width B.
  • the sliding element with more than about 50% of its extension in height serves to guide the piston.
  • an outer sealing lip has a lower height than an inner sealing lip in order to improve the sealing effect.
  • a particularly favorable solution with regard to a tilting movement of the piston provides that the cylinder housing has a second running surface which is arranged at a distance from the first running surface in the guide direction.
  • a particularly advantageous solution provides that the second running surface is arranged in the interior of the cylinder housing.
  • a particularly preferred embodiment provides that the piston is guided on the second running surface with a guide head extending from the piston head.
  • the second running surface has the same or a smaller diameter than the first running surface.
  • the piston is acted upon by a resilient force accumulator arranged in the cylinder housing in the direction of an extended end position with a maximum pressure chamber.
  • the piston In order to further obtain optimum power transmission to the element to be actuated, provision is expediently made for the piston to be provided with a pressure-transmitting element.
  • the pressure-transmitting element is a component with a spherical shape, which is preferably punctually acted upon by the piston.
  • the pressure transmission element is a component which can be acted upon by the piston surface.
  • Such a pressure transmission element is favorably a ball, which rests substantially punctiform on the element to be actuated and thus also largely reduces the transmission of tilting moments on the piston.
  • An in Fig. 1 illustrated embodiment of a hydraulic cylinder 10 comprises a cylinder housing 12, which encloses an interior space 14 in which a designated as a whole by 16 piston is arranged, which is movable in a guide direction 18 relative to the cylinder housing 12.
  • the piston 16 comprises a piston head 20, which extends transversely to the guide direction 18 in the direction of a central axis 24 of the cylinder housing 12 cylindrical first raceway 22 of the cylinder housing 12, which encloses a first, piston bottom side portion 14 a of the interior 14.
  • the piston head 20 is arranged and dimensioned so that a maximum radius to the central axis 24 extending outside 26 of the piston head 20 usually does not touch the tread 22, but between this outer side 26 and the tread 22, a gap 28 remains, which at Central axis 24 centered arrangement of the piston crown 20 is at least 5/100 mm. That is, the outer side 26 has a maximum diameter that is at least 1/10 mm smaller than an inner diameter of the tread 22.
  • the piston head 20 comprises a receptacle 32, which is arranged in the region of the outside 26 and circumscribes in the form of a depression, in which a first embodiment of a sliding element 30 is arranged, which comprises a guide element 34 on the one hand and a sealing element 36 on the other hand, the sealing element 36 having one within the Inner space 14 existing pressure chamber 40 seals in the area between the tread 22 and the piston head 20, while the guide member 34, the piston head 20 on the running surfaces 22 floating and substantially non-contact and in the guide direction 18 slidably.
  • a guide extension 42 is formed on a side facing the interior 14, which extends into the interior 14 of the cylinder housing 12 starting from the piston head 20 and forms a guide head 44, softer in turn provided with the guide head 44 alignment surfaces 46 at a second Running surface 52, formed in the cylinder housing 12 is guided, wherein the second running surface 52 encloses a second, inner portion 14b of the inner space 14.
  • the alignment surfaces 46 slide directly on the second running surface 52.
  • the piston 16 is guided in duplicate, namely on the one hand with the guide member 34 on the first tread 22 in the region of a first guide plane 56 and at a distance from the first guide plane 56 by means of sliding guide surfaces on the second running surfaces 44 aligning surfaces 46 in one second management level 58, on a the Pressure chamber 40 facing side of the first guide plane 56 and approximately parallel to this extends at a distance, so that overall results in a stable, substantially tilt-free guidance of the piston 16 in the cylinder housing 12.
  • the stable tilt-free guidance of the piston 16 is also given in an arrangement of the guide head 44 on a side facing away from the pressure chamber 40.
  • a supply channel 60 leads into the interior 14, which preferably opens into the second subregion 14b and via which a medium, in particular hydraulic medium, can be supplied to the interior 14, which acts on the piston 16 in the event of pressurization.
  • a connecting channel 62 is provided, via which directly from the supply channel 60 pressurized medium in the first portion 14a of the inner space 14 can be introduced.
  • a recess 62 is provided, in which an elastic force accumulator 64, for example in the form of a spring sits, which on the one hand on the piston 16 and on the other hand on the cylinder housing 12, for example in an end region of the supply channel 60, truncated.
  • This elastic force accumulator 64 acts on the piston 16 in such a way that, in the state not acted upon by the medium, it always moves into its position corresponding to a maximum volume of the pressure chamber 40.
  • a dome-shaped receptacle 66 for a pressure element 68 is provided in the piston head 20, with which then the actuating shaft is directly acted upon.
  • the receptacle 66 is provided with a contact surface 67, which is set back relative to the first guide plane 56 and that on an opposite side of the actuating shaft, resulting in an advantageous manner a "pulling action" on the pressure element 68 results, which has the consequence the piston 16 does not buckle laterally.
  • the pressure element 68 acts substantially punctiform on the contact surface 67 and substantially punctiform on the actuating shaft in order to also be able to move it in the guide direction 18.
  • the second running surface 52 is formed such that, although it is arranged coaxially with the first running surface 22, it has a diameter which is appreciably smaller than the first running surface 22 having.
  • the piston 16 experiences a sufficient guidance in the guide direction 18, wherein the piston head 20 or the guide head 44 relative to the first tread 22 and the second tread 52 can move substantially without jamming in the guide direction 18.
  • the guide ratio results from the diameter of the piston crown 20 and the distance between the guide planes 56 and 58.
  • the sliding member 30 comprises a support body 80 which rests with a transversely to the guide direction 18 extending foot surface 82 on a flange 84 of the receptacle 32 in the piston head 20 which extends against the outside 26 recessed into the piston head 20 and into a radial abutment surface 86th the recording 32 in the piston head 20 passes.
  • a radial abutment surface 86 of the support body 80 is supported with a support surface 88 radially to the central axis 24, wherein the ring encircling support body 80 due to its own bias in the circumferential direction with the bearing surface 88 kraftbeaufschlagt rests against the radial abutment surface 86.
  • a diameter DA of the radial abutment surface 86 of the receptacle 32 is more than 0.8 times an outer diameter DK of the piston head 20 on the outer side 26.
  • the sliding element 30 has a height H (FIG. Fig. 2 ) ranging between about 1.5 mm and about 4.5 mm. Further, the ratio of the outer diameter DK to the height H is greater than about 10.
  • a radial width B of a cross section of the sliding element greater than or equal to half the height H, in particular greater than or equal to two thirds of the height H.
  • the height H is less than about 1.3 times the height H.
  • the supporting body 80 carries, on its side facing the bearing surface 88 and facing the first running surface 22, for example three guide beads 92, 94, 96 which are arranged one above the other in the guide direction 18 and for example the guide bead 92 closest to the pressure space 40 is the first guiding bead.
  • the guide bead 94 of the second guide bead arranged on a side of the first guide bead 92 opposite to the pressure chamber 40 and the guide bead 96 arranged on a side of the second guide bead 94 opposite the first guide bead 92 are the third guide bead.
  • Each of these guide beads 92, 94, 96 forms a radially outer guide surface 102, 104 and 106, with which the support body 80 rests against the first running surface 22 and is thereby guided on this.
  • the voltage applied to the running surface 22 part of the sliding member 30, in particular of the guide beads 92, 94, 96 having part over more than 50% of the height H of the sliding member 30th
  • the first guide surface 102 has the largest radius, for example, while the guide surfaces 104 and 106 have approximately the same smaller radii, for example exhibit.
  • all guide surfaces 102, 104, 106 has a radius which is greater than the radius of the first tread 22.
  • a radially acting elastic force 108 presses the support body 80 with the radial support surface 88 against the radial abutment surface 86 and on the other hand, the guide beads 92, 94 and 96 with their guide surfaces 102, 104 and 106 presses against the tread 22.
  • the radial deformation of the seated in the receptacle 32 in the piston head 20 supporting body 80 when inserted into the cylinder housing 12 about 0.1 mm to about 2 mm from the not inserted into the housing 12 state.
  • recessed extending recessed grooves 112 and 114 are provided which, as in particular in Fig. 2 shown as Adjusters serve for the lubricant collecting between the guide surfaces 102, 104 and 106 and simultaneously cause lubrication in the area of the guide surfaces 102, 104 and 106 during the movement of the sliding element 30 in the guide direction 18.
  • the support body 80 forms with the guide beads 92, 94 and 96 and the seated on these guide surfaces 102, 104 and 106, the guide member 34, with which the floating guide of the piston head 20 and thus of the piston 16 in the first guide plane 56 to the first Running surfaces 22 such that the outer side 26 of the piston head 20, the first tread 22 is not substantially touched and consequently occurring in conventional hydraulic cylinders "shrinkage" of the tread 22 due to the mechanical wear can be avoided.
  • the sealing element 36 is provided, which is integrally molded to the guide member 34 and an outer sealing lip 120 and an inner sealing lip 122 which are V-shaped to each other and in their foot areas 124 and 126 pass into the support body 80.
  • the inner sealing lip 122 is higher in the direction of the height H than the outer sealing lip 120 in order to improve its sealing effect.
  • the inner sealing lip 122 and the outer sealing lip 120 thus lie on a pressure chamber 40 facing side of the support body 80 and extend in the non-applied state of the sliding ring 30 in the radial direction Central axis 24 on the one hand on the support surface 88 inwardly and on the guide surface 102 to the outside to form a gap 128 between the outer sealing lip 120 and the inner sealing lip 122nd
  • the sealing lips 120 and 122 are acted upon insertion of the sliding member 30 in the hydraulic cylinder 10 toward each other, so that the gap 128 decreases.
  • the outer sealing lip 120 is located with a sealing edge 130 under radial elastic bias on the tread 22, while the inner sealing lip 122 abuts with an inner sealing edge 132 on the radial abutment surface 86 of the piston crown 20.
  • a radial biasing force 138 is created in the sealing element 36 formed by the outer sealing lip 120 and the inner sealing lip 122, which tends to move the sealing lips 120 and 122 in opposite directions away from each other, thus, the sealing lips 120 and 122 with their sealing edges 130 and 132 on the tread 22 and the radial abutment surface 86 of the receptacle 32 in the piston head 20 to keep in abutment.
  • the pressure chamber 40 is pressurized with the medium, this also penetrates into the intermediate space 128 and leads to an increased pressing of the sealing edges 130 and 132 on the first running surface 22 or the contact surface 86.
  • the sliding member 30 now leads not only due to the sealing element 36 with the sealing lips 120 and 122 to a good seal between the piston head 20 and the cylinder housing 12, in particular its first tread 22, against a pressure medium 40 the medium supplied to reliably prevent leakage between the Piston bottom 20 and the cylinder housing 12, but at the same time also improves the tightness against negative pressure conditions in the pressure chamber 40 or engine-side overpressure conditions in that the guide surfaces 102, 104 and 106 due the elastic radial biasing force 108 are held on the tread 22 and thus maintained a sealing effect between the guide surfaces 102, 104 and 106 and the tread 22 even with pressure drop in the pressure chamber 40 and reducing the sealing function of the sealing lips 120 and 122, which also admitted Negative pressure conditions in the pressure chamber 40 holds, so that the guide member 34 itself also still - at least in such approved negative pressure conditions or engine-side overpressure conditions - assumes a sealing function.
  • FIG Fig. 4 In a second embodiment of a sliding element 30 'according to the invention, shown in FIG Fig. 4 , those elements which are identical to those of the first embodiment are provided with the same reference numerals, so that the description of the same may be made in full content to the explanations on the first embodiment.
  • the guide bead 142 extends in the direction of the height H of the sliding member 30 'over a portion of the support body 18, which is more than about one fifth of the extension of the support body 80 in the direction of height H and less than about half of the extension of the support body 80th in the direction of height H.
  • a radially drawn-in region 154 which extends approximately to the foot region 124 of the outer sealing lip 120, then follows.
  • the bead 142 in the second embodiment has an improved support effect by an improved loading of the support body 80 takes place radially inwardly, so that with its radial bearing surface 88 is held on the radial contact surface 86 of the piston head 20 in abutment and thus a tilting movement of the sliding member 30 'and in particular of the support body 80 is largely suppressed by a tilt axis extending perpendicular to the cross-sectional surface.
  • the height H is preferably less than 1.2 times the width B.
  • the width B is moreover preferably more than 0.8 times the height.
  • a preferred embodiment of the sliding member has values of width B to height H between about 0.9 and about 1.1.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)

Claims (34)

  1. Cylindre d'actionnement comprenant un carter de cylindre (12) avec un compartiment intérieur (14) entouré par celui-ci, un piston (16) logé dans le compartiment intérieur (14), lequel est guidé dans une direction de coulissement par au moins une surface de glissement (22) du carter de cylindre (12), et délimite par un fond de piston (20) une chambre de pression (40) dans le carter de cylindre (12), et un élément d'étanchéité (36) maintenu contre le piston (16) et disposé à la périphérie de celui-ci pour rendre étanche la chambre de pression (40) entre le piston (16) et le carter de cylindre (12), ledit élément d'étanchéité faisant partie d'un élément de glissement (30) comprenant un élément de guidage (34), l'élément de guidage (34) étant guidé de manière à pouvoir se déplacer dans la direction de coulissement (18) avec au moins une surface de guidage (102, 104, 106, 152) contre une première surface de glissement (22) du carter de cylindre (12), caractérisé en ce que l'élément de guidage (34) guide le piston (16) de manière flottante par rapport à la première surface de glissement (22), en ce que l'élément de guidage (34) comporte un corps d'appui (80) à partir duquel s'étend l'élément d'étanchéité (36), en ce que l'élément d'étanchéité (36) présente une lèvre d'étanchéité extérieure (120) et une lèvre d'étanchéité intérieure (122) qui se rejoignent en forme de V et s'étendent à partir du corps d'appui (80), en ce que la lèvre d'étanchéité extérieure (120) repose par un bord (130) de lèvre d'étanchéité contre la surface de glissement (22) et en ce que la lèvre d'étanchéité intérieure (122) repose par un bord (132) de lèvre d'étanchéité contre une surface de butée (86) du piston (16).
  2. Cylindre d'actionnement selon la revendication 1, caractérisé en ce que l'élément de guidage (34) guide le piston (16) sensiblement sans contact vers la première surface de glissement (22).
  3. Cylindre d'actionnement selon la revendication 1 ou 2, caractérisé en ce qu'en position centrée du piston (16), un interstice (28) d'au moins 1/10 mm est formé entre une face extérieure (26) du piston (16) opposée à la première surface de glissement (22) et la première surface de glissement (22).
  4. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que l'élément de glissement (30) est disposé au niveau du fond de piston (20).
  5. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que l'élément de glissement (30) est disposé dans un logement (32) au niveau d'une face extérieure (26) du piston (16).
  6. Cylindre d'actionnement selon la revendication 5, caractérisé en ce que l'élément de glissement (30) est maintenu fixe dans le logement (32) par correspondance de forme.
  7. Cylindre d'actionnement selon la revendication 5 ou 6, caractérisé en ce que l'élément de glissement (30) repose par une surface d'appui (88) contre une surface de butée (86) du logement (32).
  8. Cylindre d'actionnement selon la revendication 6 ou 7, caractérisé en ce que l'élément de glissement (30) repose contre une surface de rebord (84) du logement (32) par une surface de pied (82) s'étendant transversalement à la direction de coulissement (18).
  9. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que l'élément d'étanchéité (36) est disposé sur une face de l'élément de guidage (34) opposée à la chambre de pression (40).
  10. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que l'élément d'étanchéité (36) et l'élément de guidage (34) forment une pièce d'un seul tenant.
  11. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que les lèvres d'étanchéité (120, 122) sont disposées sur une face du corps d'appui (80) opposée à la surface de pied (82).
  12. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que la au moins une surface de guidage (102, 104, 106, 152) est disposée sur une face de l'élément d'étanchéité (36) opposée à la chambre de pression (40).
  13. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que la au moins une surface de guidage (102, 104, 106, 152) est disposée au niveau du corps d'appui (80).
  14. Cylindre d'actionnement selon la revendication 12 ou 13, caractérisé en ce que la au moins une surface de guidage (102, 104, 106, 152) est disposée dans une zone élastiquement déformable du corps d'appui (80).
  15. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que la au moins une surface de guidage (102, 104, 106, 152) est disposée contre un boudin de guidage (92, 94, 96, 142) de l'élément de guidage (34).
  16. Cylindre d'actionnement selon la revendication 15, caractérisé en ce que le boudin de guidage (92, 94, 96, 142) est formé sur le corps d'appui (80).
  17. Cylindre d'actionnement selon la revendication 16, caractérisé en ce que le boudin de guidage (142) est contigu à une surface de pied (82) du corps d'appui (80).
  18. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que l'élément de guidage (34) comporte plusieurs surfaces de guidage (102, 104, 106).
  19. Cylindre d'actionnement selon l'une des revendications 12 à 18, caractérisé en ce que chacune des surfaces de guidage est disposée sur un boudin de guidage (92, 94, 96).
  20. Cylindre d'actionnement selon la revendication 18 ou 19, caractérisé en ce que, parmi les plusieurs surfaces de guidage (102, 104, 106), quelques-unes présentent des extensions radiales différenciées.
  21. Cylindre d'actionnement selon la revendication 20, caractérisé en ce que la surface de guidage (102) ayant la plus grande extension radiale est la plus proche de la chambre de pression (40), et en ce que la au moins une autre surface de guidage (104, 106) ayant une extension radiale moindre est disposée sur une face de la première surface de guidage (102) opposée à la chambre de pression (40).
  22. Cylindre d'actionnement selon l'une des revendications 14 à 21, caractérisé en ce que des évidements (112, 114) sont ménagés entre des surfaces de guidage (102, 104, 106) successives dans la direction de coulissement (18).
  23. Cylindre d'actionnement selon la revendication 22, caractérisé en ce que les évidements (112, 114) sont réalisés en forme d'anneaux périphériques.
  24. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce qu'en état de montage de l'élément de glissement (30), la largeur B de celui-ci est supérieure à la moitié de la hauteur H.
  25. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce qu'en état de montage de l'élément de glissement (30), la hauteur H de l'élément de glissement (30) est inférieure à environ 1,3 fois la largeur B.
  26. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que le carter de cylindre (12) présente une deuxième surface de glissement (52) espacée de la première surface de glissement (22) dans la direction de coulissement (18).
  27. Cylindre d'actionnement selon la revendication 26, caractérisé en ce que la deuxième surface de glissement (52) est disposée dans le compartiment intérieur (14) du carter de cylindre (12).
  28. Cylindre d'actionnement selon la revendication 26 ou 27, caractérisé en ce que le piston (16) est guidé contre la deuxième surface de glissement (52) par une tête de guidage (44) s'étendant depuis le fond de piston (20).
  29. Cylindre d'actionnement selon l'une des revendications 26 à 28, caractérisé en ce que la deuxième surface de glissement (52) présente un diamètre égal ou inférieur à celui de la première surface de glissement (22).
  30. Cylindre d'actionnement selon la revendication 28 ou 29, caractérisé en ce que la tête de guidage (44) du piston (10) est guidée directement contre la deuxième surface de glissement (52).
  31. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que le piston (16) est contraint par un accumulateur (64) d'énergie élastique disposé dans le carter de cylindre (12) en direction d'une position de sortie finale avec une chambre de pression (40) maximale.
  32. Cylindre d'actionnement selon l'une des revendications précédentes, caractérisé en ce que le piston (16) est pourvu d'un élément de transmission de pression (68).
  33. Cylindre d'actionnement selon la revendication 32, caractérisé en ce que l'élément de transmission de pression (68) est un composant réalisé avec une forme de sphère et ayant une adhérence ponctuelle avec le piston (16).
  34. Cylindre d'actionnement selon la revendication 32, caractérisé en ce que l'élément de transmission de pression (68) est un composant réalisé avec une forme plate et ayant une adhérence de surface avec le piston (16).
EP06776415.9A 2005-07-26 2006-07-26 Cylindre d'actionnement Active EP1907708B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510036124 DE102005036124A1 (de) 2005-07-26 2005-07-26 Betätigungszylinder
PCT/EP2006/007357 WO2007012471A1 (fr) 2005-07-26 2006-07-26 Cylindre d'actionnement

Publications (2)

Publication Number Publication Date
EP1907708A1 EP1907708A1 (fr) 2008-04-09
EP1907708B1 true EP1907708B1 (fr) 2013-12-04

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EP06776415.9A Active EP1907708B1 (fr) 2005-07-26 2006-07-26 Cylindre d'actionnement

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EP (1) EP1907708B1 (fr)
DE (1) DE102005036124A1 (fr)
ES (1) ES2443893T3 (fr)
WO (1) WO2007012471A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007034978A1 (de) * 2007-07-26 2009-01-29 Wabco Gmbh Pneumatikkomponente
IT1392178B1 (it) * 2008-12-10 2012-02-22 Olab Srl Pompa a vibrazione particolarmente per l'erogazione di fluidi incomprimibili a bassa e media viscosita'.

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB539807A (en) * 1939-04-27 1941-09-24 Siam Improvements in pneumatic remote controlled release devices
DE3411824A1 (de) * 1984-03-30 1985-10-10 FAG Kugelfischer Georg Schäfer KGaA, 8720 Schweinfurt Kolbeneinheit
DE3545882A1 (de) * 1985-12-23 1987-06-25 Bbc Brown Boveri & Cie Kolben-zylinderanordnung insbesondere fuer einen hochspannungs-leistungsschalter
DE3914811A1 (de) * 1988-09-21 1990-03-22 Bosch Gmbh Robert Einkammer-arbeitszylinder
FR2784732B1 (fr) * 1998-10-20 2000-12-01 France Joint Cartouche d'etancheite
DE29916190U1 (de) * 1999-09-15 1999-12-09 Festo AG & Co, 73734 Esslingen Fluidbetätigter Antrieb
US6719298B2 (en) * 2002-01-14 2004-04-13 Skf Usa Inc. Bonded piston seal for power steering
DE20207776U1 (de) * 2002-05-17 2002-09-12 Tünkers Maschinenbau GmbH, 40880 Ratingen Durch Druckmitteldruck, insbesondere pneumatisch, betätigte Kolben-Zylinder-Einheit
FR2855142B1 (fr) * 2003-05-20 2006-05-05 Koyo Steering Europe Kse Ensemble piston pour verin de direction assistee hydraulique

Also Published As

Publication number Publication date
DE102005036124A1 (de) 2007-02-01
ES2443893T3 (es) 2014-02-20
WO2007012471A1 (fr) 2007-02-01
EP1907708A1 (fr) 2008-04-09

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