EP2937567A2 - Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un élément articulé d'entraînement destiné à l'entraînement d'un tambour cylindrique - Google Patents

Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un élément articulé d'entraînement destiné à l'entraînement d'un tambour cylindrique Download PDF

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Publication number
EP2937567A2
EP2937567A2 EP15160441.0A EP15160441A EP2937567A2 EP 2937567 A2 EP2937567 A2 EP 2937567A2 EP 15160441 A EP15160441 A EP 15160441A EP 2937567 A2 EP2937567 A2 EP 2937567A2
Authority
EP
European Patent Office
Prior art keywords
drive shaft
axial piston
piston machine
cylinder drum
lubricant
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
EP15160441.0A
Other languages
German (de)
English (en)
Other versions
EP2937567B1 (fr
EP2937567A3 (fr
Inventor
Martin Bergmann
Sabine Kausch
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 EP2937567A2 publication Critical patent/EP2937567A2/fr
Publication of EP2937567A3 publication Critical patent/EP2937567A3/fr
Application granted granted Critical
Publication of EP2937567B1 publication Critical patent/EP2937567B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01B3/0032—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
    • 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
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/109—Lubrication

Definitions

  • the invention relates to a hydrostatic axial piston machine in oblique-axis construction with a about a rotation axis rotatably disposed within a housing drive shaft, which is provided with a drive flange, and about a rotation axis rotatably disposed within the housing of the axial piston cylinder cylinder, wherein the cylinder drum is provided with a plurality Kolbenaus foundedungen in each of which a piston is arranged to be longitudinally displaceable, wherein the pistons are articulatedly secured to the drive flange, and wherein between the drive shaft and the cylinder drum, a follower joint for entrainment of the cylinder drum is arranged, wherein the follower joint has at least one designed as sliding body or as a rolling body entrainment body, which is supported in the drive shaft and the cylinder drum.
  • 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.
  • axial piston machines in Schrägachsenbauweise principle takes place in a rotation no entrainment of the cylinder drum with the piston arranged therein.
  • a follower joint is required, which is arranged between the drive shaft and the cylinder drum.
  • the housing within which the rotating drive shaft and the rotating cylinder drum are arranged, is generally filled with pressure medium, for example hydraulic oil, in order to ensure cooling and lubrication of the components.
  • pressure medium for example hydraulic oil
  • these churning losses represent an additional energy consumption, which must be provided by the drive as unwanted power loss in an axial piston machine designed as a pump or is not available as output power in an axial piston machine designed as a motor.
  • this power loss can take on a considerable size, which in Axialkolbenmaschinen the performance and operational capability are limited to high speeds out and limited.
  • the present invention has for its object to provide a generic axial piston machine is available, which is operable with a pressure-fluid-depleted housing and at the same time has sufficient lubrication and cooling of the driving body of the follower joint.
  • This object is achieved in that a lubricating device is provided for the driving pin, by means of the driving body lubricant for cooling and lubrication of the driving body of a arranged on the housing of the axial piston lubricant supply can be supplied is.
  • the driving body of the driving joint can be supplied with lubricant, for example hydraulic oil, which is supplied via a lubricant connection to the housing of the axial piston machine in a simple manner and with low construction costs, so that during operation of the axial piston machine with a pressure-fluid-exhausted housing for the operation of the machine, in particular at high speeds, sufficient cooling and lubrication of the driving body of the driving joint is made possible by the lubricant supplied via the lubricating device.
  • lubricant for example hydraulic oil
  • a supply of the driving body of the driving joint with lubricant, which is supplied via the lubricant connection to the housing, can be ensured with low construction costs, if according to an advantageous embodiment of the invention, the lubricating device is arranged in the drive shaft and has a arranged in the drive shaft lubricant channel.
  • lubricant can be guided from the lubricant connection on the housing to the driving bodies of the driving joint in a simple manner via a lubricant channel arranged in the drive shaft.
  • the lubricant passage has a lubricant supply hole arranged in the drive shaft, which is connected to the lubricant port, and at least one arranged in the drive shaft lubrication hole which is connected to the Schierstoffmakerssbohrung and which extends to the peripheral surface of the drive shaft and in the Peripheral surface is provided with an opening, wherein the opening of the lubrication hole in the peripheral surface is arranged such that upon rotation of the drive shaft via the lubricant supply bore and the lubrication hole supplied lubricant flows through the centrifugal force occurring on the driving body.
  • a lubricant supply hole is introduced in the drive shaft of the axial piston machine.
  • a transverse bore is connected as a lubricating hole for each driving body, which is arranged in the drive shaft and which is provided on the outer circumference of the drive shaft with an opening through which the lubricant supplied via the lubricant supply bore lubricant and directly to the associated driving body of the driving joint can flow.
  • a lubricant supply bore and corresponding lubrication holes designed as transverse bores can be produced in the drive shaft of the axial piston machine with low construction costs.
  • the driving body is received in a bed of the drive shaft and in a bedding of the cylinder drum.
  • a targeted supply of the lubricant to the driving body in the region of the two bedding is possible.
  • the lubrication hole is directed to the driving body.
  • the lubricant supplied via the lubricant supply bore and the lubrication bore flows directly onto the driver bodies through the centrifugal force, so that the driver bodies are targeted by lubricant and can be specifically cooled and lubricated with a small amount of lubricant.
  • the driving torque to be transmitted between the drive shaft and the cylinder drum for driving the cylinder drum it may be sufficient for small driving torques to be transmitted to provide a single driving body.
  • the number of driving bodies can be increased. If a plurality of distributed over the circumference arranged driving body is provided over the circumference, a lubricating hole is advantageously provided for each driving body. As a result, it is achieved in a simple manner that lubricant can flow to each driving body via the associated lubrication hole for cooling and lubrication, so that the several driving bodies of the driving joint can be reliably cooled and lubricated with a small amount of lubricant.
  • the lubricant supply bore is formed as a coaxial with the axis of rotation of the drive shaft arranged longitudinal bore in the drive shaft.
  • a coaxial and thus formed as a central bore in the drive shaft longitudinal bore can be made with low construction costs.
  • the lubricant supply bore extends to a bearing device, by means of which the drive shaft is rotatably mounted in the housing.
  • the drive shaft is mounted in the housing on both sides of the cylinder drum
  • the bearing of the drive shaft in the housing comprises a drive flange side bearing device and a cylinder drum side bearing means, wherein the lubricant supply bore extends to the cylinder drum side bearing means.
  • the arrangement of the lubricant channel in the cylinder drum-side region of the drive shaft thus results in advantages, since the drive shaft is not weakened by the lubricant supply bore and the lubrication holes with respect to the transmission of the drive or output torque and must be increased in diameter.
  • the lubricant supply bore is provided in the region of the bearing device with a feed opening, which is connected to the lubricant connection arranged on the housing of the axial piston machine.
  • a feed opening can easily with the lubricant supply hole connected to the housing of the axial piston engine arranged lubricant port to supply the lubricating device with lubricant.
  • the feed opening is formed on an axial end face of the drive shaft.
  • a lubricant space is formed between the bearing device, the end face of the drive shaft and the housing, which is in communication with the lubricant connection.
  • each driving body is designed as a driving body pair with two half-bodies, which are arranged alternately in the drive shaft and the cylinder drum and abut each other by means of contact surfaces.
  • the driving body pair in this case has in each case one belonging to the cylinder drum cylindrical side half body and belonging to the drive shaft drive shaft side half body, wherein the cylinder drum side half body of Mit Spotify emotionspress is taken in a bedding of the cylinder drum and the drive shaft side half body of Mit SpotifySystems in a ballast of the drive shaft.
  • the half-bodies in the area of the contact surfaces and / or in the area of the bedding lubricant can be supplied.
  • the half-bodies of the driving body pair can thus be cooled and lubricated with the lubrication device according to the invention in a simple manner on the contact surfaces as well as on the surfaces with which the half-bodies are arranged in the beddings.
  • the driving pin is formed as a rotationally synchronous driving joint for rotationally synchronous rotation of the cylinder drum and the drive shaft.
  • a rotationally synchronous entrainment of the cylinder drum a uniform drive or output torque is achieved on the drive shaft and it can be the component loads of the axial piston machine can be reduced.
  • the noises of the axial piston machine and of a drive train coupled to the axial piston machine are reduced with a rotationally synchronous driving joint.
  • the follower joint is designed as a cone beam half-roll joint, which has at least one pair of rollers as Mit SpotifyAvem with two semi-cylindrical half-rollers as a half body, wherein the semi-cylindrical half-rollers are flattened to a rotational axis and the half-rollers on the flattened sides planar sliding surfaces as Ber## lake form, at which the half rollers of the roller pair abut to form a surface contact.
  • Such a cone-beam half-roll joint between the drive shaft and the cylinder drum can be performed in a simple manner by appropriate geometric design as homokinetic constant velocity joint, in which an exact and uniform and thus rotationally synchronous entrainment of the cylinder drum.
  • the drive shaft through the cylinder drum or the axial piston machine are passed in the axial direction to store the drive shaft on both sides of the cylinder drum can.
  • the half rolls of each pair of rolls are arranged in pairs.
  • the half-rollers of a pair of rollers of the conical-beam half-roller joint are essentially formed up to the axis of rotation and thus flattened to the longitudinal axis of the cylindrical bodies.
  • By flattening arise on the flattened sides of the half-rollers flat sliding surfaces as contact surfaces against which the two half-rollers of a pair of rollers abut each other and where the force is transmitted over a surface contact between the flat surfaces.
  • pairs of rollers each of consist of two semi-cylindrical half rollers whose half rollers are flattened to a rotational axis and thus the longitudinal axis of the half rollers and which lie against each other on the flattened sides to form a surface contact and flat sliding surfaces, the forces and thus the torque to take the cylinder drum with low construction costs be transferred, since the half rollers are simple and inexpensive to produce.
  • the fact that the contact surfaces between the two half rollers of a pair of rollers are formed as flat sliding surfaces and a surface contact between the two half rollers of a pair of rollers for power transmission occurs, even at high forces to be transferred when taking the cylinder drum low Hertzian pressure.
  • the cone beam half-roll joint formed by corresponding pairs of rolls is therefore still robust against overload, which can arise, for example, by a high rotational acceleration.
  • the axial piston machine according to the invention as a hydraulic motor
  • the axial piston machine according to the invention can thus also be used in applications with high rotational accelerations.
  • the lubrication device according to the invention in this case the lubricant for cooling and lubrication can be supplied to the two half-rollers in the area of the contact surfaces formed as a flat sliding surfaces during operation of the axial piston machine with a pressure-medium-empty housing.
  • the driving body in particular the half rollers, is arranged in the radial direction within the piston and spaced from the axes of rotation of the drive shaft and the cylinder drum.
  • the preferred trained as a cone beam half-roll joint follower joint is thus disposed within the ring and the pitch circle of the pistons, whereby a space-saving design of the axial piston is achievable and targeted lubricant lubricant can be supplied to the driving bodies by the centrifugal force effect for cooling and lubrication on the formed in the drive shaft lubricant channel .
  • the driving body for example, half rolls of the pairs of rollers, perpendicular to the axis of rotation of the drive shaft and the axis of rotation of the cylinder drum, so that at the contact surfaces formed by the flat sliding surfaces and thus the contact surfaces, the torque can be transmitted to take the cylinder drum.
  • This arrangement of the driving body of the Mit varieties of the Mit varieties, in particular the half-rollers of the cone beam half-roll joint, also makes it possible in a simple manner to provide the follower joint with a concentric with the axis of rotation of the cylinder drum longitudinal recess to pass the drive shaft through the cylinder drum for two-sided storage and arranged the driving body by means of a drive shaft Lubricant channel to supply by the centrifugal force effect with lubricant for cooling and lubrication.
  • each pair of rollers to the cylinder drum belonging cylinder drum side half roller and belonging to the drive shaft drive shaft side half roller wherein the cylinder drum side half roller of a pair of rollers in a cylindrical, in particular partially cylindrical, cylinder drum side recording as bedding and the drive shaft side half roller of a pair of rollers in a cylindrical, in particular part-cylindrical, drive shaft side recording is taken as a bedding.
  • the forces and torque for driving the cylinder drum can be transmitted in a simple manner.
  • the cylindrical receptacles in which the corresponding half-roll is received and bedded can be prepared in a simple manner and with little manufacturing effort, which causes in conjunction with the simple and inexpensive to produce half-rolls the follower joint for the entrainment of the cylinder drum low production costs.
  • the two half-rollers can also be supplied with lubricant for cooling and lubrication in the area of the bedding in the drive shaft and the cylinder drum during operation of the axial piston machine with a pressure-medium-empty housing.
  • the axial piston machine according to the invention can be operated only in one direction of rotation, it being sufficient to provide for this direction of rotation one or more driving bodies, which allow a transmission of a driving torque in the desired direction of rotation between the drive shaft and the cylinder drum.
  • the axial piston machine is operable in both directions of rotation, wherein for each Direction of rotation in each case at least one driving body is provided for rotationally synchronous entrainment of the cylinder drum.
  • the axial piston machine according to the invention can be designed as a constant machine with a fixed displacement volume.
  • the hydrostatic axial piston machine 1 designed as a bent axis machine according to FIGS FIGS. 1 to 3 has a housing 2, which consists of a housing pot 2a and a housing cover 2b.
  • 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.
  • 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 V formed by the KolbenausEnglishept 8 and the piston 10 Verdrängerlor on a control surface 15, which is provided with not shown kidney-shaped control recesses, the 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 FIG. 1 is designed as an adjusting machine with a variable displacer volume.
  • the control surface 15 against which the cylinder drum 7 rests is formed for this purpose on a weighing body 100 which is pivotably arranged in the housing 2 about a pivot axis which lies at the intersection point S of the rotation axis R t of the drive shaft 4 and the rotation axis R z of the cylinder drum 7 and perpendicular to the axes of rotation R t and R z is arranged.
  • the inclination angle ⁇ of the rotation axis R z of the cylinder drum 7 changes to the rotation axis R t of the drive shaft 4.
  • the cylinder drum 7 can be pivoted to a zero position in which the rotation axis R z of the cylinder drum 7 coaxial with the axis of rotation R t 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. 1 can be executed as unilaterally pivotable or as two-sided pivotable adjusting.
  • a device for pivoting the weighing body 100 and thus the cylinder drum 7 is in the FIG. 1 not shown in detail.
  • 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.
  • Piston recess 8 is arranged.
  • 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 joint 30 is arranged between the drive shaft 4 and the cylinder drum 7, which couples the drive shaft 4 and the cylinder drum 7 in the direction of rotation.
  • the entrainment joint 30 has at least one driving body M1-M4 designed as a sliding body, which is supported in the drive shaft 4 and the cylinder drum 7.
  • Each driving body M1-M4 is for this purpose -as in connection with the FIG. 3 is shown in detail -in each case in a bedding B1 of the drive shaft 4 and a bed B2 of the cylinder drum 7 is added.
  • the driving body M1-M4 are in the illustrated embodiment in each case as driving body pair P1-P4 with two half-bodies M1 a, M1b - M4a, M4b is formed, which are arranged alternately in the drive shaft 4 and the cylinder drum 7 and abut by means of contact surfaces BF.
  • Each driving body pair P1-P4 has a cylindrical drum-side half body M1a, M2a, M3a, M4a belonging to the cylinder drum 7 and a drive shaft-side half body M1b, M2b, M3b, M4b belonging to the drive shaft 4, wherein the cylindrical drum-side half body M1a, M2a, M3a, M4a of Mit Cyprus stresses P1-P4 in the bed B2 of the cylinder drum 7 and the drive shaft side half-body M 1 b, M2b, M3b, M4b of Mitddling stresses P1-P4 in the bedding B1 of the drive shaft 3 is added.
  • the driving joint 30 is formed in the illustrated embodiment as a constant velocity joint, which allows a rotationally synchronous entrainment of the cylinder drum 7 with the drive shaft 4, so that there is a uniform, synchronous rotation of the cylinder drum 7 with the drive shaft 4.
  • 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, 52, 53 as driving body pair P1, P2, P3, P4, 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 sleeve-shaped driver element 40 is arranged in the central longitudinal recess 11 of the cylinder drum 7.
  • the driver element 40 is secured to the cylinder drum 7 in the longitudinal direction of the cylinder drum 7 in the axial direction and in the circumferential direction.
  • the driver element 40 rests with an end face against a diameter shoulder 11a of the longitudinal recess 11.
  • the rotation is effected by means of a securing means 45, which is formed in the illustrated embodiment by a arranged between the sleeve-shaped driver element 40 and the cylinder drum 7 connecting pin.
  • the drive shaft 4 guided through the axial piston machine 1 also extends through the sleeve-shaped driver element 40.
  • the inner diameter of the sleeve-shaped driver element 40 is provided with a contour aligned with the longitudinal recess 11 of the cylinder drum 7.
  • Each of the plurality of roller pairs 50-53 of the cone-beam half-roller joint 31 consists of two and thus a pair of semi-cylindrical half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b as half bodies M1a, M1b, M2a, M2b, M3a , M3b, M4a, M4b.
  • the semi-cylindrical half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b are each flattened from a substantially to an axis of rotation RR t , RR z cylindrical body formed.
  • the pairs of half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b form planar sliding surfaces GF as contact surfaces BF, on which the two half rollers 50a, 50b, 51a, 51b, 52a , 52b, 53a, 53b of a pair of rollers 50, 51, 52, 53 abut each other to form a surface contact.
  • the half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b and thus the half bodies M1a, M1b, M2a, M2b, M3a, M3b, M4a, M4b are radially spaced within the pitch circle of the pistons 10 and from the axes of rotation R t , R z arranged.
  • 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 50-53 has a cylindrical drum-side half-roller 50a, 51a, 52a, 53a belonging to the cylinder drum 7 and a drive shaft 4 belonging to the drive shaft side half-roller 50b, 51b, 52b, 53b, which abut the flat sliding surfaces GF and each other stay in contact.
  • the cylindrical drum-side half roller 50a, 51a, 52a, 53a of the respective roller pair 50-53 are each in a cylindrical, in particular partially cylindrical, cylinder drum side receptacle 55a, 56a, 57a, 58a as bedding B2 and the drive shaft side half roller 50b, 51b, 52b, 53b a pair of rollers 50-53 in a cylindrical, in particular part-cylindrical, drive shaft side receiving 55b, 56b, 57b, 58b taken as bedding B1.
  • the half rollers 50a, 51a, 52a, 53a, 50b, 51b, 52b, 53b are secured in the respective cylindrical receptacle 55a, 56a, 57a, 58a, 55b, 56b, 57b, 58b in the longitudinal direction of the corresponding axis of rotation.
  • each half-rollers 50a, 51a, 52a, 53a, 50b, 51b, 52b, 53b are provided in the cylindrical portion with a collar 60 which in a groove 61 of the corresponding receptacle 55a, 56a, 57a, 58a, 55b, 56b , 57b, 58b.
  • the individual rotation axes RR t of the plurality of drive shaft-side half rollers 50b, 51b, 52b, 53b thus form a cone beam about the rotation axis R t of the drive shaft 4 with the point at the intersection S t .
  • the rotational axes RR z of the cylinder-drum-side half rollers 50a, 51a, 52a, 53a are inclined to the rotation axis R z of the cylinder drum 7 by an inclination angle ⁇ .
  • the rotation axes RR z of the cylindrical drum-side half rollers 50a, 51a, 52a, 53a intersect the rotation axis 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, 52a, 53a thus form a cone beam about the rotation axis R z of the cylinder drum 7 with the point at the point of intersection S z .
  • the inclination angles ⁇ of the rotation axes RR z of the cylinder drum side half rollers 50a, 51a, 52a, 53a 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, 52b, 53b to the rotation axis R t of the drive shaft 4 are in magnitude identical.
  • 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 thus inclined at half the inclination angle or swivel angle a / 2 with respect to a perpendicular to the axis of rotation R t of the drive shaft 4 plane E1 and a plane perpendicular to the axis of rotation R z of the cylinder drum 7 plane E2.
  • the plane E passes through the intersection S of the axes of rotation R t , R z .
  • the half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b of the respective roller pair 50, 51, 52, 53 are arranged in the region of the points of intersection SP of the axes of rotation RR t , RR z , whereby at the points of intersection SP two half rollers of the respective roller pair 50-53, the power transmission between the flat sliding surfaces GF takes place for driving the cylinder drum 7.
  • each paired half rollers 50a, 50b, 51a, 51b, 52a, 52b, 53a, 53b to each other can be rotated by the corresponding receptacles 55a, 56a, 57a, 58a, 55b, 56b, 57b, 58b align the flat surfaces and thus the sliding surfaces GF of the juxtaposed half rollers to each other.
  • the in the FIGS. 1 to 3 illustrated axial piston machine 1 is operable in both directions of rotation.
  • at least one driving body M1-M4 or pair of rollers 50-53 is provided for each direction of rotation and thus torque direction of the driving torque for the entrainment of the cylinder drum 7.
  • the driving body M1, M2 and thus the roller pairs 50, 51 serve to entrain the cylinder drum 7 in a rotation of the drive shaft 4 in the counterclockwise direction.
  • 51 forces are transmitted to the flat sliding surfaces GF of the half rollers 50a, 50b and 51 a, which generate a driving torque for driving the cylinder drum 7.
  • the driving body M3, M4 and thus the pairs of rollers 52, 53 serve to entrain the cylinder drum 7 in an opposite rotation of the drive shaft 4 in a clockwise direction.
  • forces are transmitted to the flat sliding surfaces GF of the half rollers 52a, 52b and 53a, 53b of the roller pairs 52, 53, which generate a driving torque for driving the cylinder drum 7.
  • two pairs of rollers 50, 51 and 52, 53 and thus two driving body M1, M2 or M3, M4 are provided for each rotational direction, wherein the driving body M1, M2 or pairs of rollers 50, 51 for the first direction of rotation and the driving body M3, M4 or roller pairs 52, 53 are distributed uniformly over the circumference for the second direction of rotation.
  • a radial force balance can be achieved.
  • the pairs of rollers 50, 51 are arranged offset by a rotation angle of 180 ° and the pairs of rollers 52, 53 offset by a rotation angle of 180 °.
  • the roller pairs 50, 51 for the first direction of rotation are offset from the pairs of rollers 52, 53 for the second direction of rotation by a rotation angle of 90 °.
  • the drive shaft 4 is provided for this purpose with a pocket-shaped recess 70, 71, 72, 73, on whose side surfaces in each case a drive shaft-side receptacle 55b, 56b, 57b, 58b and thus a bedding B1 is formed.
  • the sleeve-shaped driver element 40 is provided for this purpose with finger-shaped elevations 41, 42, 43, 44 which extend in the direction of the drive shaft 4 and in which in each case a cylindrical drum-side receptacle 55a, 56a, 57, 58a and thus a bedding B2 is formed.
  • the sleeve-shaped driver element 40 is further provided with the hollow spherical portion 27 of the spherical guide 25.
  • Each finger-shaped elevation 41, 42, 43, 44 of the driver element 40 engages in an associated pocket-shaped recess 70, 71, 72, 73 of the drive shaft 4 a.
  • the axial piston machine 1 is designed for operation with a pressure-medium-exhausted housing 2.
  • Such an operation means an operation of the axial piston machine 1 in which a low pressure medium level is formed in the housing 2 such that the rotating engine components do not or only slightly dip into pressure medium in order to avoid splashing losses of the rotating engine components during operation of the axial piston machine ,
  • a lubricating device 80 is provided for the driving joint 30, by means of the respective driving bodies M1-M4 lubricant, for example hydraulic oil, for cooling and lubrication of the corresponding Mit Spotify stresses M1-M4 of a arranged on the housing 2 of the axial piston machine 1 lubricant port 81 can be fed.
  • lubricant for example hydraulic oil
  • the lubrication device 80 is arranged in the drive shaft 4 and has a lubricant channel 82 arranged in the drive shaft 4.
  • the lubricant passage 81 is formed by a lubricant supply hole 83 arranged in the drive shaft 4, which is connected to the lubricant port 81. Furthermore, the lubricant channel 81 for each driving body M1-M4 of Mit Spotifygelenk 30 on a arranged in the drive shaft 4 lubrication hole 84-87.
  • the lubrication holes 84-87 are respectively connected to the lubricant supply bore 83 and extend to the peripheral surface of the drive shaft 4. In the peripheral surface of the drive shaft 4, the lubrication holes 84-87 are each provided with an opening 90-93.
  • the opening 90-93 of the lubricating hole 84-87 are in the illustrated embodiment in the pocket-shaped recess 70, 71, 72, 73 disposed in the peripheral surface of the drive shaft 4 arranged such that upon rotation of the drive shaft 4 via the lubricant supply hole 93 and the lubrication holes 84th Supplied lubricant flows through the centrifugal force occurring on the associated driving body M 1-M4.
  • the lubrication holes 84-87 are arranged inclined in the illustrated embodiment, each in drive shaft 4 and inclined with the opening 90-93 in the direction of the cylinder drum 7, so that the lubrication holes 84-87 introduced from radially outside, for example by drilling, in the drive shaft 4 can be.
  • the lubrication holes 84-87 can thus be easily made in the drive shaft 4, in which the lubricant supply hole 93 is drilled from radially outward at a desired angle to the bedding B1 of the drive shaft 4 over.
  • the inclination angle of the lubrication holes 84-87 is preferably selected such that the lubrication holes 84-87 with its longitudinal axis - as in the FIG. 2 is apparent - are directed to the axial center region of the drive shaft side half body M1 b, M2b, M3b, M4b.
  • the drive shaft side half body M1 b, M2b, M3b, M4b as a semi-cylindrical half roller 50b, 51b, 52b, 53b thus the lubrication holes 84-87 are seen with its longitudinal axis - in the axial longitudinal direction of the half roller 50b, 51b, 52b, 53b - Aligned to the axial center area.
  • the lubrication holes 84-87 and their openings 90-93 are thus directed respectively to the associated follower body M1-M4.
  • the lubricant exiting through the centrifugal force from the opening 90-93 thus flows directly to the associated driving body M1-M4.
  • the contact surfaces BF of the two half bodies M1a, M1b - M4a, M4b of the respective driving body pair P1-P4 and the surfaces with which the half bodies M1a, M1b - M4a, M4b are arranged in the bedding B1, B2, thus become from the opening 90-93 exiting directly by the centrifugal force lubricant, so that with a small amount of lubricant safe cooling and lubrication of the driving body M1-M4 is achieved.
  • the lubricant supply bore 83 is formed in the illustrated embodiment as a coaxial with the axis of rotation R t of the drive shaft 4 arranged longitudinal bore in the drive shaft 4.
  • the trained as a longitudinal bore lubricant supply hole 83 extends in the illustrated embodiment to the cylinder drum side bearing means 5b.
  • the lubricant supply bore 83 is provided with a supply port 95 which is connected to the lubricant port 81 disposed on the housing 2 of the axial piston engine 1.
  • the feed opening 95 is formed in the illustrated embodiment on the axial end side of the drive shaft 4 and formed by the bore opening of the lubricant supply bore 83.
  • the lubricant supply bore 83 is formed in the illustrated embodiment as a blind bore, which can be introduced from the cylinder drum side end of the drive shaft 4 in the drive shaft 4.
  • a lubricant space 96 is formed which communicates with the lubricant port 81.
  • a cover 97 is arranged, which seals the lubricant chamber 96 to the environment.
  • the lubricant port 81 is formed on the lid 97, which is provided for this purpose, for example with a threaded bore 98, to which a lubricant line is connectable.
  • Cooling and lubrication of the cylinder-drum-side bearing device 5b by means of the lubricant supplied to the lubricant connection 81 is furthermore made possible via the lubricant chamber 96.
  • the lubrication device 80 makes it possible, during operation of the axial piston machine 1 with a pressurized-empty housing 2, to carry the driving body M1-M4 of the driving joint 30 for driving the cylinder drum 7 in a simple manner by means of lubricant supplied to the housing-side lubricant port 81 of the axial piston machine 1 and to lubricate.
  • the cylinder drum side bearing device 5b of the drive shaft 4 can be cooled and lubricated by the lubricant supplied to the housing-side lubricant port 81 of the axial piston machine 1.
  • the axial piston machine 1 By the operation of the axial piston machine 1 with a pressure medium emptied housing 2, the churning losses can be reduced, so that in the use of the axial piston engine according to the invention in a vehicle with an internal combustion engine drive, a fuel economy of the engine can be achieved.
  • the invention is not limited to the illustrated embodiments.
  • the axial piston machine 1 according to the invention can alternatively be designed as a constant machine instead of as an adjusting machine.
  • the inclination angle ⁇ of the rotation axis R z of the cylinder drum 7 with respect to the rotation axis R t of the drive shaft 4 is constant and fixed.
  • the control surface 15 against which the cylinder drum 7 rests can in this case be formed on the housing 2.
  • 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)
  • Details Of Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP15160441.0A 2014-04-08 2015-03-24 Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un élément articulé d'entraînement destiné à l'entraînement d'un tambour cylindrique Active EP2937567B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014104953.5A DE102014104953A1 (de) 2014-04-08 2014-04-08 Hydrostatische Axialkolbenmaschine in Schrägachsenbauweise mit einem Mitnahmegelenk zur Mitnahme der Zylindertrommel

Publications (3)

Publication Number Publication Date
EP2937567A2 true EP2937567A2 (fr) 2015-10-28
EP2937567A3 EP2937567A3 (fr) 2016-03-16
EP2937567B1 EP2937567B1 (fr) 2018-05-09

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EP15160441.0A Active EP2937567B1 (fr) 2014-04-08 2015-03-24 Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un élément articulé d'entraînement destiné à l'entraînement d'un tambour cylindrique

Country Status (5)

Country Link
US (1) US9963967B2 (fr)
EP (1) EP2937567B1 (fr)
JP (1) JP6542014B2 (fr)
CN (1) CN104976090B (fr)
DE (1) DE102014104953A1 (fr)

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EP3000560A1 (fr) * 2014-09-25 2016-03-30 HILTI Aktiengesellschaft Appareil d'enfoncement à ressort à gaz
ITUB20155999A1 (it) * 2015-11-30 2017-05-30 Merlo Group Innovation Lab S R L Macchina idraulica a cilindri flottanti
US20180340501A1 (en) * 2017-05-23 2018-11-29 Weishun Willaim Ni Variable displacement fuel pump with position sensor
EP3477102B1 (fr) * 2017-10-25 2020-12-16 Innas B.V. Dispositif hydraulique
CN113748965B (zh) * 2021-10-20 2024-07-05 王奇 一种水产养殖废水农田调节灌溉处理设备
US20240200541A1 (en) * 2022-12-20 2024-06-20 Hamilton Sundstrand Corporation Cylinder barrel

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Also Published As

Publication number Publication date
JP6542014B2 (ja) 2019-07-10
EP2937567B1 (fr) 2018-05-09
CN104976090B (zh) 2019-05-10
US9963967B2 (en) 2018-05-08
JP2015200317A (ja) 2015-11-12
US20150285077A1 (en) 2015-10-08
EP2937567A3 (fr) 2016-03-16
CN104976090A (zh) 2015-10-14
DE102014104953A1 (de) 2015-10-08

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