EP3171021A1 - Hydrostatische axialkolbenmaschine - Google Patents

Hydrostatische axialkolbenmaschine Download PDF

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Publication number
EP3171021A1
EP3171021A1 EP16195300.5A EP16195300A EP3171021A1 EP 3171021 A1 EP3171021 A1 EP 3171021A1 EP 16195300 A EP16195300 A EP 16195300A EP 3171021 A1 EP3171021 A1 EP 3171021A1
Authority
EP
European Patent Office
Prior art keywords
ball
piston
dome
spherical
hydrostatic
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
Application number
EP16195300.5A
Other languages
German (de)
English (en)
Other versions
EP3171021B1 (fr
Inventor
Martin Bergmann
Lukas Krittian
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.)
Linde Hydraulics GmbH and Co KG
Original Assignee
Linde Hydraulics GmbH and Co KG
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Filing date
Publication date
Priority claimed from DE102015121882.8A external-priority patent/DE102015121882A1/de
Application filed by Linde Hydraulics GmbH and Co KG filed Critical Linde Hydraulics GmbH and Co KG
Publication of EP3171021A1 publication Critical patent/EP3171021A1/fr
Application granted granted Critical
Publication of EP3171021B1 publication Critical patent/EP3171021B1/fr
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Classifications

    • 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
    • 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
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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

Definitions

  • the invention relates to a hydrostatic axial piston machine with at least one in a receiving bore of a cylinder barrel longitudinally displaceable piston, wherein the piston is articulated by means of a ball and a dome-shaped recess formed ball joint on a support element, wherein between the piston and the support member, a hydrostatic discharge is formed ,
  • Known hydrostatic axial piston machines use ball joint connections between a piston and a support element and thus between the power-converting components.
  • an axial piston machine designed as a swash plate machine such ball joint connections between the piston and a sliding block are used as the supporting element.
  • an axial piston machine designed as a bent-axis machine such ball joint connections between the piston and a drive flange are used as the support element.
  • the piston is arranged longitudinally displaceable in a receiving bore of the cylinder drum of the axial piston, wherein the piston and the receiving bore form a pressurized displacement.
  • the impressed by the pressure in the displacement chamber on the piston piston forces lead to high pressures and loads in the ball joint.
  • the piston is provided with a connecting bore which connects the displacement of the piston with the spherical gap between the ball and the dome-shaped recess of the ball joint, so that the pressure of the displacement chamber is passed into the spherical gap of the ball joint. Therefore, in the spherical gap of the ball joint, a hydrostatic relief pressure field builds up with a hydrostatic unloading force that compensates for the piston forces.
  • the ball and the dome-shaped recess are each made idealgeometrisch, i. the ball and the dome-shaped recess are each formed with a spherical surface, carries the ball only in the pole or on the line of contact between the bore tip of the connecting hole and the dome-shaped recess, which is formed due to manufacturing in the surface of the ball.
  • the spherical gap in the ball joint continuously increases, so that no appreciable hydrostatic relief pressure field for the hydrostatic relief of the piston forces in the ball joint connection can be constructed and high leakage losses occur at the spherical gap of the ball joint connection.
  • an ideal geometrically produced ball and dome-shaped recess thus results in a low hydrostatic discharge of the piston forces, which leads to high pressure at the bearing line of contact between the ball and the dome-shaped recess, resulting in high friction in the ball joint, high wear of the ball joint connection and high Losses of the axial piston machine result.
  • the contact line with which the ball is supported in the dome-shaped recess and with which carries the ball to move towards the equator of the dome-shaped recess and to adapt the shape of the dome-shaped recess accordingly by the AusNOungsradien the dome-shaped recess are laterally offset from the longitudinal axis of the dome-shaped recess.
  • the production and production of such a dome-shaped recess can be done on a lathe, when the laterally displaced AusNOungsradius is rotated relative to the longitudinal axis and thus the central axis of the dome-shaped recess.
  • the piston with its longitudinal axis to the longitudinal axis of the recess tends - which occurs during operation of the axial piston engine principle migrates from the pressure in the displacement piston normal force with increasing inclination angle from the direction of the hydrostatic discharge force of the relief pressure field, whereby the percentage relief of the piston normal forces reduces the hydrostatic discharge force.
  • a dome-shaped recess thus has the inclination and thus the misalignment of the piston to the longitudinal axis of the dome-shaped recess an influence on the degree of relief of the piston normal force by the hydrostatic discharge.
  • the present invention has for its object to provide an axial piston machine of the type mentioned in which the ball joint connection can be made with little manufacturing effort and in which the inclination and thus the misalignment of the piston to the longitudinal axis of the dome-shaped recess has no effect on the degree of relief the piston has normal force by the hydrostatic discharge.
  • the dome-shaped recess is formed as a spherical recess with a AusNOungsradius and the ball is formed only in a contact region of the ball joint, which is disposed between the equator and the pole of the spherical recess, as a spherical cap with a spherical radius and the surface of the ball in the direction of the pole and the equator of the spherical recess is withdrawn relative to the spherical cap.
  • the dome-shaped recess is carried out idealgeometrisch and has a spherical, spherical surface with a AusNFungsradius on.
  • Adapted shape of the ball is thus by an adapted form the ball, the contact line with which the ball is supported in the dome-shaped recess and with which carries the ball, moved in the direction of the equator of the dome-shaped recess.
  • the ball is for this purpose according to the invention only in the contact region of the ball joint, which is arranged between the equator and the pole of the spherical recess formed as a spherical cap with a spherical radius and the surface of the ball in the direction of the pole and the equator of the spherical recess relative to the spherical cap retracted is.
  • the ball is thus carried out only idealgeometrisch in the contact area and has only in the contact area on a spherical, spherical surface with the ball radius.
  • the ball is thus designed only in the contact area as a spherical layer with a spherical surface.
  • the ball is retracted relative to the ideal geometric ball shape.
  • the ball joint connection according to the invention results in a lower manufacturing costs, since the dome-shaped recess, which is idealgeometrisch designed as a spherical surface, easy to manufacture and manufacture, and the displacement of the contact line can be produced by the special shape of the ball.
  • the special shape of the ball can in this case be produced and manufactured in a simple manner, for example by a turning operation, whereby the ball-and-socket joint according to the invention has a simple production with a low manufacturing outlay of the ball and socket joint.
  • the hydrostatic relief pressure field is also symmetrical to the longitudinal axis of the piston. If the piston tilts with its longitudinal axis to the longitudinal axis of the recess - which basically occurs in axial piston machine during operation of the axial piston - is achieved that the inclination and thus the inclination of the piston to the longitudinal axis of the dome-shaped recess has no effect on the degree of relief of the piston normal force by the has hydrostatic discharge.
  • the ball is provided in the direction of the pole and the equator of the spherical recess with reduced ball radii and tangential transitions.
  • the shape of the ball in the region of the pole and of the equator can be easily withdrawn relative to the ideal geometrical spherical shape which is formed in the contact region.
  • the piston for hydrostatic discharge of the ball joint connection is provided with a connecting bore which connects the displacement chamber, which is formed by the receiving bore of the cylinder barrel and the longitudinally displaceable piston, with the ball joint connection.
  • the pressure from the displacement chamber can be guided in a simple manner into the spherical gap of the ball joint connection in order to be able to build up a hydrostatic relief pressure field and a hydrostatic relief force in the ball joint connection.
  • the axial piston machine according to the invention can be designed as a swash plate machine according to an advantageous embodiment of the invention, wherein the support element is designed as a sliding block.
  • the ball can be arranged on the piston and the dome-shaped recess on the sliding block.
  • the ball on the shoe and the dome-shaped recess is arranged on the piston.
  • the axial piston machine according to the invention can be designed according to an alternative and also advantageous embodiment of the invention as a bent axis machine, wherein the support element is designed as a drive flange.
  • the ball is expediently arranged on the piston and the dome-shaped recess on the drive flange.
  • FIG. 1 a hydrostatic axial piston machine 1 according to the invention in swash plate design is shown in a longitudinal section.
  • the Axialkolbentriebmaschine 1 has a rotatable about a rotational axis D arranged cylinder drum 2, which is provided with a plurality of concentric with the axis of rotation D receiving bore 3, which are preferably formed by cylinder bores and in each of which a piston 4 is arranged longitudinally displaceable.
  • the cylinder drum 2 is supported in the axial direction with an end face on a housing-fixed control surface 5, which is formed on a disc-shaped control base 6 which is rotatably attached to a housing 7 or a corresponding housing cover 7a of the housing 7.
  • the control base 6 is provided for controlling the supply and discharge of pressure medium in the displacer spaces V formed by the receiving bores 3 and the pistons 4 with kidney-shaped control recesses which form an inlet connection 8 and an outlet connection 9.
  • the inlet connection 8 communicates with a channel 10 in the housing 7 or the housing cover 7a.
  • a channel 11 formed in the housing 7 or the housing cover 7a is connected.
  • the receiving bores 3 are provided on the end face of the cylinder drum 2, each with a preferably kidney-shaped connecting channel 12, around the displacer V formed by the piston 4 and the mounting holes 3 at a rotation of the Cylinder drum 2 about the rotation axis D alternately to the inlet port 8 and the outlet port 9 to connect.
  • the cylindrical drum 2 is penetrated by a central bore, which forms a concentric with the axis of rotation D arranged recess 14 through which a concentric with the axis of rotation D arranged drive shaft 15 is guided through the cylinder drum 2.
  • the drive shaft 15 is rotatably supported by bearings 16, 17 in the housing 7.
  • the cylinder drum 2 is rotatably connected to the drive shaft 15, but axially displaceably connected, for example by means of a toothing 18.
  • a arranged in the recess 14 spring 19 is used for pressing the cylinder drum 2 to the control surface. 5
  • the engine pistons 4 are supported in the region projecting out of the cylinder drum 2 by means of a support element AE designed as a sliding shoe 21 on the stroke-generating lifting disk 20, for example a swashplate, inclined to the rotation axis D.
  • the lifting disk 20 may be integrally formed or fixed to the housing 7, the axial piston engine 1 having a fixed displacement volume.
  • the sliding shoes 21 are articulated to the respective piston 4 by means of a spherical joint KV formed as a spherical joint.
  • the ball joint KV is formed by a ball K and a hollow spherical, dome-shaped recess KA.
  • the ball K is arranged on the supporting element AE formed by the sliding shoe 21 and the dome-shaped recess KA on the piston 4.
  • each piston 4 is provided with a connecting bore VB, which connects the displacement chamber V of the piston 4 with the ball joint connection KV.
  • the sliding blocks 21 are in operative connection with a hold-down device 25, which prevents lifting of the sliding shoes 21 and thus the piston 4 of the lifting disc 20.
  • FIG. 2 a hydrostatic axial piston machine 100 according to the invention in a bent-axis design is shown in a longitudinal section.
  • the axial piston machine 100 designed as a bent-axis machine has a housing 102 in which a drive shaft 104 provided with a drive flange 103 is mounted rotatably about a rotation axis D1 by means of a bearing device 105.
  • a cylinder drum 107 is arranged in the housing 102, which is arranged rotatably about a rotational axis D2 with a plurality of concentric with the rotational axis D2 of the cylinder drum 107 arranged receiving bores 109, which are preferably formed by cylinder bores and in which a piston 110 is arranged longitudinally displaceable.
  • the axis of rotation D1 of the drive shaft 104 intersects the axis of rotation D2 of the cylinder drum 107 at the point of intersection SP.
  • the cylinder drum 107 rests with an end face against a control body 112 provided with a control surface 111, which is fastened in a rotationally fixed manner to the housing 102 or a corresponding housing cover 102a of the housing 102.
  • kidney-shaped control recesses are formed to control the supply and discharge of pressure medium in the Verdrängerlor V formed by the receiving bores 109 and the piston 110, which form an inlet port 113 and an outlet port 114 of the axial piston machine 100.
  • the cylindrical drum 107 is provided on each receiving bore 109 with a preferably kidney-shaped connecting channel 115.
  • the in the FIG. 2 illustrated axial piston machine 1 is designed as a constant machine with a constant displacement volume.
  • the constant machine is the Tilt angle of the rotation axis D2 of the cylinder drum 107 with respect to the rotation axis D1 of the drive shaft 104 fixed.
  • the control body 112 by means of an adjusting device, for example a pivoting slide, adjustable in inclination, whereby the axial piston engine 1 has a variable displacement volume.
  • the cylinder drum 107 is supported on a support pin 120 pivotally connected to the drive flange 103 by a ball joint, and a spring 121 is further supported on the support pin 120, which presses the cylinder drum 107 against the control body 112 provided with the control surface 111.
  • the support pin 120 is arranged concentrically to the rotational axis D2 of the cylinder drum 107 and arranged in a corresponding receiving bore 122 of the cylinder drum 107.
  • the pistons 110 are articulated in the region projecting out of the cylinder drum 107, in each case on the supporting element AE designed as a drive flange 103.
  • a spherical joint KV designed as a spherical joint is respectively formed between the respective piston 110 and the drive flange 103.
  • the ball joint KV is formed by a provided with a ball K ball head 110a of the piston 110 and a hollow spherical, dome-shaped recess KA in the cylindrical drum 107 facing end face of the drive flange 103, in which the piston 110 is fixed to the ball head 110a.
  • each piston 110 is provided with a connecting bore VB, which connects the displacement chamber V of the piston 110 with the ball joint connection KV.
  • a hold-down plate 135 is provided.
  • the hold-down plate 135 is fastened to the drive flange 103 by means of screw connections 136.
  • FIG. 3 a ball joint connection KV of an axial piston machine of the prior art is shown.
  • the ball K arranged on the piston 110 into the dome-shaped recess KA of the drive flange 103, it is necessary for the ball K to be produced with a smaller ball radius R1 than the recess radius R2 of the dome-shaped recess KA.
  • the ball K and the dome-shaped recess KA are each made idealgeometrisch, ie, the ball K and the dome-shaped recess KA are each formed with a spherical surface.
  • the spherical gap S in the ball joint connection KV increases continuously, so that no significant hydrostatic relief pressure field for the hydrostatic relief of the piston forces in the ball joint connection KV can be built up and high leakage losses at the spherical Gap S of the ball joint connection KV result.
  • FIG. 4 a ball joint KV of an axial piston machine according to the invention is shown.
  • the ball joint KV of FIG. 4 can also be used between a piston 4 and a shoe 21 as a support element AE a swash plate machine.
  • the dome-shaped recess KA is manufactured and manufactured with ideal geometry, ie the dome-shaped recess KA has a spherical, spherical surface with a recess radius R2.
  • the contact line KL is in the FIG. 4 the contact line KL, with which the ball K is supported in the dome-shaped recess KA and with which carries the ball K, moved in the direction of the equator AQ of the dome-shaped recess KA. This is at the FIG. 4 According to the invention adapted to the shape of the ball K.
  • the ball K is manufactured and manufactured in such a way that the ball K is supported only in a contact area KB of the ball joint KV, in which the ball K is supported in the recess KA, i. in the region of the contact line KL, which is arranged between the equator AQ and the pole P of the spherical recess, formed as a spherical cap KK with a spherical radius R1.
  • the ball K is thus formed only in the contact area KB as a spherical disk with the surface of a spherical cap KK and thus formed idealgeometrisch only in the contact area KB, i. formed with a spherical surface.
  • the ball K is provided in the direction of the pole P and the equator AQ of the spherical recess KA with ball radii R3, R4 reduced in relation to the ball radius R1, which have tangential transitions to the spherical cap KK.
  • the hydrostatic relief pressure field DF - as in FIG. 5a is shown - arranged symmetrically to the longitudinal axis L2 of the piston 110. If the piston 110 with his Longitudinal axis L2 to the longitudinal axis L1 of the recess KA tends - as in the FIG. 5b is shown - is achieved by the fact that the inclination and thus the inclination angle ⁇ of the piston 110 to the longitudinal axis L1 of the dome-shaped recess KA has no effect on the Degree of relief of the piston normal force FK by the resulting hydrostatic discharge force HE of the relief pressure field DF.
  • FIGS. 4 In the ball joint connection KV of the invention FIGS. 4 .
  • dome-shaped recess KA is idealgeometrisch formed as a spherical recess and can be easily manufactured and manufactured.
  • the ball K with the adapted shape to produce the offset to the equator AQ of the recess KA contact line KL can also be easily and with low manufacturing costs by a simple external machining, for example by a turning, manufactured and manufactured, so that the inventive Ball joint KV has a simple production with low production costs and low production costs.
  • the axial piston machine 1, 100 according to the invention can be designed as a pump or as a motor.
  • the axial piston machine 1 can be designed as a constant machine with a constant displacement volume or as an adjusting machine with a variable displacement volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP16195300.5A 2015-11-19 2016-10-24 Hydrostatische axialkolbenmaschine Active EP3171021B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015120040 2015-11-19
DE102015121882.8A DE102015121882A1 (de) 2015-11-19 2015-12-15 Hydrostatische Axialkolbenmaschine

Publications (2)

Publication Number Publication Date
EP3171021A1 true EP3171021A1 (fr) 2017-05-24
EP3171021B1 EP3171021B1 (fr) 2020-01-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16195300.5A Active EP3171021B1 (fr) 2015-11-19 2016-10-24 Hydrostatische axialkolbenmaschine

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EP (1) EP3171021B1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167153A (en) * 1984-11-14 1986-05-21 Honda Motor Co Ltd Swash plate hydraulic devices
CA2116329A1 (fr) * 1991-11-21 1993-05-27 Colin Seabrook Pompes a eau et moteurs
US20030097927A1 (en) * 2001-11-28 2003-05-29 Nick Boone Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE102012108014A1 (de) * 2012-08-30 2014-03-06 Linde Hydraulics Gmbh & Co. Kg Gleitschuh einer hydrostatischen Axialkolbenmaschine
DE102012110564A1 (de) * 2012-11-05 2014-05-08 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Verdrängermaschine mit einer Rollenabstützung der Kolben

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2167153A (en) * 1984-11-14 1986-05-21 Honda Motor Co Ltd Swash plate hydraulic devices
CA2116329A1 (fr) * 1991-11-21 1993-05-27 Colin Seabrook Pompes a eau et moteurs
US20030097927A1 (en) * 2001-11-28 2003-05-29 Nick Boone Extended male slipper servo pad arrangement for positioning swashplate and method assembling same
DE102012108014A1 (de) * 2012-08-30 2014-03-06 Linde Hydraulics Gmbh & Co. Kg Gleitschuh einer hydrostatischen Axialkolbenmaschine
DE102012110564A1 (de) * 2012-11-05 2014-05-08 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Verdrängermaschine mit einer Rollenabstützung der Kolben

Also Published As

Publication number Publication date
EP3171021B1 (fr) 2020-01-01

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