EP4081714A1 - Working cylinder with cushioned end-stroke - Google Patents
Working cylinder with cushioned end-strokeInfo
- Publication number
- EP4081714A1 EP4081714A1 EP20848691.0A EP20848691A EP4081714A1 EP 4081714 A1 EP4081714 A1 EP 4081714A1 EP 20848691 A EP20848691 A EP 20848691A EP 4081714 A1 EP4081714 A1 EP 4081714A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- ring
- piston
- axial
- cylinder
- pressure medium
- 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.)
- Granted
Links
- 238000013016 damping Methods 0.000 claims abstract description 147
- 238000007142 ring opening reaction Methods 0.000 claims abstract description 8
- 230000013011 mating Effects 0.000 claims description 11
- 238000007789 sealing Methods 0.000 claims description 5
- 238000011161 development Methods 0.000 description 11
- 230000018109 developmental process Effects 0.000 description 11
- 230000000694 effects Effects 0.000 description 10
- 238000007667 floating Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 230000003111 delayed effect Effects 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000000750 progressive effect Effects 0.000 description 2
- 235000014676 Phragmites communis Nutrition 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000037237 body shape Effects 0.000 description 1
- 238000012790 confirmation Methods 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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
- F15B15/224—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston which closes off fluid outlets in the cylinder bore by its own movement
-
- 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 end position damped working cylinder.
- the object of the invention is to show a damping for an end position damped working cylinder, which provides high precision and easy adjustment of the damping, is also suitable for high bending loads on the piston unit and for different cylinder types, has a high level of robustness and operational safety and is also simple and inexpensive can be produced.
- the end position damped working cylinder has a cylinder and a piston unit.
- the cylinder has a cylinder tube, a first and a second closure part.
- the first closure part is arranged on the first cylinder tube end and the second closure part is arranged on the second cylinder tube end of the cylinder tube.
- the arrangement of the two closure parts is designed in such a way that they are connected to the respective cylinder tube ends in a pressure-tight manner.
- the two closure parts are preferably each welded to the cylinder tube along the circumferential common contact surface. Other connections, such as screwing, are also possible.
- the cylinder tube and the closure parts form a cylinder interior.
- the cylinder interior is to be understood as the interior of the cylinder, which is formed by the closure parts and the cylinder tube and in which the pressure medium is located when used as intended. Furthermore, the piston is arranged in the cylinder interior.
- the cylinder has a damping zone in at least one end area.
- the damping zone is the area of the cylinder interior in which damping takes place when the piston unit enters. Damping is understood to be a force effect that delays the movement of the piston unit.
- the damping zone is located at at least one end region of the cylinder tube and comprises the part of the cylinder interior between a pressure medium connection and an axial delimitation by the closure part arranged at this end region.
- the cylinder has a laterally arranged pressure medium connection, the pressure medium connection being assigned to the damping zone and axially spaced from the axial delimitation of the cylinder interior.
- the damping zone extends between the pressure medium connection and the axial limitation.
- the axial limitation physically blocks further movement of the piston unit and thus defines the maximum movement path of the piston unit axially on one side.
- the axial limitation is preferably formed by the closure part.
- the closure part has a corresponding stop surface against which the piston unit can rest so that it assumes its end position.
- the end position of the piston unit during operation can also be before the axial limit is reached.
- the piston unit has a piston base body and an annular body.
- the piston unit is preferably composed of a piston rod and a piston, the piston then having the piston base body and the ring body.
- the piston base body and the ring body are also referred to collectively as the piston below.
- the piston base body can be designed differently.
- the piston rod can thus be guided completely through or only partially into the piston base body.
- the piston unit can be designed monolithically and then have only one piston rod and one piston section. According to the invention, the piston unit slidably penetrates the first closure part and forms at least one working space in the cylinder interior.
- the first closure part is designed to receive the piston unit in a sliding manner and has sealing and guide elements for this purpose.
- the piston base body is guided in an axially displaceable manner by means of a guide in the cylinder interior.
- the piston base body has at least one receptacle for a guide.
- the receptacle is preferably designed as a groove into which a guide ring is inserted as a guide.
- the ring body has a circumferential inner ring groove on a radial outer jacket surface.
- a piston ring is arranged in this inner ring groove.
- the circumferential inner ring groove is designed to accommodate the piston ring and to fix it in its axial position. Furthermore, the circumferential inner ring groove is designed to allow a radial movement of the piston ring at least to the extent that it can be resiliently deformed. This is achieved by a sufficient depth of the circumferential inner ring groove.
- the piston ring rests resiliently on the inner wall of the cylinder and has a piston ring gap.
- the piston ring is designed to be resilient, in particular radially elastic, and in a relaxed state has an outer diameter which is greater than the inner diameter of the cylinder tube.
- the piston ring assumes a state of tension in the circumferential inner ring groove and lies against the inner wall of the cylinder. In this state of tension, the piston ring deforms elastically and reduces its outer diameter and the size of the piston ring gap.
- the ring body receives a guide pin of the piston base body in a ring opening and forms an annular gap between a radial inner circumferential surface of the ring body and the guide pin.
- the ring opening is a preferably hollow cylindrical recess. However, it can also have a different geometry if it is designed to be guided by the guide pin.
- the ring body is designed so that it can be arranged with its ring opening on the guide pin of the piston base body.
- the guide pin is part of the piston body.
- the guide pin is preferably a tapered section of the piston base body. However, it can also be a connected component.
- the guide pin is arranged at the end of the piston unit which faces the end position to be damped.
- the guide pin is preferably cylindrical. The outside diameter of the guide pin is then smaller than the inside diameter of the ring opening.
- the guide pin can, however, also have any other geometry that is suitable for guiding the ring body.
- the solution according to the invention is in particular characterized in that the ring body has an axial movement play and a radial movement play with respect to the piston base body. Due to the radial play, the ring body is also referred to below as a floating ring body.
- the ring body is limited in its position on the guide pin in its axial mobility by means of a locking body.
- the locking body is preferably designed as a Seeger ring, which is inserted into an annular groove correspondingly arranged on the guide pin.
- Other locking body shapes are also possible, which can be arranged on the piston base body and axially limit the freedom of movement of the ring body.
- the ring body has an axial ring surface on the piston base body side, and the piston base body has an axial counter-ring surface on the opposite side.
- the piston unit is designed to move axially over the pressure medium connection with the piston ring when moving into the damping zone and to enclose a damping pressure medium volume in a damping zone space in the damping zone.
- the damping zone space refers to the part of the cylinder interior that is delimited by the piston unit, the closure part and the cylinder tube after the pressure medium connection has been passed over by the piston ring. As the axial movement of the piston unit progresses in the direction of the axial end position, the damping zone space is reduced.
- the part of the pressure medium that is enclosed in the damping zone space and flows out of it is referred to as the damping pressure medium volume.
- the piston unit is designed to have a first operating state in the event of a retraction movement within the damping zone and a second operating state in the event of an extension movement within the damping zone.
- the first operating state is also referred to below as the damping operating state.
- the second operating state is also referred to below as the exit operating state.
- the axial ring surface on the piston base body side and the axial mating ring surface on the ring body side are in contact with one another and form a sealing plane.
- the volume of the damping pressure medium is enclosed by the piston unit, which also increases the pressure in the damping zone space compared to the pressure at the pressure medium connection.
- the piston ring gap is designed according to the invention for a throttled outflow of the damping pressure medium volume.
- the pressure of the enclosed pressure medium i.e. of the damping pressure medium volume
- the operating pressure is understood to be the pressure of the pressure medium which is present at the pressure medium connection and which corresponds to the pressure in the rest of the working space.
- the pressure medium can only flow out through the piston ring gap.
- a force is generated which counteracts the retraction movement of the piston unit.
- an axial gap is formed between the axial ring surface on the piston base body side and the axial mating ring surface on the ring body side.
- This axial gap between the axial ring surface on the piston base body side and the axial mating ring surface on the ring body side is also referred to below for short as the axial gap.
- the ring body moves away from the axial mating ring surface of the piston base body on the ring body side and an axial gap is formed between the piston base body and the ring body.
- the axial gap and the annular gap form a pressure medium inflow channel.
- the pressure medium inflow channel is designed for an inflow of the pressure medium into the damping zone space.
- the axial gap between the axial ring surface of the ring body on the piston base and the axial mating ring surface on the ring body side of the piston base as well as the radial ring gap between the radial inner surface of the ring and the guide pin form a pressure medium channel with a cross-section that can be designed in a structurally configurable manner, which, regardless of the cross-section of the piston ring gap, provides an inflow of pressure medium in the damping zone space.
- the piston unit is moved out of its end position and the damping zone without undesired damping.
- the piston unit thus executes the extension movement.
- the extension movement can be initiated practically without delay by means of the ring body and its axial movement play.
- This is based on the fact that when pressure is applied to the pressure medium connection, the ring body is actively moved axially away from the piston base body. The force causing this results from the surface area of the ring surface on the piston base body side and the pressure difference between the pressure at the pressure medium connection and the pressure of the damping pressure medium in the damping zone space.
- the ring body is designed as a volume body and thus designed to displace a partial volume of the damping pressure medium in the damping zone space, whereby the pressure medium presses on the piston body and the piston unit is immediately displaced from the end position.
- the ring body is decoupled from the exact radial position of the piston base body due to its floating mounting.
- the ring body By means of the radially elastic piston ring, the ring body always exactly follows the inner wall of the cylinder in its radial position in the sense of self-adjustment. This also applies in particular when the piston base body is adversely affected in its radial position, in particular as a result of deformations of the piston rod in the event of buckling loads.
- the ring body does not have to transmit any radial forces to the inner wall of the cylinder.
- a particularly small gap dimension can also advantageously be provided between the outer circumferential surface of the ring body and the inner wall of the cylinder, without the risk of grinding on the inner wall of the cylinder, as would not be possible according to the prior art.
- the floating ring body can advantageously be provided with axial play at the same time, with a particularly low structural effort, and two different operating states can be provided with a damping operating state and an exit operating state, which on the one hand have a precise damping effect during a retraction movement and on the other hand, bypassing the damping enable an active extension movement.
- the cross section of the annular gap is also advantageously independent of the relative radial positional relationship of the ring body and guide pin within the radial movement always constant and can easily be determined by the difference between the inner diameter of the ring body and the outer diameter of the guide pin.
- damping characteristics and the extension characteristics can be adapted to the respective requirements with simple constructive means such as the choice of the axial distance of the pressure medium connection, the shape of the cylinder inner wall in the damping zone, the width of the piston ring gap or the width of the radial gap and the ring gap . This can also - if provided - take place separately for each end position.
- the end position damping can be provided both in only one end position and in both end positions.
- the solution can be used in different cylinder types, such as in particular differential working cylinders, synchronous cylinders, pull cylinders or plunger cylinders.
- the elastic piston ring which is tensioned against the inner wall of the cylinder, can also advantageously compensate for manufacturing-related deviations in the cylinder tube and thus enable high damping precision.
- the constant distance between the ring body and the inner wall of the cylinder has the advantage that magnetic position sensors can be used very reliably and provide precise axial position data for the piston unit.
- the axial play of the ring body is limited axially against the piston center by a locking ring.
- the locking ring is inserted into a groove in the guide pin, the locking ring not being completely received by the groove.
- the securing ring can in particular be a circlip that is inexpensive and available as a standard component.
- the axial play of movement of the ring body is limited in one direction by the axial counter-ring surface of the piston base body and in the other direction by the locking ring.
- the advantage is that by means of a structurally very simple and at the same time reliable means by means of the axial distance between the locking ring and the ring body, the axial movement play of the ring body and thus the possible width of the axial gap between the axial ring surface on the piston base body side and the axial mating ring surface on the ring body side as a section of the pressure medium inflow channel can be determined.
- the guide pin has an axial groove.
- the axial groove is designed as part of the pressure medium inflow channel.
- the axial groove is at least one groove which runs axially along the guide pin.
- the axial groove can also be formed by several grooves.
- the cross section of the annular gap can be expanded with a simple means and thus advantageously used in connection with the axial gap for the targeted adjustment of the pressure medium inflow in the second operating state. In this way, the achievable speed of the extension movement in the damping zone can be determined.
- the cross section of the pressure medium inflow channel can advantageously be expanded independently of the radial movement play of the ring body.
- the cylinder has a position encoder.
- the position transmitter is designed to record a position of the ring body.
- the position transmitter detects the position of the piston unit by means of a measuring method that registers and evaluates a capacitive, magnetic, mechanical or electromagnetic change in properties during the piston movement.
- a measuring method that registers and evaluates a capacitive, magnetic, mechanical or electromagnetic change in properties during the piston movement.
- different position sensors for determining the piston position are known from the prior art. For example, in the case of a magnetic design, detection can take place using a reed switch.
- the cylinder inner wall has a conicity in the damping zone and in the first operating state the piston ring is designed to narrow the piston ring gap as the retraction movement progresses.
- the piston ring is tightened more and more during the retraction movement, since its outer diameter has to adapt to the increasingly smaller inner diameter of the cylinder inner wall.
- the piston ring gap is thus also progressively reduced and the cross section for the outflow of the damping pressure medium volume is reduced.
- the damping effect of the damping zone increases up to a maximum.
- the strength of the conicity determines the increase in the damping effect depending on the travel distance covered.
- the inner wall of the cylinder can, however, also initially have a conical section and then a cylindrical section in the damping zone along the retraction movement.
- the damping effect is increased to a maximum in the conical area, while in the subsequent cylindrical section of the damping zone the maximum damping effect achieved continues to have an effect until the end position is reached.
- the course of the damping effect can also be adapted to specific requirements.
- the cylinder has a further damping zone in a further end region axially opposite the end region.
- the cylinder has a further laterally arranged pressure medium connection, the further pressure medium connection being assigned to the further damping zone and axially spaced from a further axial delimitation of the cylinder interior opposite the axial delimitation.
- the further pressure medium connection, the further damping zone and the further axial limitation basically correspond in function and design to the pressure medium connection, the damping zone and the axial limitation.
- the further damping zone and the further pressure medium connection are arranged in spatial proximity to the second closure part on the second end of the cylinder tube.
- the piston unit has a further ring body axially opposite the ring body and the piston base body has a further guide pin axially opposite the guide pin.
- the further ring body is designed analogously to the ring body and is arranged on the opposite side of the piston unit.
- the further guide pin also has at least one further locking body, which limits the axial freedom of movement of the further ring body.
- This further locking body is also preferably designed as a further locking ring which is inserted into a further groove in the further guide pin.
- the further ring body and the further guide pin can differ in their dimensions from the ring body and the guide pin in spite of the basically identical structure. For example, different damping characteristics can be implemented at the two end positions of the piston unit become. This is particularly useful in the case of a working cylinder that is heavily loaded asymmetrically.
- the piston unit is designed to have a third operating state in the event of a retraction movement within the further damping zone and a fourth operating state in the event of an extension movement within the further damping zone.
- the third operating state is also referred to below as the further damping operating state.
- the fourth operating state is also referred to below as the further extended operating state.
- the third operating state is also referred to as the further damping operating state and has the features of the first operating state in a corresponding manner in relation to the further damping zone.
- the fourth operating state is also referred to as the further extended operating state and has the features of the second operating state in a corresponding manner in relation to the further damping zone.
- damping characteristics in each of the two end position damping can be set independently of that of the other end position damping.
- the invention is illustrated as an exemplary embodiment on the basis of Fig. 1 End position damped working cylinder as differential cylinder with end position damping on one side (sectional view)
- Fig. 7 piston unit (isometric view) explained in more detail.
- Fig. 1 shows an overview of a first embodiment of the end position damped differential working cylinder.
- the end position damping is arranged at the end position assigned to the second closure part 5. It is an end position cushioning on the piston crown, which cushions the retraction movement.
- the end position damped working cylinder has a cylinder 1 and a piston unit 2.
- the cylinder 1 is composed of the cylinder tube 3, the first closure part 4 and the second closure part 5.
- the cylinder tube 3 and the two closure parts 4, 5 are connected to one another in such a way that they enclose a cylinder interior 8.
- the first closure part 4 is assigned to the first cylinder tube end 6 and the second closure part 5 is assigned to the second cylinder tube end 7.
- the inside of the second closure part 5 forms an axial delimitation 11 and the inside of the first closure part 5 forms a further axial delimitation 27, which delimits the axial movement space of the piston unit 2 arranged in the cylinder interior 8.
- the axial delimitations 11, 27 are designed as stop surfaces for the piston unit 2, which moves axially during operation.
- the pressure medium connection 10 is arranged at the second cylinder tube end 7 and the further pressure medium connection 26 is arranged at the first cylinder tube end 6.
- the piston unit 2 has a piston base body 12 and an annular body 13.
- the piston unit 2 is composed of a piston rod and a piston, which are firmly connected to one another.
- the piston base body and the ring body together form the piston.
- the piston rod of the piston unit 2 is guided through the first closure part 4 and slidably mounted therein.
- the ring body 13 is pushed onto the guide pin 18, which is designed as a taper on the piston base body 12.
- the piston base body 12 is guided in the cylinder tube 3 by means of a guide 14.
- FIG. 2 shows an enlargement of FIG. 1 in the area of the second closure part 5. Furthermore, the piston base body 12 is in an end position, as a result of which the piston base body 12 rests with its guide pin 18 on the axial delimitation 11.
- the arrangement and the design of the ring body 13 is shown in more detail.
- the ring body 13 is designed as a metal ring which, on its outer circumferential surface 13c, has an inner ring groove 15 in which the piston ring 16 is inserted.
- the inner ring groove 15 is formed in such a way that the piston ring 16 has greater freedom of movement in the radial direction, so that it can be elastically deformed radially.
- the elastic piston ring has a piston ring gap 16a (see in particular FIG. 7 in this regard) and is clamped against the cylinder inner wall 17.
- the ring body 13 is pushed onto the guide pin 18 and rests with an axial ring surface 13d on the piston base body side on the counter ring surface 12a of the piston base 12 on the ring body side. Axially opposite the axial freedom of movement of the annular body 13 is limited by a locking ring 22 be.
- the ring opening 13a of the ring body is designed in such a way that it exceeds the diameter of the guide pin 18, so that the ring body has a radial freedom of movement with respect to the guide pin 18.
- the damping zone 9 represents an axial section and extends from the pressure medium connection 10 to the end position of the piston ring 16 in front of the second closure part 5.
- damping zone 9 when the piston unit 2 moves in, there is a damping effect which is opposite to the moving in movement of the piston unit 2 and this decelerates. This is further described in detail in FIG.
- a second embodiment is shown. It is a differential working cylinder with damping in both end positions.
- Another ring body 28 is also present.
- the further ring body 28 is structurally identical to the ring body 13 and is pushed onto a further guide pin 29 and fixed there by a further locking ring 30.
- Both ring bodies 13, 28 and both guide pins 18, 29 are axially opposite one another on the piston base body 12.
- a damping effect is also brought about in the further damping zone 25 by the further ring body in a manner corresponding to that in the damping zone 9.
- the further damping zone 25 extends between the further pressure medium connection 26 and the end position of the further piston ring 31 in front of the further axial delimitation 27 on the first closure part 4.
- a synchronous working cylinder is shown, which is also end-position damped on both sides.
- the difference to the differential working piston from FIG. 3 is that the piston rod section of the piston base body 12 is guided through both closure parts 4, 5 and is mounted in a sliding manner.
- the second closure part 5 is therefore also designed as a guide closure part in this exemplary embodiment.
- the piston base body 12 is designed similarly to that from FIG. 3, but it differs in that the piston rod extends through it. Both sections of the piston unit 2 are firmly connected to one another here as well.
- the first operating state which is the damping operating state
- the second operating state which is the exit operating state
- the piston unit is in the retraction movement and the piston ring 16 in the inner ring groove 15 of the ring body 13 has just passed the pressure medium connection 10 and encloses a damping pressure medium volume in the damping zone space 20.
- the pressure in the damping fluid volume is greater than the pressure at the pressure fluid connection 10.
- the ring body 13 is pressed with its piston base body-side axial ring surface 13d against the ring body-side axial mating ring surface 12a, whereby an annular sealing plane is formed there.
- the pressure medium from the damping pressure medium volume can now only flow back to the pressure medium connection 10 via the piston ring gap 16a in the piston ring 16, whereby the retraction movement of the piston unit 2 is counteracted by a damping force.
- the retraction movement is delayed until the piston unit 2 reaches the axial limit 11.
- the second operating state is shown in FIG. 6.
- the piston unit 2 completes a Ausfahrbewe movement. This is caused by the pressure medium flowing into the damping zone space 20 from the pressure medium connection 10 (as soon as the pressure at the pressure medium connection 10 is greater than that in the damping pressure medium volume).
- the ring body 13 also has a radial freedom of movement. This is provided by an annular gap 19 between the inner circumferential surface 13b and the guide pin 18.
- the axial gap 21 and the annular gap 19 form a continuous pressure medium inflow channel for the pressure medium flowing into the damping zone space 20.
- an axial groove 24 in the guide pin additionally increases the flow cross-section of the pressure medium inflow channel.
- the pressure medium can thus flow into the damping zone space 20 with a low pressure loss and the extension movement is hardly delayed.
- the mode of operation shown in FIGS. 5 and 6 corresponds, in the case of an embodiment with end position damping on both sides, to the interaction of the third and fourth operating states in the further damping zone 25 by means of the further annular body 28.
- the third operating state is during the retraction movement into the further damping zone 25 and the fourth operating state is during the extension movement taken from the further damping zone 25.
- the third operating state is the damping operating state and the fourth operating state is the exit operating state.
- FIGS. 5 and 6 a position transmitter 23 arranged on the cylinder tube is shown in FIGS. 5 and 6.
- FIG. 7 shows the piston unit 2 of an exemplary embodiment of a differential working cylinder with end position damping on both sides in an oblique view.
- the ring body 13, the piston ring 16 with its piston ring gap 16a, the locking ring 22, the guide 14 and the axial groove 24 are shown. Furthermore, axially opposite on the piston base body 12, the further ring body 28 and the further piston ring 31 arranged there with its further piston ring gap 31a are shown.
- the piston rings 16, 31 and the safety ring 22 are each formed by an elastic metal ring.
- the further securing ring and the further guide pin are covered and therefore have no reference symbols in FIG. 7.
- the ring body 13 receives the piston ring 16 in the inner ring groove 15 and is fixed with the safety ring 22 on the guide pin 18.
- the guide 14 is arranged in a groove in the piston base body 12.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE202019005218.6U DE202019005218U1 (en) | 2019-12-23 | 2019-12-23 | End-position cushioned working cylinder |
PCT/DE2020/000339 WO2021129900A1 (en) | 2019-12-23 | 2020-12-18 | Working cylinder with cushioned end-stroke |
Publications (2)
Publication Number | Publication Date |
---|---|
EP4081714A1 true EP4081714A1 (en) | 2022-11-02 |
EP4081714B1 EP4081714B1 (en) | 2023-11-22 |
Family
ID=74346760
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20848691.0A Active EP4081714B1 (en) | 2019-12-23 | 2020-12-18 | Working cylinder with cushioned end-stroke |
Country Status (7)
Country | Link |
---|---|
US (1) | US11953033B2 (en) |
EP (1) | EP4081714B1 (en) |
JP (1) | JP2023506142A (en) |
CN (1) | CN114829787A (en) |
DE (1) | DE202019005218U1 (en) |
DK (1) | DK4081714T3 (en) |
WO (1) | WO2021129900A1 (en) |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
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US3592106A (en) * | 1969-06-25 | 1971-07-13 | Cascade Corp | Ram with cushioned piston stroke |
US3626812A (en) * | 1970-07-09 | 1971-12-14 | Bucyrus Erie Co | Cylinder-cushioning arrangement |
FR2319795A1 (en) * | 1975-08-01 | 1977-02-25 | Renault | HYDRAULIC CYLINDER START ACCELERATION DEVICE |
US4048905A (en) * | 1976-03-29 | 1977-09-20 | The Boeing Company | Variable orifice hydraulic snubber |
US4207800A (en) * | 1978-11-02 | 1980-06-17 | Homuth Kenneth C | Single directional sealing piston ring |
JPH0650306A (en) * | 1992-07-29 | 1994-02-22 | Kayaba Ind Co Ltd | Cushion device of hydraulic cylinder |
DE29803739U1 (en) | 1998-03-04 | 1998-05-28 | Buemach Engineering Internatio | End position damping |
US6186043B1 (en) * | 1999-04-05 | 2001-02-13 | Deere & Company | Cushion hydraulic cylinder |
US10024344B2 (en) * | 2014-05-15 | 2018-07-17 | Ognibene Power S.P.A. | Hydraulic piston-cylinder group |
JP6403639B2 (en) * | 2015-06-29 | 2018-10-10 | 株式会社Taiyo | Cushioning device for fluid pressure cylinder |
JP6581457B2 (en) * | 2015-10-01 | 2019-09-25 | Kyb−Ys株式会社 | Fluid pressure cylinder |
-
2019
- 2019-12-23 DE DE202019005218.6U patent/DE202019005218U1/en active Active
-
2020
- 2020-12-18 EP EP20848691.0A patent/EP4081714B1/en active Active
- 2020-12-18 WO PCT/DE2020/000339 patent/WO2021129900A1/en unknown
- 2020-12-18 DK DK20848691.0T patent/DK4081714T3/en active
- 2020-12-18 US US17/787,675 patent/US11953033B2/en active Active
- 2020-12-18 CN CN202080088516.XA patent/CN114829787A/en active Pending
- 2020-12-18 JP JP2022532012A patent/JP2023506142A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
DE202019005218U1 (en) | 2021-03-24 |
EP4081714B1 (en) | 2023-11-22 |
WO2021129900A1 (en) | 2021-07-01 |
CN114829787A (en) | 2022-07-29 |
DK4081714T3 (en) | 2024-02-26 |
US20230011362A1 (en) | 2023-01-12 |
US11953033B2 (en) | 2024-04-09 |
JP2023506142A (en) | 2023-02-15 |
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