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
  • F15B15/1438—Cylinder to end cap assemblies
• • 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
  • F15B15/1428—Cylinders
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
  • F16B21/00—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings
  • F16B21/10—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts
  • F16B21/16—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft
  • F16B21/18—Means for preventing relative axial movement of a pin, spigot, shaft or the like and a member surrounding it; Stud-and-socket releasable fastenings by separate parts with grooves or notches in the pin or shaft with circlips or like resilient retaining devices, i.e. resilient in the plane of the ring or the like; Details

Definitions

• the invention relates to a working cylinder, in particular a hydraulic working cylinder.
• Working cylinders are known as such from the prior art. They usually have a cylinder tube and closure parts coupled to it.
• Both screw-on cylinders and cylinders with screw connection of only one closure part and MAG welding of the other closure part are provided in high quality according to the state of the art and have proven to be high-quality and reliable products.
• a manufacturing disadvantage is that it is difficult to coordinate the threads of the closure parts and the cylinder tube in such a way that, in the event of a desired special angular position of the closure parts relative to one another or to the cylinder tube, a suitable tightening torque is applied when screwing.
• the working cylinder has a cylinder and a piston unit as basic components. It is characterized in particular by a specially designed coupling section.
• the cylinder of the working cylinder according to the invention has a cylinder tube, a closure part and a further closure part.
• the cylinder tube has two opposite cylinder tube end sections with a cylinder tube end section and a further cylinder tube end section.
• the closure part is arranged on the cylinder tube end section and the further closure part is arranged on the further cylinder tube end section.
• the cylinder tube end section and the further cylinder tube end section are also collectively referred to below as the cylinder tube end sections.
• the closure part and the further closure part are also collectively referred to as the closure parts.
• the cylinder tube and the closure parts arranged thereon form a cylinder interior.
• the piston unit forms at least one working space in the cylinder interior.
• the piston unit is preferably made as an assembly Piston and piston rod are formed, with the piston rod slidingly passing through one of the closure parts, which is then present as a guide closure part.
• the piston unit can also be present, for example, as a plunger piston or as a piston unit of a synchronous cylinder.
• the working cylinder according to the invention is characterized by a coupling section designed in a special way.
• the coupling section has the closure part, the cylinder tube end section, a segmented coupling ring and a locking body.
• the closure part is arranged to be inserted axially into the cylinder tube end section.
• the closure part has a cylindrical outer surface, also referred to as the outer surface of the closure part
• the cylinder tube has a cylindrical inner surface, also referred to as the inner surface of the cylinder tube.
• the closure part is thus enclosed radially by the inner surface. Both lateral surfaces correspond in diameter, whereby the closure part is fixed in its positional relationship relative to the cylinder tube with the exception of the axial positional relationship, i.e. except for the linear degree of freedom along the cylinder's longitudinal axis.
• a supporting press fit can also be available as an option.
• the cylinder tube has a circumferential inner ring groove on the inner surface.
• the contour corresponds to the cross section of the coupling ring and is preferably essentially semicircular in the case of a circular coupling ring cross section.
• the closure part has an axially distal outer ring groove that is open on one side on its outer surface.
• the axial cylindrical point is considered to be axially distal.
• the contour corresponds to the cross section of the coupling ring and is preferably essentially quarter-circle-shaped in the case of a circular coupling ring cross section.
• the inner ring groove and the outer ring groove form an annular groove space in which the coupling ring is arranged.
• the coupling ring is radially enclosed by the outer ring groove. Since the outer annular groove on the closure part is designed to be axially open on one side, the annular groove space spanned by the two annular grooves is not completely enclosed by the annular grooves, but is instead accessible axially distally.
• the coupling ring is segmented by means of separating cuts. It consists of several coupling ring segments, hereinafter also referred to as ring segments.
• the ring segments are arranged butt-butting to one another at the separating cuts.
• the ring segments lie against each other with practically no gap due to the butt-butting arrangement.
• the surfaces of the separating cuts opposite each other at the butt joint are essentially parallel to one another.
• all ring segments together form a practically gap-free ring body and span an angle of 360 degrees.
• a particular advantage over a resilient piston ring with a piston ring gap is that a continuous annular surface or ring line for force transmission is provided on the one hand between the groove wall of the inner ring groove and the coupling ring and on the other hand between the coupling ring and the groove wall of the outer ring groove.
• the separating cuts of at least one piston ring segment are designed to be parallel or opening in a concentric direction to one another.
• a surprising solution was therefore found with an eccentric joining direction to arrange the coupling ring in the outer ring groove with virtually no gap, whereas this is not possible with radial cutting cuts.
• Designed to be parallel is to be understood as meaning that the separating cuts have mutually parallel surfaces at one end of a ring segment and at the other end of a ring segment.
• separating cuts at one end of a ring segment and at the other end of a ring segment have surfaces relative to one another, the plane planes of which are, on the one hand, essentially parallel to the longitudinal axis of the cylinder and, on the other hand, are at an angle which is a Insertion of the relevant ring segment in a radially eccentric direction allows.
• the closure part In cooperation with the outer ring groove and the inner ring groove, the closure part is fixed axially on one side by the coupling ring in a distal direction in a form-fitting manner. The full load resulting from the operating pressure is absorbed in this direction.
• the annular surface sections of the inner ring groove and the outer ring groove adapted to the coupling ring are advantageously available here, so that undesirably high surface pressures are avoided by sufficiently large areas.
• the locking body is arranged axially distally on the closure part by means of a releasable fastening.
• An axially distal arrangement is understood to mean that the locking body is arranged opposite the axially distal one-sided opening of the outer ring groove.
• a releasable fastening is understood to mean, in particular, a screw connection of the locking body to the closure part.
• the locking body can in particular be designed as an annular body if the closure part is a guide closure part, so that a free space remains for the piston rod.
• the blocking body can also be designed as a flat cylindrical body.
• the blocking body can also be in several parts.
• the locking body has a circumferential annular surface which forms pressure contact with the coupling ring and the coupling ring in the annular groove space positively determined.
• the contour of the annular surface can preferably correspond to the cross section of the coupling ring and can, for example, be essentially quarter-circle-shaped.
• the blocking body can thus cover the remaining open section of the annular groove space.
• other contours are also possible, for example part-circular contours of less than 90 degrees, inclined ring surfaces without curvature or part-circular contours with a radius that deviates from the coupling ring cross section, for example in order to optimize the pressure contact and thus the positioning of the coupling ring.
• the locking body secures the closure part axially on one side in a form-fitting manner in a proximal direction by means of the pressure contact with the coupling ring.
• the load transfer here takes place indirectly via the releasable fastening, which is advantageous but not problematic since only small forces, for example from the friction of the piston unit in a guide closure part, have to be absorbed in this direction.
• the solution according to the invention has the following advantages in particular.
• the continuous ring surface or ring line for force transmission on the one hand between the groove wall of the inner ring groove and the coupling ring and on the other hand between the coupling ring and the groove wall of the outer ring groove avoids uneven stresses in the groove areas of the coupling partners, reduces notch stresses, for example, and thus increases the maximum load capacity.
• the possible high load capacity is also advantageous, since the coupling ring does not have to be designed with springs due to its segmentation and can have a large cross section.
• Another advantage is that the coupling is particularly easy to detach. With the appropriate design, it is therefore possible to use a screwdriver or wrench with a standard drive to dismantle the locking body, remove the ring segments and thus remove the locking part for inspection or repair purposes.
• the working cylinder is characterized in that the piston ring has four piston ring segments and all separating cuts are designed parallel to one another.
• the two similar ring segments of the first type there are two similar ring segments of the first type and two similar ring segments of the second type.
• the ring segments of the same type are each arranged opposite one another. After the two ring segments of the first type are positioned in the inner ring groove, the two ring segments of the second type can be inserted from the center in a radially eccentric direction due to the parallel separating cuts. It can therefore be used using the four ring segments
• the coupling ring can be joined over 360 degrees to form a completely closed, practically gap-free ring body.
• the working cylinder is characterized in that the locking body is arranged in the proximal direction with an axial elastic prestress.
• the coupling between the cylinder tube and the closure parts is subject to high mechanical stress due to the high and changing operating pressures and the associated dynamic loads.
• this can lead to undesirable play occurring, which is also known as so-called breathing.
• Such play can occur when the groove walls of the annular grooves and the coupling ring form against one another.
• the working cylinder is characterized in that the releasable fastening of the locking body is designed by means of cap screws, the respective screw head of which has a one-sided support on the locking body and an axial force on the support and that the cap screws have an elastic bend to their longitudinal axis exhibit.
• the working cylinder is characterized in that the circumferential annular surface of the locking body is designed as a cone.
• the circumferential ring surface forms a pressure contact with the coupling ring.
• a distribution of force on the coupling ring into an axial and a radial portion is effective by means of the annular surface inclined as a cone, the axial portion pushing the piston ring in particular into the outer ring groove of the closure part and the radial portion Piston ring is pressed in particular into the inner ring groove of the cylinder and thus counteracts the development of play and breathing.
• the working cylinder is characterized in that a coupling section according to the invention is arranged on both cylinder tube end sections.
• Both coupling sections have the same basic structure, so that the description content for the coupling section also applies in a corresponding manner to the further coupling section at the opposite end of the cylinder tube.
• a solution is therefore advantageously provided in which access for inspection or repair purposes is made possible at both ends of the working cylinder.
• this is advantageously possible Cylinder tube to be designed the same way at both ends and thus simplify production.
• FIG. 4 sectional view of a working cylinder
• Fig. 8 Axial view of the coupling section
• the cylinder 1 shows, in an exemplary embodiment, a guide-side section of a working cylinder with the coupling section 7 arranged there on the cylinder 1.
• the cylinder 1 has a closure part 4a, here designed as a guide closure part, and a cylinder tube 3.
• the cylinder tube end section 5a is arranged, which in the present case is designed as a separate sleeve.
• the cylinder tube 3 can also be designed to be monolithic.
• An interior space 6 is formed by the closure parts 5a, 5b.
• the piston rod of the piston unit 2 and the at least one working space 6.1 formed in this way, in the exemplary embodiment the piston rod space, are shown.
• the coupling section 7 has, in addition to the cylinder tube end section 5a, the coupling ring 8 and the locking body 9 with the releasable fastening 10.
• Fig. 2 shows the coupling section in an enlarged view, with a representation in Fig. 2 initially being without the coupling ring 8.
• the cylinder tube 3 has an inner ring groove 11.1 on its cylinder tube end section 5a, which is arranged on the inside of the cylindrical cylinder tube inner surface.
• the inner ring groove 11.1 has a substantially semicircular contour.
• the closure part 4a has on its cylindrical outer surface the outer annular groove 11.2, which has a substantially quarter-circle-shaped contour and is therefore open on one side in the distal axial direction.
• the two annular grooves 11.1, 11.2 span the annular groove space 11.3.
• the locking body 9 is annular in the exemplary embodiment and is placed axially in such a way that its circumferential annular surface 9.1 is the one of the two Ring grooves 11.1, 11.2 still left open quadrant of the ring groove space covered. Furthermore, the axial directions distal and proximal are shown by arrows.
• the locking body 9 is elastically prestressed in the axially proximal direction and transmits a force to the coupling ring 8 via the circumferential annular surface 9.1.
• the circumferential annular surface 9.1 is designed as a cone and thus has an inclined contour force-forming, advantageously acts as an inclined plane and thus increases the force for pressing the coupling ring into the annular grooves 11.1, 11.2. This advantageously prevents play from forming as a result of the high and dynamic operating loads acting axially distally and causing the working cylinder to breathe.
• Fig. 4 shows, in addition to Fig.
• FIG. 5 shows a four-part embodiment variant of the coupling ring 8.
• all the separating cuts 8.1 are aligned parallel.
• Four coupling ring segments 8.2 are formed by the four separating cuts 8.1.
• Fig. 6 shows, in addition to Fig. 5, a schematic representation of the exemplary embodiment with parallel separating cuts 8.1.
• the two coupling ring segments of the first type (shown on the left and right) can be positioned in the inner ring groove 11.1.
• the two coupling ring segments of the second type (shown above and below) can then be inserted between the coupling ring segments 8.2 of the first type by means of an eccentric radial joining movement.
• the respective joining movement of the coupling ring segments 8.2 of the second type is shown by the two arrows.
• Fig. 7 essentially corresponds to Fig. 6, so that the description content there applies in a corresponding manner. Deviating from the exemplary embodiment in Fig.
• the joining between the coupling ring segments 8.2 of the first type is made easier and on the other hand the wedge-shaped inlet ensures pressure contact on the separating cuts 8.1 made, which supports the gap-free positioning of the coupling ring segments 8.2 relative to one another.
• the locking body 9 is designed here as an annular body, which in this way surrounds the passage of the piston rod.
• the detachable fastening 10 is formed by three screws arranged at an angle of 120 degrees, the head of which rests on one side with the one-sided support 10.1 on the locking body and on the axially lower support of the closure part 4a.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)
• Actuator (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=87036610

Family Applications (1)

Country Status (6)

Family Cites Families (11)

• 2022
  • 2022-06-10 DE DE102022002094.7A patent/DE102022002094A1/de active Pending
• 2023
  • 2023-06-01 WO PCT/DE2023/000044 patent/WO2023237141A1/de not_active Ceased
  • 2023-06-01 CN CN202380045816.3A patent/CN119452175A/zh active Pending
  • 2023-06-01 US US18/873,171 patent/US12560185B2/en active Active
  • 2023-06-01 JP JP2024570952A patent/JP2025520304A/ja active Pending
  • 2023-06-01 EP EP23734443.7A patent/EP4536979A1/de active Pending

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