EP3992469A1 - Cylindre de travail amorti en fin de course - Google Patents

Cylindre de travail amorti en fin de course Download PDF

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Publication number
EP3992469A1
EP3992469A1 EP21000286.1A EP21000286A EP3992469A1 EP 3992469 A1 EP3992469 A1 EP 3992469A1 EP 21000286 A EP21000286 A EP 21000286A EP 3992469 A1 EP3992469 A1 EP 3992469A1
Authority
EP
European Patent Office
Prior art keywords
piston
piston ring
ring
damping
cylinder
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.)
Pending
Application number
EP21000286.1A
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German (de)
English (en)
Inventor
Josef Bueter
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.)
Buemach Engineering International BV
Original Assignee
Buemach Engineering International 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
Application filed by Buemach Engineering International BV filed Critical Buemach Engineering International BV
Publication of EP3992469A1 publication Critical patent/EP3992469A1/fr
Pending 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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke

Definitions

  • the invention relates to a working cylinder with end position damping and a high-precision damping behavior.
  • controlled hydraulic throttles are used in the inlets and outlets. In this way, the outflowing or inflowing volume flow of the working cylinder is throttled.
  • the throttling is controlled, for example, by electronic control systems as a function of the travel of the working cylinder. Disadvantages of this solution are a high design effort, the low robustness and a large hysteresis effect due to the inertia of the hydraulic system.
  • EP 0 949 422 B1 describes a solution as progressive throttling via a variable annular gap of a piston ring, which is arranged on the piston and at one end of the cylinder passes over the laterally arranged fluid connection and enters a conicity, where it encloses the fluid in a pressure chamber formed in this way.
  • the outflow of fluid is increasingly throttled at the end of the piston movement via an annular gap that becomes ever narrower. It is a very tried and tested solution, but technically demanding and requires great precision in setting the piston ring preload in order to define the damping zone.
  • the object of the invention is to show end position damping for a working cylinder, which provides high precision and easy adjustability of the damping characteristics and the damping path, is suitable for different types of cylinders, has a high level of robustness and operational reliability, is particularly low-wear and is simple and inexpensive to produce .
  • the working cylinder with end position damping has a cylinder and a piston unit as basic components, with a piston ring limiter being assigned to the piston unit according to the invention.
  • a generic cylinder has a cylinder tube, a first closure part and a second closure part, the cylinder tube having a first and a second cylinder tube end.
  • the first closure part is arranged at the first end of the cylinder tube and the second closure part is arranged at the second end of the cylinder tube.
  • the cylinder tube and the closure parts form a cylinder interior.
  • the closure parts are connected to the cylinder tube in a fluid-tight manner, for example welded or screwed. However, other joining methods for the connection are also possible.
  • the closure parts also form a axial limitation and define by their distance the working path of the piston unit of the working cylinder.
  • the cylinder has a damping zone in at least one end area.
  • the cylinder has at least one lateral pressure medium connection, which is associated with the damping zone and is spaced axially from an axial boundary of the cylinder interior.
  • the damping zone is defined by the distance between the pressure medium connection and the end stop in the closure part. Damping is understood to mean a force effect that develops over the displacement path of the piston unit in the damping zone and counteracts the movement and delays it.
  • the piston unit slides through the first closure part and forms at least one working space in the cylinder interior.
  • there may only be one working space in particular in the case of a plunger cylinder, but also, for example, two working spaces, in particular in the case of a differential cylinder or synchronous cylinder.
  • the piston unit is sealingly guided in a bore in the first closure part.
  • the piston unit can be designed, for example, as a plunger piston, as in a plunger cylinder, or as a unit made up of a piston and piston rod, as in a differential cylinder or double-rod cylinder.
  • the piston unit has a piston body which is guided in an axially displaceable manner by means of a guide in the cylinder interior.
  • the piston body can be, for example, the piston in a piston-piston rod assembly, a plunger piston or the piston rod.
  • the piston body has a circumferential inner annular groove on a radial outer lateral surface.
  • the piston unit also has a piston ring. This is located in the inner ring groove. It is resilient and has an annular gap.
  • the inner ring groove is sufficiently deep, so that the piston ring a reduction in circumference with a reduction in the annular gap opening can dip into the inner ring groove.
  • the piston unit is designed to overrun the pressure medium connection during an inward movement in the direction of the end position and to enclose a damping pressure medium volume in a damping zone space in the damping zone.
  • the piston unit During the retraction movement within the damping zone, the piston unit has a first operating state. During an extension movement within the damping zone, the piston unit has a second operating state. A third operating state occurs when there is a movement in the area outside the damping zone.
  • the piston ring In the first and the second operating state, the piston ring rests with its outer lateral surface against the inner wall of the cylinder and blocks a flow of pressure medium between the outer lateral surface and the inner wall of the cylinder. All wall sections of the cylinder that are opposite the outer lateral surface of the piston ring are understood to be the cylinder inner wall. This can involve both sections of the cylinder tube and the closure parts.
  • the annular gap is also designed for an inflow of a pressure medium into the damping zone space.
  • the inflow occurs when pressure is applied to the pressure medium via the annular gap or preferably via the release of a bypass.
  • the pressure medium can flow into the damping chamber much more quickly via an optional bypass than via the annular gap, thus avoiding damping of the extension movement, which is usually not desired.
  • the working cylinder with end position damping according to the invention is characterized in particular in that the piston unit has a piston ring limiter.
  • This is designed to limit a spring deflection of the piston ring in a relaxation direction and to set the piston ring in a prestressed position.
  • the piston ring is resilient. It is thus designed to assume a working position in the first operating state and in the second operating state and to bear resiliently against the cylinder inner wall in the damping zone. In the working position, the piston ring is under tension and is compressed against its spring direction by the inner wall of the cylinder.
  • the piston ring is also designed to assume a prestressed position in the third operating state.
  • a prestressed position in the context of the present invention is understood to mean that the expansion of the piston ring is not limited by the inner wall of the cylinder but by another means, with the spring tension of the piston ring being less in the prestressed position than in the working position.
  • the piston ring is set to an exactly definable outer diameter by the preload position, undefined starting areas of the attenuation bypassed. Rather, the axial starting position of the damping is precisely defined by the limited expansion diameter of the piston ring in conjunction with the axial progression of the inner diameter of the cylinder.
  • the piston ring When the axial position is reached, in which the outer diameter of the piston ring in its prestressed position corresponds to the cylinder inner diameter in the area of the conicity, the piston ring does not start with a spring force of zero, as in the prior art, but with a definable spring force and ensures so already from this axial point on a spring-loaded tight fit to the inner wall of the cylinder.
  • the spring force can be determined by the spring constant and the position of the prestressing layer in relation to the spring deflection of the piston ring.
  • the damping zone can advantageously be made structurally shorter.
  • the piston ring limiter is designed as a radial piston ring limiter.
  • a radial piston ring limiter is understood to mean that the widening is limited by a radial definition of the preload position. This means that the maximum radial distance between the outer surface area of the piston ring and the main longitudinal axis of the piston is specified.
  • the piston ring has a base flange and a piston ring limiter.
  • the base flange provides a radial annular surface set back from an outer lateral surface.
  • the piston ring has a stepped outer contour, with the radial ring surface of the base flange section having a smaller outer diameter than the outer ring surface of the main section.
  • the radial piston ring limiter is designed as a hold-down ring. For this purpose, it has a radial overlapping surface.
  • the radial overlapping surface limits a radial expansion of the piston ring by means of a radial form fit with the radial ring surface of the piston.
  • the piston ring limiter is designed as a circumferential limiter.
  • This circumference limiter can be designed as an additional shaped element on the piston rod or as an additional component.
  • the molding or component may be formed of a continuous or split shape. The circumferential limiter absorbs the tangential tensile forces in the area of the annular gap due to the spring action and thus limits the expansion of the annular gap.
  • the piston ring which is limited in expansion in this way, has the advantage of compensating for play when entering the damping zone. Any manufacturing tolerances in the synchronism between the piston unit and the cylinder tube can be compensated for in this way. Furthermore, there is a defined starting point for the damping due to the piston ring diameter, which always remains the same in the preload position and is limited in circumference. The start-up zone of the damping is clearly defined in its characteristic by the specified piston ring gap
  • the piston ring has a tension connection on the piston ring gap, which is designed to limit an opening width of the piston ring gap.
  • the tangential expansion of the piston ring is limited to a certain amount with a tension element.
  • the tension element can be designed in the form of a tie rod, but also in another form.
  • the circumference limiter is formed by two shaped pins which engage in two axial elongated holes in the piston ring on both sides of the piston ring gap.
  • the piston ring limiter is designed as a tangentially acting expansion limiter.
  • the expansion limiter is formed as an arrangement of two mold pins.
  • the piston ring has two elongated holes in the axial direction on both sides of the piston ring gap.
  • the piston body has two axial bores and is designed to accommodate the form pins in the two bores Have bores of the piston body and the slots of the piston ring overlapping positions.
  • This design of the deflection limiter is also referred to below as a pin lock.
  • the pin lock has the advantage that a tangentially acting widening limitation determines a maximum opening width of the annular gap particularly precisely and at the same time a radial and rotational positional relationship between the piston ring and the piston can also be defined.
  • the piston ring has a tensile connection at the piston ring gap. This is designed to limit the opening width of the piston ring gap.
  • the piston body has a piston base body. This is guided in an axially displaceable manner by means of a guide in the cylinder interior.
  • the piston base body has at least one annular body. This has a circumferential inner ring groove on a radial outer lateral surface, the piston ring being arranged in the inner ring groove and the piston ring resting resiliently against the inner wall of the cylinder.
  • the piston ring has a piston ring gap.
  • the ring body accommodates a guide pin of the piston base body in a ring opening, with an annular gap being formed between a radial inner lateral surface of the ring body and the guide pin.
  • the annular body has an axial and a radial play of movement relative to the piston body.
  • the annular body has an axial annular surface on the piston base body side. Matching this, the piston base body has an opposite axial mating ring surface on the ring body side.
  • the piston body is designed such that, in the first operating state, the axial annular surface on the piston base body side and the axial mating annular surface on the annular body side rest against one another and form a sealing plane.
  • the axial ring surface on the piston base body side and the axial mating ring surface on the ring body side have an axial gap relative to one another.
  • the axial gap and the annular gap form a pressure medium inflow channel.
  • the pressure medium channel is designed for an inflow of pressure medium into the damping zone space.
  • the piston ring gap can thus be overflown via a bypass. As a result, an undamped extension movement of the piston unit out of the damping zone is possible. This ensures a quick extension movement of the cylinder at the beginning of the movement.
  • the cylinder has a further damping zone in a further end region axially opposite the end region.
  • the further damping zone is designed in the same way as the damping zone, so that all of the description content for the damping zone, in particular for the axially spaced lateral pressure medium connection, for the piston ring with piston ring limiter and for the operating states also apply to the further damping zone in a corresponding manner.
  • the working cylinder is designed as a working cylinder that is damped in both end positions.
  • the figure 1 shows an embodiment of the working cylinder 1, which is designed here as a double-sided damped differential cylinder, as a sectional view. Shown is the cylinder tube 3 with the two closure parts 6, 7, the first closure part 6 being the base closure part and the second closure part 7 being the guide closure part. Piston unit 2 is guided in it.
  • the working space 10 is located within the cylinder interior 8, the working space 10 being present here as a piston bottom space 10.1 and as a piston rod space 10.2.
  • the damping zone 9 is introduced in the closure parts 6, 7 at the cylinder tube ends 4, 5, the damping zone 9 is introduced.
  • the parts required for end position cushioning are placed in cushioning zone 9.
  • a piston ring limiter 14 is mounted to position the piston ring 11 and to limit it radially from springing out.
  • the pressure medium for the working movement of the piston unit 2 is supplied via the pressure medium connection 16 for the extension movement and via the further pressure medium connection 16.1 for the retraction movement. Due to the serial activation of the pressure medium connections 16, 16.1, the piston unit 2 moves linearly alternating in the axial direction in the cylinder tube 3.
  • the piston unit 2 has a piston rod which passes through the second closure part 7, here as a guide closure part. Furthermore, the piston unit 2 has a guide piston which guides the piston unit 2 radially in the cylinder tube 3 . The seal of the guide piston separates the two working spaces 10.1, 10.2, ie the piston head space 10.1 and the piston rod space 10.2, from one another.
  • the piston unit 2 has an annular body 25 that can be displaced axially with respect to the piston rod.
  • the piston rod forms the basic piston body.
  • the inner ring groove 13 which accommodates the piston ring 14 , is arranged in the ring body 25 .
  • the ring body is arranged on the piston.
  • the piston forms the main body of the piston.
  • the figure 2 1 shows the damping zone 9 of the cylinder 1 in a detailed sectional view.
  • the piston ring 14 is received by the ring body 25 .
  • the ring body 25 is coupled to the piston rod with a slight axial and radial play.
  • the piston ring 14 rests in the end position with its outer lateral surface resiliently against the inner wall in the damping zone 9 and is thus in the working position in the first and second operating state.
  • the ring body 25 also accommodates the piston ring limiter 17, which in this embodiment is designed as a radial piston ring limiter. If the piston ring 14 in the third operating state outside of the Damping zone is, it is limited by the piston ring limiter 17 in its radial deflection and at the same time radially positioned and centered. At the same time, in the present exemplary embodiment, the piston ring 14 is also fixed on one side in its axial position by the piston ring limiter 17 .
  • the annular body 25 is guided on a guide pin 28 with axial and radial movement.
  • the guide pin 28 is a section of the piston rod of the piston unit 2.
  • the axial annular surface 27 of the annular body 25 on the piston base body side and the mating annular surface 22 of the piston base body, here the piston rod, are opposite and form the sealing plane 21.
  • the annular body 25 is pressed axially against the mating ring surface 22 by the overpressure in the damping pressure medium volume compared to the pressure medium connection 16, so that the sealing plane seals and the pressure medium can only pass via the piston ring gap.
  • the pressure conditions are reversed and an axial annular gap opens between the axial annular surface 27 and the mating annular surface 22.
  • the pressure medium can also flow as a bypass into the damping chamber via the overflow channel (no reference number), see above that an undesired extension damping is avoided.
  • the figure 3 shows the piston ring 14 and the piston ring limiter 17 in a schematic oblique representation.
  • the piston ring limiter 17 is designed as a radial piston ring limiter.
  • a base flange 14a is formed on the piston ring 14 .
  • This has a radial annular surface 18 towards the outside in the radial direction.
  • the piston ring limiter 17 has a radial overlap ring surface 19 .
  • the radial annular surface 18 of the piston ring 14 rests against this in the spring-open state. The spring deflection of the piston ring 14 is thus limited.
  • the sealing plane 21 seals the pressure medium from the damping zone space to the rest of the piston head space 10.1 onwards. As a result, a defined overflow of the pressure medium is only ensured through the piston ring gap 15 .
  • the figure 4 shows a further variant of the expansion limitation of the piston ring 14 in the form of a pin lock in detail in a schematic sectional view.
  • the piston limiter 17 is designed as a circumferential limiter.
  • the piston ring 14 is prevented from springing open radially by two axially arranged shaped pins 23 .
  • the two shaped pins 23 are positioned in the annular body 25 in two axial bores 24 in an annular shoulder. The axial movement of the piston ring 14 is blocked by the inner ring groove 13 .
  • Another locking ring secures the shaped pins 23 axially with a positive fit.
  • the figure 5 shows in a detailed oblique view the geometric design of the piston ring 14 in the embodiment as a pin lock. It's about the in figure 4 illustrated embodiment.
  • the shaped pins 23 engage in two oblong holes placed opposite one another on the circumference of the piston ring 14 at the piston ring gap 15 and thus define the maximum spring-opening travel of the piston ring 14 in the circumferential direction. In this way, the piston ring gap 15 is defined in its maximum opening gap and the maximum overflowing volume flow of the pressure medium is determined.
  • a further embodiment variant of the piston ring 14 is shown as a schematic oblique view as a detailed view.
  • the circumference and thus at the same time the radial spring-opening travel of the piston ring 14 is limited by the tension connector 20 in this variant.
  • the pull connector 20 has a limiting effect on the circumferential expansion of the piston ring 14.
  • two slots are provided on the circumference in the axial direction.
  • the elongated holes are open with an opening in the circumferential direction.
  • the tension connection 20 is inserted in the form of a tie rod after assembly. So the annular gap is 15 in limited to its maximum opening width.
  • the piston ring gap 15 thus has a defined gap that enables a determinable volume flow of the pressure medium for the damping.
  • figure 7 shows schematically the effect of the piston ring limiter 17 on the force-spring travel relationship.
  • the spring deflection s is plotted on the abscissa axis, with a relaxation position present without the piston ring limiter 17 lying at the origin of the coordinates.
  • the piston ring 14 is maximally deflected and the piston ring gap 15 is largest.
  • S max the piston ring gap 15 is closed and the piston ring 14 is maximally tensioned.
  • the force F is entered on the ordinate axis.
  • the spring deflection s of the piston ring 14 is limited in the direction of the relaxation position by the piston ring limiter 17 at the point s v .
  • the bias condition is in the third regime.
  • the piston ring 14 rests against the piston ring limiter with the force F v . If the piston ring 14 comes into sliding contact with the inner wall of the cylinder during an entry movement into the damping zone and continues to deform on the spring deflection from point s v in the direction of s max , in contrast to the prior art, this is already in contact with the piston ring limiter 17 from the beginning of the damping predefined force F v on the inner wall of the cylinder.
  • the piston ring 14 is compressed more and more in the spring deflection range between points s v and s max , so that the force F continues to increase from point F v to point F max .
  • the area between the point s v and s max or between the point F v and F max corresponds to the first operating state with a course in the direction s max or F max and the second operating state with a course in the opposite direction.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
EP21000286.1A 2020-10-28 2021-10-12 Cylindre de travail amorti en fin de course Pending EP3992469A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202020004533.0U DE202020004533U1 (de) 2020-10-28 2020-10-28 Endlagengedämpfter Arbeitszylinder

Publications (1)

Publication Number Publication Date
EP3992469A1 true EP3992469A1 (fr) 2022-05-04

Family

ID=78211780

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21000286.1A Pending EP3992469A1 (fr) 2020-10-28 2021-10-12 Cylindre de travail amorti en fin de course

Country Status (2)

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EP (1) EP3992469A1 (fr)
DE (1) DE202020004533U1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4048905A (en) * 1976-03-29 1977-09-20 The Boeing Company Variable orifice hydraulic snubber
JPH0198967U (fr) * 1987-12-23 1989-07-03
JPH01115059U (fr) * 1988-01-29 1989-08-02
EP0949422B1 (fr) 1998-03-04 2001-09-19 Bümach Engineering International B.V. Dispositif amortisseur de fin de course
EP0779435B1 (fr) 1995-12-16 2001-11-14 Bümach Engineering International B.V. Verin hydraulique
JP2005016631A (ja) * 2003-06-26 2005-01-20 Shin Caterpillar Mitsubishi Ltd 流体圧シリンダ

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB515230A (en) 1938-05-28 1939-11-29 William Arthur Oubridge Improvements in piston and like packing rings
DE4307265C1 (de) 1993-03-02 1994-08-11 Mannesmann Ag Vorrichtung zur Endlagendämpfung eines Kolbens in Druckflüssigkeitszylindern
DE19647472A1 (de) 1996-11-16 1998-05-20 Zahnradfabrik Friedrichshafen Pneumatischer oder hydraulischer Stellmotor mit einer Abschalteinrichtung
DE10142562A1 (de) 2001-08-30 2003-03-27 Hydac Technology Gmbh Hydrozylinder
GB0716406D0 (en) 2007-08-23 2007-10-03 Cross Mfg Co 1938 Ltd Sealing rings

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4048905A (en) * 1976-03-29 1977-09-20 The Boeing Company Variable orifice hydraulic snubber
JPH0198967U (fr) * 1987-12-23 1989-07-03
JPH01115059U (fr) * 1988-01-29 1989-08-02
EP0779435B1 (fr) 1995-12-16 2001-11-14 Bümach Engineering International B.V. Verin hydraulique
EP0949422B1 (fr) 1998-03-04 2001-09-19 Bümach Engineering International B.V. Dispositif amortisseur de fin de course
JP2005016631A (ja) * 2003-06-26 2005-01-20 Shin Caterpillar Mitsubishi Ltd 流体圧シリンダ

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Publication number Publication date
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