Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/0082—Details
  • F01B3/0085—Pistons
  • F01B3/0088—Piston shoe retaining means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
  • F04B1/124—Pistons
  • F04B1/126—Piston shoe retaining means
• • 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
  • F16J—PISTONS; CYLINDERS; SEALINGS
  • F16J1/00—Pistons; Trunk pistons; Plungers
  • F16J1/10—Connection to driving members
  • F16J1/14—Connection to driving members with connecting-rods, i.e. pivotal connections
  • F16J1/22—Connection to driving members with connecting-rods, i.e. pivotal connections with universal joint, e.g. ball-joint

Definitions

• the invention is based on an axial piston machine in bent-axis design, having the features of the preamble of claim 1.
• Known axial piston machines of this type have an engine, which comprises as essential components a rotatably mounted drive shaft with a molded drive flange, a cylinder drum guided in axially extending cylinder bores, longitudinally displaceable piston and a control body.
• the longitudinally displaceably guided in the cylinder bores pistons each have at the free end after the formation of a neck on a spherical piston head which is rotatably received in a ball socket formed in the drive flange.
• a return pulley is provided, which engages behind the piston head and thus prevents it from sliding out of the spherical shells.
• the manufacture and installation of the return pulley is expensive.
• the retraction hole walls must be designed such that friction and wear are minimized during functional operation.
• For releasably securing the retraction disc further holes in the disc for receiving screws are required. Additional threaded holes in the drive plate to accommodate the mounting screws are necessary.
• the spherical piston heads rotatably holding bearing metal rings.
• the DT 20 61 906 or the DT 24 02 066 A1 each show such a solution.
• the spherical shell is provided here with an extension into which a bearing metal ring is pressed.
• the invention has for its object to further develop an axial piston oblique-axis design with the features of the preamble of claim 1 so that a pressure relief of the ball head is guaranteed in all cases.
• This object is achieved for an axial piston machine in bent-axis design with the features of the preamble by an additional equipment with the features of the characterizing part of claim 1.
• at least one groove is provided on the inner surface of the retraction rings, which has a course connecting the annular end sides together.
• the introduction of a groove in a retraction ring is particularly simple and fast.
• Such configured return ring allows during the Um Kunststoffvorganges a pressure relief to the leakage oil space.
• the so-called relief groove leads to an improvement of the hydrostatic discharge and to a reduced friction effect.
• the groove has a spiral shape.
• the groove can be screwed in with a simple tool directly when creating the ring. The tool is fixed and the ring is unscrewed. This results in a simple and cost-effective spiral groove.
• Other ways of the course of the relief groove are conceivable, for example, one or more grooves have an axial course.
• the inner diameter of the ring preferably widens radially at the piston head-side end, so that a pivoting of the piston against the drive flange is not limited by the ring.
• FIG. 1 shows a longitudinal section through an engine of an axial piston machine according to the invention
• FIG. 2 shows a longitudinal section through a spherical piston head corresponding to a detail A of Figure 1
• 3 shows a longitudinal section through a Triebflanschabterrorism from the front side of the drive flange up to a radial extension of two spherical shells
• Fig. 4 shows a longitudinal section through a retraction ring.
• engine 1 of an axial piston oblique-axis construction comprises as essential components a rotatably mounted drive shaft 2 with a molded drive flange 3, a cylinder drum 4 guided in axially extending cylinder bores 5, longitudinally displaceable piston 6 and a control body 7.
• the cylinder drum 4 arranged between the drive flange 3 and the control body 7 and is supported on the control body side with a concave bearing surface 8 on the facing convex control surface 9 of the control body 7 from.
• the cylinder drum 4 is rotatable about a centering pin 10 on the drive flange 3 and - in particular for adjusting the working stroke of the piston 6 - pivotally mounted.
• the centering pin 10 protrudes into a central cylinder bore 11 and is pressed by a compression spring 12, which is arranged between the centering pin 10 and the cylinder drum 4, to the drive flange 3.
• the longitudinally displaceably guided in the cylinder bores 5 piston 6 are designed conical.
• FIG. 2 shows a detailed detail A from FIG. 1, which comprises a ball head 15 which is rotatably fixed in a ball socket 16 with a retraction ring 17.
• the ball head 15 has a vertex 20 and an equatorial circuit 21.
• the center point of the equatorial circle 21 corresponds to the center of the ball head 15.
• the equatorial circle 21 encloses a 90 ° angle with the piston axis 22 and separates an upper hemisphere enclosing the vertex 23 from a lower hemisphere 24.
• the ball shell 16 passes over the upper hemisphere 23 of the ball head 15 out.
• the upper hemisphere 23 fits exactly into the ball socket 16.
• the inner diameter of the ball socket 16 springs back radially and becomes larger as a result.
• the shape of the spherical shell 16 from the radial recess 30 to an opening of the spherical shell 16 is shown in Fig. 3.
• a cylindrical transition 31 connects the radial recess 30 with a second radial recess 32.
• the retraction ring 17 has at the piston-side inner edge a bevel-shaped chamfer 40 at a 30 ° angle which has a depth of 5 mm.
• the retraction ring has a v-shaped spiral groove 41, which makes it possible for the pressed-in helical groove 41 State resource from the inner, piston head side annular end face 42 to the outer, piston neck-side annular end face 43 can flow.
• each piston head 15 has a pocket-shaped opening 25, from which a spiral groove 26 terminates in a circumferential annular groove 27 above the equatorial circle 21.
• the pocket-shaped opening 25 in the apex 20 of the piston head 15 is connected via a throttle point 28 and a subsequent Kolben preparegangsbohrung 29 with a working space 18 in the cylinder bore 5 in connection PHg.
• the ball shell 16 has a symmetrical to the longitudinal axis of the ball shell 16 pocket-shaped recess 35, the larger diameter than the diameter of the pocket-shaped opening 25 in the vertex 20 of the ball head 15th
• the region corresponding to the swivel angle range of the axial piston machine of the concave spherical shell surface constitutes a bearing surface 45, at which the Ball head surface with a bearing counter surface as a defined relief surface 46 is supported by an emerging in a bearing gap 48 pressure field 49.
• the relief surface 46 of a resulting hydrostatic bearing 47 is limited by the circumferential groove 27 on the upper hemisphere 23.
• the pressure field 49 absorbs the piston force and thus prevents a metallic contact between the ball head 15 and the concave spherical shell surface 45.
• the bearing gap 48 becomes smaller.
• the inlet pressure rises until the pressure difference at the throttle 28 is almost zero, ie the inlet pressure corresponds approximately to the supply pressure.
• the bearing 47 is hydrostatically relieved.
• the bearing gap 48 becomes larger, the inlet pressure drops and approaches the supply pressure until the bearing 47 is hydrostatically relieved at approximately equal pressures.
• the ball head 15 is pressed into the retraction ring 17 and operating means can flow via the spiral groove 41 in the retraction ring 17 in a leakage oil chamber 50.
• the inlet pressure drops and at approximate pressure equilibrium, the ball bearing 47 is hydrostatically relieved.
• the groove shape in the retraction ring is not limited to a spiral, but it is important that the ring end faces are connected via the groove.
• the compound consists e.g. even with at least one axially extending groove.

Landscapes

• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Reciprocating Pumps (AREA)
• Pistons, Piston Rings, And Cylinders (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=41571815

Family Applications (1)

Country Status (5)

Families Citing this family (11)

Family Cites Families (16)

• 2009
  • 2009-01-21 DE DE200910005390 patent/DE102009005390A1/de not_active Withdrawn
  • 2009-12-11 CN CN200980155016.7A patent/CN102292541B/zh not_active Expired - Fee Related
  • 2009-12-11 WO PCT/EP2009/008869 patent/WO2010083861A1/de active Application Filing
  • 2009-12-11 EP EP09795333A patent/EP2389514A1/de not_active Withdrawn
  • 2009-12-11 US US13/145,090 patent/US8850953B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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