EP2930360A2 - Machine à piston axial dans une construction à axe oblique avec patins de guidage dans le plateau d'entraînement - Google Patents

Machine à piston axial dans une construction à axe oblique avec patins de guidage dans le plateau d'entraînement Download PDF

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Publication number
EP2930360A2
EP2930360A2 EP15160552.4A EP15160552A EP2930360A2 EP 2930360 A2 EP2930360 A2 EP 2930360A2 EP 15160552 A EP15160552 A EP 15160552A EP 2930360 A2 EP2930360 A2 EP 2930360A2
Authority
EP
European Patent Office
Prior art keywords
drive flange
axial piston
shoe
piston machine
machine according
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.)
Withdrawn
Application number
EP15160552.4A
Other languages
German (de)
English (en)
Other versions
EP2930360A3 (fr
Inventor
Martin Bergmann
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.)
LHY Powertrain GmbH and Co KG
Original Assignee
Linde Hydraulics GmbH and Co KG
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 Linde Hydraulics GmbH and Co KG filed Critical Linde Hydraulics GmbH and Co KG
Publication of EP2930360A2 publication Critical patent/EP2930360A2/fr
Publication of EP2930360A3 publication Critical patent/EP2930360A3/fr
Withdrawn legal-status Critical Current

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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
    • F01B3/0002—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0663—Casings, housings
    • F03C1/0665—Cylinder barrel bearing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0668—Swash or actuated plate
    • F03C1/0671—Swash or actuated plate bearing means or driven axis bearing 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
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2092—Means for connecting rotating cylinder barrels and rotating inclined swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to a hydrostatic axial piston machine in oblique axis construction with a drive shaft arranged rotatably about a rotation axis within a housing, with a drive flange rotatably disposed within the housing, and a cylinder drum arranged rotatably about a rotation axis within the housing of the axial piston machine, the cylinder drum provided with a plurality of piston recesses is, in each of which a piston is arranged longitudinally displaceable, wherein the pistons are hinged to the drive flange, and wherein the drive flange is supported on a housing-side sliding surface by means of a thrust bearing, which is designed as a hydrostatically relieved sliding bearing having a plurality of sliding shoes, each are mounted articulated in the drive flange and are provided on a facing on the sliding surface front side with a pressure pocket, the supply of pressure medium with an associated displacement of the Axialk Olbenmaschine communicate.
  • a thrust bearing which is designed as a hydrostatically relieve
  • the piston arranged longitudinally displaceably in the cylinder drum are usually fastened by means of a ball joint to the drive flange of a drive shaft.
  • the piston forces are based here on the piston on the drive shaft located on the drive flange and generate a torque.
  • a hydrostatically relieved slide bearing as thrust bearing it is already known in an axial piston machine in a bent axis machine in an axial end face of the drive flange, with the drive flange abuts a housing-side sliding surface, form pressure pockets, which are in communication with the displacement for supplying pressure medium ,
  • the drive flange is formed as a separate from the drive shaft component and arranged movable in the axial direction relative to the drive shaft.
  • a torque connection such as a spline toothing of the drive flange is connected to the drive shaft torque.
  • Such axial piston machines are for example from the FIG.
  • the present invention has for its object to provide a generic axial piston machine in Schrägachsenbauweise with a hydrostatic relief of the axial forces by the drive flange articulated sliding shoes available, which is operable at high speeds and at the same time has a high efficiency.
  • the sliding blocks are each articulated in such a manner in the drive flange, that with a rotating drive flange a compensating force acts on the sliding block, which is directed opposite to the centrifugal force acting on the shoe, wherein the point of application of the compensating force on the shoe selected is that on the sliding shoe no Abkippmoment arises or a Abkippmoment is partially or completely compensated.
  • the point of application of the compensating force on the shoe selected is that on the sliding shoe no Abkippmoment arises or a Abkippmoment is partially or completely compensated.
  • an acting on the shoe and the centrifugal force counteracting compensating force is generated, which acts on the shoe so that no slipping moment arises on the shoe or a Abkippmoment is partially or completely compensated.
  • the axial piston machine according to the invention can thus be prevented by the compensating force tipping of the shoe from the housing side sliding surface due to the force acting on the shoe centrifugal force, so that the axial piston according to the invention can be operated at high speeds without tilting the shoes, so that even at high speeds Increase of leakage at the hydrostatically relieved slide bearing between the shoes and the housing side sliding surface is prevented and the axial piston machine has a high efficiency at high speeds.
  • the point of application of the compensating force in the axial direction at the height of the center of gravity of the shoe ensures that the centrifugal force and the balancing force are directly opposite, so that no tilting moment arises on the shoe.
  • the sliding block is articulated in a recess of the drive flange, wherein the radial support point of the sliding block in the recess of the drive flange corresponds to the point of application of the compensating force.
  • the balancing force is thus applied to the radial support point of the shoe in the recess on which the centrifugal force of the shoe is supported.
  • the radial support point of the sliding block is located in the recess of the drive flange on a plane which is perpendicular to.rotation axis of the drive flange and arranged in the axial direction in the region of the center of gravity of the sliding block.
  • the plane goes in the axial direction through the center of gravity of the shoe is.
  • the sliding block is articulated in a recess of the drive flange, wherein the radial support point of the sliding block in the recess of the drive flange is spaced from the point of application of the compensating force in the axial direction.
  • This position of the point of application of the balancing force can be an the slip shoe from the centrifugal force resulting Abkippmoment be compensated in a simple manner to prevent tilting of the shoe from the housing side sliding surface.
  • the sliding block is operatively connected to a compensating body which partially or completely compensates for a tilting moment arising from the centrifugal force on the sliding block.
  • additional compensating bodies which are in operative connection with the sliding shoes and compensates partially or completely for the sliding shoes resulting from the centrifugal force, can also be prevented with little additional construction effort that tilt the sliding blocks at high speeds of the housing side sliding surface.
  • An expedient embodiment of the invention provides that the compensating body generates the compensating force acting on the sliding shoe, which is directed counter to the centrifugal force on the sliding shoe, wherein the point of application of the compensating body generated and acting on the shoe balance force in the region of the center of gravity of the shoe.
  • the point of application preferably lies in the center of gravity of the sliding shoe.
  • the sliding shoe can be mounted in a recess of the drive flange such that the radial support point of the sliding block is spaced in the recess of the drive flange in the axial direction from the center of gravity of the sliding block about a first lever arm.
  • the compensation body is articulated according to an advantageous embodiment of the invention on the drive flange by means of a hinge connection and is in operative connection with the slide shoe in the axial direction in the region of the center of gravity, wherein the balancing force is generated by the force acting on the balancing body centrifugal force.
  • the counteracting centrifugal force acting on the sliding shoe and the centrifugal force acting on the sliding shoe is thus generated by the centrifugal force acting on the compensating body.
  • the deflection of the force direction can be achieved with a particularly simple construction cost when the hinge connection of the compensation body is arranged on the drive flange in the axial direction between the center of gravity of the shoe and the center of gravity of the compensation body. From the center of gravity of the compensating body radially acting centrifugal force can be generated by this choice of articulation and thus the support point of the compensating body in the drive flange in a simple way at the center of gravity of the shoe a radially inward acting balancing force.
  • the articulation of the compensating body with the drive flange is for this purpose spaced from the center of gravity of the compensating body about a second lever arm.
  • the mass of the compensating body, the first lever arm and the second lever arm are designed such that the compensating force generated by the compensating body has substantially the same size as the centrifugal force acting on the sliding shoe.
  • the compensating body can be arranged radially outside of the sliding shoes and generate from the outside an acting on the shoe in the center of gravity of the shoe balance force.
  • the compensation body is arranged coaxially with the sliding block and within the radial dimensions of the sliding block in the drive flange.
  • the compensating body For receiving the compensating body in the drive flange of the drive flange is provided with a further recess according to an expedient development of the invention, in which the compensating body is articulated, wherein the further recess is arranged coaxially to the recess for the shoe.
  • the further recess is in operative connection with the displacer and the compensating body is provided with a connecting channel, by means of which the pressure pocket of the sliding block communicates with the displacer space.
  • a preferred embodiment of the invention is arranged for articulated mounting of the shoe in the recess of the drive flange and thus for the tilt compensation of the shoe in the recess of the drive flange of the shoe with a diameter clearance in the recess of the drive flange.
  • the shoe is provided in the region of the radial support point with a diameter extension.
  • the radial support point of the shoe in the recess can be formed in a simple manner and with little construction and thus for the balancing force a defined point of attack can be achieved.
  • the radial outer surface of the diameter extension is formed as a spherical surface whose center lies in the center of gravity of the shoe.
  • the radial outer surface of the diameter extension is formed as an annular surface.
  • the radial outer surface of the diameter extension is formed as a cylindrical surface, wherein between the cylindrical surface and the recess of the drive flange a diameter clearance is formed.
  • a spring device which acts on the sliding shoe in the direction of the housing-side sliding surface.
  • a pressure space is formed between the drive flange and the shoe, which is connected to the displacement chamber.
  • a pressure-dependent contact pressure of the sliding shoes on the housing-side sliding surface can be achieved in a simple manner.
  • the pressure pocket which is also connected to the displacement chamber, causes the sliding surface of the sliding shoe to be partially relieved of the housing-side sliding surface, so that an additional hydrostatic contact force acts on the sliding shoe.
  • the shoe is provided with a groove-shaped recess in which the sealing device, in particular a sealing ring, is arranged.
  • a connection of the pressure shoe pressing the pressure chamber can be achieved with the displacer with low construction costs, if at least one recess is formed in the region of the joint of the compensating body, by means of which the pressure chamber with the displacer is connectable ,
  • the drive flange and the drive shaft can be formed by separate components which are connected to one another in a force-locking or positive-locking manner. This may result in advantages in the production of these two components.
  • the drive flange is formed in one piece on the drive shaft in the axial piston according to the invention, so that the axial piston machine according to the invention is suitable for high speeds and can transmit a high torque.
  • the hydrostatic axial piston machine 1 designed as a bent axis machine according to FIGS FIGS. 1 and 2 has a housing 2, which consists of a housing pot 2a and a housing cover 2b, which is fixed to the housing pot 2a.
  • a drive shaft 4 provided with a drive flange 3 is rotatably mounted about a rotation axis R t by means of bearing devices 5a, 5b.
  • the drive flange 3 is integrally formed on the drive shaft 4, so that the drive shaft 4 and the drive flange 3 are made in one piece.
  • a cylinder drum 7 is arranged in the housing 2, which is arranged rotatably about an axis of rotation R z and provided with a plurality KolbenausEnglishept 8, which are arranged in the illustrated embodiment concentric with the axis of rotation R z of the cylinder drum 7.
  • a piston 10 is arranged longitudinally displaceable.
  • the rotation axis R t of the drive shaft 4 intersects the rotation axis R z of the cylinder drum 7 at the point of intersection S.
  • the cylinder drum 7 is provided with a central, concentric with the axis of rotation R z of the cylinder drum 7 arranged longitudinal recess 11 through which the drive shaft 4 extends therethrough.
  • the drive shaft 4 guided through the axial piston machine 1 is mounted on both sides of the cylinder drum 7 by means of the position devices 5a, 5b.
  • the drive shaft 4 is mounted with the drive flange side bearing device 5a in the housing pot 2a and with the cylinder drum side bearing device 5b in the housing cover 2b.
  • the drive shaft 4 is designed at the drive flange end with a torque transmission means 12, for example a spline, for introducing a drive torque or for tapping a drive output torque.
  • a torque transmission means 12 for example a spline
  • the opposite, cylinder-drum-side end of the drive shaft 4 guided through the axial piston machine 1 ends in the region of the housing cover 2b.
  • a concentric with the axis of rotation R t of the drive shaft 4 arranged bore 14 is formed, which is formed in the illustrated embodiment as a through hole.
  • the cylinder drum 7 is located to control the supply and discharge of pressure medium in the piston chambers formed by the piston recesses 8 and the piston 10 Verdrängeragonist V on a control surface 15 which is provided with not shown kidney-shaped control recesses, an inlet port 16 and an outlet port of Form axial piston 1.
  • the cylinder drum 7 is provided with a control opening 18 on each piston recess 8.
  • the axial piston machine 1 of FIGS. 1 and 2 is designed as a constant machine with a constant displacement volume.
  • the constant machine of the inclination angle ⁇ and thus the pivot angle of the rotation axis R z of the cylinder drum 7 with respect to the axis of rotation R t of the drive flange 3 and the drive shaft 4 is fixed and constant.
  • the control surface 15, against which the cylinder drum 17 abuts, is in this case formed on the housing 2, in the illustrated exemplary embodiment on the housing cover 2b or a rotatably arranged in the housing 2 control disc.
  • the pistons 10 are each hinged to the drive flange 3.
  • each formed as a spherical joint articulation 20 is formed between the respective piston 10 and the drive flange 3 .
  • the articulation 20 is formed in the illustrated embodiment as a ball joint, which is formed by a ball head 10a of the piston 10 and a spherical cap 3a in the drive flange 3, in which the piston 10 is attached to the ball head 10a.
  • the pistons 10 each have a collar portion 10b, with which the piston 10 is arranged in the piston recess 8.
  • a piston rod 10c of the piston 10 connects the collar portion 10b with the ball head 10b.
  • the collar portion 10b of the piston 10 is arranged with play in the piston recess 8.
  • the collar portion 10b of the piston 10 may be designed to be spherical.
  • a sealing means 21 for example a piston ring, is arranged on the collar portion 10b of the piston 10.
  • a spherical guide 25 is formed between the cylinder drum 7 and the drive shaft 4.
  • the spherical guide 25 is formed by a spherical portion 26 of the drive shaft 4, on which the cylinder drum 7 is arranged with a arranged in the region of the central longitudinal recess 11 hollow spherical portion 27.
  • the center of the sections 26, 27 lies on the intersection point S of the axis of rotation R t of the drive shaft 4 and the axis of rotation R z of the cylinder drum 7.
  • a driving device which couples the drive shaft 4 and the cylinder drum 7 in the direction of rotation.
  • the carrier device is not shown in detail.
  • a follower joint 30 which is formed in the illustrated embodiment as a constant velocity joint in Kegelstrahlbauwese and allows a rotationally synchronous entrainment of the cylinder drum 7 with the drive shaft 4, so that a uniform, synchronous rotation of the cylinder drum 7 with the drive shaft 4 results.
  • the trained as constant velocity joint driving joint 30 is formed in the illustrated embodiment as a cone beam half-roll joint 31.
  • the cone-beam half-roll joint 31 is formed by a plurality of roller pairs 50, 51 which are arranged between the drive shaft 4 and a sleeve-shaped driver element 40 connected in a rotationally fixed manner to the cylinder drum 7.
  • the drive shaft 4 also extends through the driving joint 30.
  • Each of the plurality of roller pairs 50, 51 of the cone-beam half-roller joint 31 consists of two and thus one pair of semi-cylindrical half-rollers 50a, 50b, 51a, 51b.
  • the semi-cylindrical half rollers 50a, 50b, 51a, 51b are each formed by a cylindrical body flattened substantially to a rotation axis RR t , RR z .
  • the pairs of half rollers 50a, 50b, 51a, 51b form planar sliding surfaces GF, against which the two half rollers 50a, 50b, 51a, 51b of a pair of rollers 50, 51 abut one another to form a surface contact.
  • the half rollers 50a, 50b, 51a, 51b are arranged in the radial direction within the pitch circle of the pistons 10 and spaced from the axes of rotation R t , R z .
  • the driving joint 30 can therefore be arranged space-saving within the pitch circle of the piston 10 and the drive shaft 4 are performed radially within the half-rollers of the cone-beam half-roll joint 31.
  • Each roller pair 50, 51 has a cylindrical drum-side half-roller 50a, 51a belonging to the cylinder drum 7 and a drive shaft-side half-roller 50b, 51b which abut one another on the flat sliding surfaces GF and are in contact with each other.
  • the cylindrical drum-side half roller 50a, 51a of the corresponding roller pair 50, 51 are each in a cylindrical, in particular partially cylindrical, cylinder drum side receptacle 55a and the drive shaft side half roller 50b, 51 b of a pair of rollers 50, 51 in a cylindrical, in particular partially cylindrical, drive shaft side housing 55b added and in the respective cylindrical receptacle 55a, 55b secured in the longitudinal direction of the corresponding axis of rotation.
  • each half rollers 50a, 51a, 50b, 51b are provided in the cylindrical portion with a collar 60 which engages in a groove 61 of the corresponding receptacle 55a, 55b.
  • the drive shaft-side half-roller 50b is shown by the roller pair 50 with thick lines and the cylindrical drum-side half-roller 50a resting on the half-roller 50b is shown with thin lines.
  • the cylindrical drum-side half roller 51 a is shown with thick lines and thin lines on the half roller 51 a resting drive shaft side half roller 51 b.
  • the half rollers 50b and 51a are in the sectional plane of the FIG. 2 lying flattened, flat sliding surfaces GF shown.
  • the rotational axes RR z of the cylinder-drum-side half rollers 50a, 51a are inclined to the rotation axis R z of the cylinder drum 7 by an inclination angle ⁇ .
  • the axes of rotation RR z of the cylindrical drum-side half rollers 50a, 51a intersect the axis of rotation R z of the cylinder drum 7 at the point of intersection S z .
  • the individual rotation axes RR z of the plurality of cylindrical drum-side half rollers 50a, 51a thus form a cone beam about the rotation axis R z of the cylinder drum 7 with the point at the intersection S z .
  • the inclination angle ⁇ of the rotation axes RR z of the cylinder drum side half rollers 50a, 51a to the rotation axis R z of the cylinder drum 7 and the rotation axes RR t of the drive shaft side half rollers 50b, 51b to the rotation axis R t of the drive shaft 4 are identical in magnitude.
  • the inclination angles ⁇ of the rotation axes RR z , RR t of the half rollers of the drive shaft 4 and the cylinder drum 7 to be coupled together are thus the same.
  • the plane E is therefore inclined at half the inclination angle or swivel angle ⁇ / 2 with respect to a plane E 1 perpendicular to the axis of rotation R t of the drive shaft 4 and a plane E 2 perpendicular to the axis of rotation R z of the cylinder drum 7.
  • the plane E passes through the intersection S of the axes of rotation R t , R z .
  • the half rollers 50a, 50b, 51a, 51b of the respective roller pair 50, 51 are arranged in the region of the points of intersection SP of the axes of rotation RR t , RR z , whereby at the intersections SP of the two half rollers of the respective roller pair 50, 51, the power transmission between the flat sliding surfaces GF takes place to take the cylinder drum 7.
  • a thrust bearing 100 is provided, which is designed as a hydrostatically relieved sliding bearing 102.
  • the hydrostatically relieved sliding bearing 102 comprises a plurality of sliding shoes 105, which are each mounted longitudinally displaceably and articulated in the drive flange 3 and are each provided with a pressure pocket 106 at an end surface facing the sliding surface 101, which is supplied with pressure medium having an associated displacement space V of the axial piston machine 1 keep in touch.
  • each piston 10 is associated with a shoe 105.
  • the pressure pockets 106 in the sliding shoes 105 are in each case connected via a connecting channel 107 in the drive flange 3 and a connecting channel 108 in the piston 10 with the respective displacement chamber V, which is formed by the piston recess 8 and the piston 10 arranged therein.
  • the housing-side sliding surface 101 can be formed directly in the housing 2 or as in the illustrated embodiment - on a circular disk 109 which is rotatably mounted on the housing 2.
  • the designed as hydrostatically relieved sliding bearing 102 thrust bearing 100 serves to hydrostatically relieve the axial forces occurring during operation of the axial piston 1 on the drive flange 3.
  • the axial force F A and thus the axial force component of the piston force F K is relieved by a generated by means of the sliding shoes 105 hydrostatic discharge force F E.
  • the bearing devices 5 a, 5 b of the drive shaft 4 can be dimensioned smaller so that small mass forces result in the bearing devices 5 a, 5 b and compact dimensions of the axial piston machine 1 according to the invention can be achieved.
  • the sliding shoes 105 are each acted upon by means of a spring device 110, for example a compression spring, in the direction of the housing-side sliding surface 101 and thus pressed against the housing-side sliding surface 101.
  • a spring device 110 for example a compression spring
  • the sliding shoes 105 are each arranged longitudinally displaceable and articulated in a recess 111 of the drive flange 103.
  • the recesses 111 are formed in the illustrated embodiment in each case by a to the rotation axis R t of the drive shaft 4 and the drive flange 103 concentrically arranged receiving bore.
  • a pressure chamber D is formed in each case, which is connected via the connecting channels 107 and 108 with the displacement chamber V.
  • a connecting channel 112 is arranged in each case, which connects the pressure pocket 106 with the pressure chamber D and thus with the associated displacement chamber V.
  • the pressure chamber D and the pressure pocket 106 are designed such that an additional hydrostatic contact force acts, which presses the sliding shoes 105 against the sliding surface 101.
  • the sliding shoe 105 is sealed in each case by means of a sealing device 115 with respect to the pressure chamber D.
  • the sliding shoe 105 is provided with a groove-shaped recess 116, in which the sealing device 115, for example a sealing ring, is arranged.
  • a support of the centrifugal force F F takes place with a centrifugal force F F opposite and directed radially inward compensation force F FR on the drive flange 3, which in the embodiment of FIGS. 1 to 4 is in the region of the recess 111.
  • the sliding shoes 105 are each articulated in the drive flange 103 in the axial piston machine 1 according to the invention in such a way that the point of application AP is the compensating force F FR the sliding block 105 is arranged such that on the sliding shoe 105 no Abkippmoment arises.
  • the position of the force pair, that of the centrifugal force F F and the opposing compensating force F FR is formed, to each other is thus selected according to the invention such that no centrifugal force Abkippmoment caused on the shoe 105.
  • the radial support point A of the shoe 105 in the recess 111 of the drive flange 3, which acts on the compensating force F FR , arranged on a plane EE, which is directed perpendicular to the axis of rotation R t of the drive flange 3 and in the axial direction in the region of the center of gravity SP of the shoe 105 is arranged.
  • the radial support point A thus forms the point AP of the compensating force F FR .
  • the centrifugal force F F and the opposing compensating force F FR have aligned operating lines.
  • the force pair formed from the centrifugal force F F and the opposing compensating force F FR is therefore directly and directly opposite, so that the centrifugal force F F and the counteracting compensating force F FR have no lever arms to the support point A of the shoe 105 in the recess 111 and thus no centrifugal force Abkippmoment arises on the shoes 105.
  • the shoe 105 is - as in the FIG. 5 is illustrated - arranged with a diameter clearance DS1 in the recess 111 of the drive flange 103 and in the region in which the support point A is arranged, provided with a diameter extension.
  • FIGS. 5 to 7 is the area of FIGS. 1 to 4 , in which the support point A and thus the plane EE is arranged, shown in an enlarged view.
  • the radial outer surface of the diameter extension of the shoe 105 which is disposed within the recess 111, formed as a spherical surface SF, whose center MP lies in the center of gravity SP of the shoe 105.
  • the spherical partial surface SF an articulated mounting of the shoe 105 is achieved in the recess 111, which further ensures a good tilt compensation of the shoe 105.
  • FIGS. 6 and 7 Alternative embodiments are shown, which can be used in the axial piston machine 1 according to the invention.
  • FIG. 6 is the radial outer surface of the diameter extension of the shoe 105 in the region of the plane EE and thus formed in the region of the support point A as a cylindrical surface ZF, whose lateral surface is concentric with the longitudinal axis of the shoe 105.
  • a diameter clearance DS2 is formed between the cylindrical surface ZF and the recess 111 of the drive flange 3. The diameter clearance DS2 is less than the diameter clearance DS1 at the remaining portions of the shoe 105.
  • the annular surface RF designed as an annular partial surface has a radius R whose root point is arranged on the plane EE and is radially spaced from the center of gravity SP of the sliding shoe 105.
  • FIG. 8 a further embodiment of an axial piston machine 1 according to the invention is shown in a bent-axis design, wherein the same components are provided with the same reference numerals.
  • the sliding shoes 105 are each such longitudinally displaceable and articulated in the drive flange 103, that with a rotating drive flange 103, a compensating force F FR acts on the shoe 105, which is directed opposite to the force acting on the shoe 103 centrifugal force F F , wherein the point AP of the balancing force F FR on the shoe 105 is selected such that on the shoe 105, a centrifugal force-dependent Abkippmoment is partially or completely compensated.
  • the sliding shoe 105 is in each case operatively connected to an additional compensation body 200 which partially or completely compensates for a tilting moment arising on the sliding shoe 105 from the centrifugal force F F.
  • the compensation body 200 generates the force acting on the shoe 105 compensating force F FR , which is opposite to the centrifugal force F F on the shoe 105.
  • the attack point AP of the compensating body 200 generated and acting on the shoe 105 compensating force F FR is located in the center of gravity SP of the shoe 105th
  • the radial support point A of the shoe 105 in the recess 111 of the drive flange 3 is spaced in the axial direction of the center of gravity SP of the shoe 105 to a first lever arm c.
  • the compensation body 200 is articulated to the drive flange 103 by means of a hinge connection 210 and is in operative connection with the slide shoe 105 in the center of gravity SP.
  • the compensating force F FR is generated by the centrifugal force F F2 acting on the compensating body 200.
  • the balancing body 200 is disposed coaxially with the slide shoe 105 and within the radial dimensions of the slide shoe 105 in the drive flange 3 longitudinally displaceable and articulated.
  • the drive flange 3 is for this purpose provided with a further recess 211, in which the compensating body 200 is mounted longitudinally displaceable and articulated.
  • the further recess 211 is arranged coaxially with the recess 111 for the sliding shoe 105 and has a reduced diameter relative to the recess 111.
  • the further recess 211 is connected via the connecting channel 107 in the drive flange 3 and the connecting channel 108 in the piston 10 with the displacer V in operative connection.
  • the balancing body 200 is provided with a connecting channel 212, by means of which the pressure pocket 106 of the shoe 105 is in communication with the displacement chamber V.
  • the connection of the compensation body 200 with the shoe 105 is carried out in the illustrated embodiment by a ball joint 220, whose center MMP is arranged in the center of gravity SP of the shoe 105.
  • the ball joint 220 is formed in the illustrated embodiment by a ball head on a pin-shaped portion of the compensation body 200 and a spherical cap-shaped recess in the shoe 105.
  • compensating body 200 in the recess 211 of the balancing body is arranged with a diameter clearance DS3 in the recess 211 and the hinge joint 210 formed by a diameter extension of the compensating body 200.
  • the radial outer surface of the compensating body 200 in the region of the diameter enlargement as an annular surface analogous to the FIG. 7 educated. It is understood that the radial outer surface of the compensation body 200 in the region of the diameter extension alternatively analogous to the Figures 5 and 6 can be executed.
  • the hinge 210 forms a radial support point B, with which the balancing body 200 is supported in the recess 211.
  • the articulated connection 210 and thus the support point B of the compensation body 200 on the drive flange 3 is arranged in the axial direction between the center of gravity SP of the slide shoe 105 and the center of gravity SK of the compensation body 200.
  • the center of gravity SK of the compensation body 200 is spaced from the articulation 210 and thus from the support point B about the lever arm a.
  • the spring device 110 is arranged in the recess 211 and acts on the compensation body 200, which is in operative connection with the sliding shoe 105.
  • the spring device 110 can be arranged in the recess 111 and act directly on the slide shoe 105.
  • the pressure chamber D acting on the sliding shoe 105 is arranged between the sliding shoe 105, the recess 111 and the compensating body 200.
  • at least one recess 215 is formed in the region of the articulated connection 210 of the compensation body 200.
  • the pressure chamber D is thus connected via the recess 215, and the diameter clearance DS3 of the compensating body 200 with the connecting channel 107 in connection.
  • the shoe 105 is the FIG. 8 analogous to the FIG. 7 provided with a cylindrical outer surface, wherein the Kippein suitkeit by a corresponding diameter clearance is achieved. Between the cylindrical outer surface of the shoe 105 and the recess, a relatively short guide length is formed, so that in conjunction with a correspondingly dimensioned diameter clearance the required Kippein monokeit the shoe 105 is made possible.
  • the articulated mounting of the sliding shoes 105 in the recess 111 of the drive flange analogous to Figures 5 and 6 respectively.
  • the compensating force F FR is generated by the radially outward centrifugal force F F2 of the compensating body 200, which arises from the mass m 2 of the compensating body 200 and acts on the center of gravity SK of the compensating body 200, in conjunction with the achieved by the choice of Abstweiluss B deflection Force direction radially inward.
  • the mass m 2 of the compensating body 200, the first lever arm c and the second lever arm a are designed such that the compensating force F FR generated by the compensating body 200 has substantially the same size as the centrifugal force F F acting on the sliding block 105.
  • the additional compensation body 200 by means of the additional compensation body 200, the tilting moment of the sliding shoes 105 can be compensated and tilting of the sliding shoes 105 from the housing-side sliding surface 101 at high rotational speeds can be prevented.
  • FIGS. 1 to 7 is achieved by the position of the support point A in the going through the center of gravity SP level EE that on the shoe 105 no Abkippmoment arises.
  • the plane EE in which the support point A is arranged, may be slightly spaced in the axial direction of the center of gravity SP, so that only a partial compensation of the Abkippmoments done.
  • This position of the plane EE creates a small lever arm in the axial direction between the force pair formed by the centrifugal force F F and the compensating force F FR , which can be tolerated with appropriate dimensioning of the pressing force of the spring 110 and the hydrostatic discharge.
  • the choice of the hydrostatic relief by the sliding shoes 105 can be selected such that the hydrostatic discharge force F E of the axial force F A corresponds, so that the axial force F A is exactly compensated.
  • This design can be realized in an axial piston machine designed as a constant machine with a constant displacement volume.
  • the hydrostatic relief force F E can be dimensioned smaller than the axial force F A , so that the remaining difference of the axial force from these two forces is absorbed by the drive flange side bearing device 5a.
  • the hydrostatic discharge force F E can be dimensioned greater than the axial force F A in the amount, so that the remaining difference amount of the axial force from these two forces is absorbed by the cylinder drum side bearing device 5b.
  • the axial piston machine 1 can, instead of being a constant machine, alternatively be designed as an adjusting machine with a variable displacer volume.
  • a variable displacer volume In an adjustment of the inclination angle ⁇ and thus the pivot angle of the rotation axis R z of the cylinder drum 7 with respect to the axis of rotation R t of the drive shaft 4 is adjustable to change the displacer volume.
  • the control surface 15 against which the cylinder drum 7 rests is formed for this purpose on a cradle body which is pivotably mounted in the housing 2 about a pivot axis which lies at the intersection S of the axis of rotation R t of the drive shaft 4 and the axis of rotation R z of the cylinder drum 7 and perpendicular to the rotation axes R t and R z is arranged.
  • the angle of inclination and thus the pivot angle ⁇ of the rotation axis R z of the cylinder drum 7 to the rotation axis R t of the drive shaft changes 4.
  • the cylinder drum 7 can be pivoted to a zero position in which the axis of rotation R z of the cylinder drum 7 coaxial with Rotation axis R t of the drive shaft 4 is. Starting from this zero position, the cylinder drum 7 can be pivoted to one or both sides, so that the axial piston of the FIG. 5 can be executed as unilaterally pivotable or as two-sided pivotable adjusting.
  • driver element 40 can be integrally formed on the cylinder drum 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP15160552.4A 2014-04-08 2015-03-24 Machine à piston axial dans une construction à axe oblique avec patins de guidage dans le plateau d'entraînement Withdrawn EP2930360A3 (fr)

Applications Claiming Priority (1)

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DE102014104952.7A DE102014104952A1 (de) 2014-04-08 2014-04-08 Axialkolbenmaschine in Schrägachsenbauweise mit Gleitschuhen im Triebflansch

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EP2930360A2 true EP2930360A2 (fr) 2015-10-14
EP2930360A3 EP2930360A3 (fr) 2015-11-04

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US (1) US10001010B2 (fr)
EP (1) EP2930360A3 (fr)
JP (1) JP6611453B2 (fr)
CN (1) CN104976089B (fr)
DE (1) DE102014104952A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH716310A1 (de) * 2019-06-12 2020-12-15 Urben & Kyburz Ag Bauteil einer Kolbenmaschine und Verfahren zur Herstellung des Bauteils.

Citations (5)

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US3198130A (en) 1962-04-06 1965-08-03 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3827337A (en) 1971-04-28 1974-08-06 Renault Hydrostatic bearings for the swash plate of a barrel-cylinder hydraulic pump or motor
US4546692A (en) 1982-10-22 1985-10-15 Hydromatik Gmbh Radial bearing for drive plate of inclined-axis type axial piston machine
US4872394A (en) 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
DE10154921A1 (de) 2001-11-08 2003-05-15 Linde Ag Hydrostatische Axialkolbenmaschine in Triebflanschbauweise

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JPS5761184U (fr) * 1980-09-30 1982-04-10
JPH0313589Y2 (fr) * 1985-07-31 1991-03-27
DD253059A1 (de) * 1986-09-29 1988-01-06 Karl Marx Stadt Ind Werke Hydrostatische axialkolbenmaschine
JP2963218B2 (ja) * 1991-01-28 1999-10-18 本田技研工業株式会社 斜板プランジャ式油圧装置
JP2000009025A (ja) * 1998-06-19 2000-01-11 Honda Motor Co Ltd アキシャルプランジャ型油圧機器におけるプランジャアッセンブリ
DE102007049393A1 (de) * 2007-10-15 2009-04-16 Linde Material Handling Gmbh Axialkolbenmaschine
DE102011053645A1 (de) * 2011-09-15 2013-03-21 Linde Material Handling Gmbh Axialkolbenmaschine mit einem druckmittelgefüllten Gehäuse

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Publication number Priority date Publication date Assignee Title
US3198130A (en) 1962-04-06 1965-08-03 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3827337A (en) 1971-04-28 1974-08-06 Renault Hydrostatic bearings for the swash plate of a barrel-cylinder hydraulic pump or motor
US4546692A (en) 1982-10-22 1985-10-15 Hydromatik Gmbh Radial bearing for drive plate of inclined-axis type axial piston machine
US4872394A (en) 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
DE10154921A1 (de) 2001-11-08 2003-05-15 Linde Ag Hydrostatische Axialkolbenmaschine in Triebflanschbauweise

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH716310A1 (de) * 2019-06-12 2020-12-15 Urben & Kyburz Ag Bauteil einer Kolbenmaschine und Verfahren zur Herstellung des Bauteils.
WO2020249682A1 (fr) * 2019-06-12 2020-12-17 Urben & Kyburz Ag Élément d'une machine à pistons et procédé pour fabriquer l'élément

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DE102014104952A1 (de) 2015-10-08
US10001010B2 (en) 2018-06-19
EP2930360A3 (fr) 2015-11-04
CN104976089A (zh) 2015-10-14
JP2015200318A (ja) 2015-11-12
CN104976089B (zh) 2019-06-11
US20150285076A1 (en) 2015-10-08
JP6611453B2 (ja) 2019-11-27

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