WO2007054319A1 - Machine a piston hydrostatique - Google Patents

Machine a piston hydrostatique Download PDF

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Publication number
WO2007054319A1
WO2007054319A1 PCT/EP2006/010768 EP2006010768W WO2007054319A1 WO 2007054319 A1 WO2007054319 A1 WO 2007054319A1 EP 2006010768 W EP2006010768 W EP 2006010768W WO 2007054319 A1 WO2007054319 A1 WO 2007054319A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
cylinder
cylinder drum
pistons
hydrostatic piston
Prior art date
Application number
PCT/EP2006/010768
Other languages
German (de)
English (en)
Inventor
Marcus Herrmann
Werner Hörmann
Georg Jacobs
Original Assignee
Brueninghaus Hydromatik Gmbh
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 Brueninghaus Hydromatik Gmbh filed Critical Brueninghaus Hydromatik Gmbh
Priority to US12/093,163 priority Critical patent/US20080250920A1/en
Priority to EP06828992A priority patent/EP1945949A1/fr
Publication of WO2007054319A1 publication Critical patent/WO2007054319A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—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
    • F04B1/2035—Cylinder barrels
    • 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
    • F03C1/0602—Component parts, details
    • F03C1/0605—Adaptations of pistons
    • 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
    • F03C1/0602—Component parts, details
    • F03C1/0607—Driven 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
    • F03C1/0639—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 having two or more sets of cylinders or pistons
    • 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
    • F03C1/0647—Particularities in the contacting area between cylinder barrel and valve plate
    • F03C1/0649—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
    • F03C1/0652—Cylinders
    • 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
    • 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
    • F04B1/128—Driving 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
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • F04B1/2028—Bearings
    • 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
    • F04B1/22—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 having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/11—Kind or type liquid, i.e. incompressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a hydrostatic piston engine with a cylinder drum unit, which is penetrated by a drive shaft, wherein on the drive shaft rotatably piston are arranged.
  • a hydrostatic piston machine in which a drive shaft penetrates a first and a second cylinder drum unit. Symmetrically between the two cylinder drum units, a support plate is fixed to the drive shaft. On the support plate pistons are arranged opposite one another, which are displaceably mounted in cylinder chambers of the cylinder drum units. The cylinder drum units each have an angle of their rotation axis with respect to the angle of the drive shaft. In this way, the rotatably connected to the drive shaft piston in the cylinder chambers perform a lifting movement.
  • the cylinder chambers are formed in individual cylinders, which are supported on a common drum plate and form a cylinder unit with this.
  • a retaining device is formed, which allows a radial movement of the cylinder.
  • This all-round sliding arrangement allows a compensating movement of the cylinder, which is required due to the fixed arrangement of the pistons in the support plate and the angle of inclination of the cylinder drum unit relative to the drive shaft axis.
  • the described arrangement has the disadvantage that the centrifugal forces cause a tilting moment on the part of the cylinder.
  • the cylinders are held individually via a retaining device in contact with the drum plate, but it comes due to the large number of relatively moving parts to a considerable wear, since for the acting forces only a small contact surface of the cylinder is present.
  • the cylinder drum unit is also penetrated by a drive shaft.
  • Rotatably connected to the drive shaft are pistons that dip into cylinder recesses of the cylinder drum unit.
  • the cylinder recesses are arranged together in a cylinder drum, which forms the cylinder drum unit. This thus performed in a compact form cylinder drum is centered on a total provided on the drive shaft bearing.
  • the individual cylinder recesses of the cylinder drum thus carry out no independent movements. Rather, a centering of the entire cylinder drum is achieved relative to the axis of rotation of the drive shaft. Due to the one-piece design of the cylinder drum itself, the individual cylinder recesses can also perform no tilting movement when centrifugal forces occur.
  • the piston To connect via a hinge connection with the drive shaft is advantageous.
  • the non-rotatable connection of the piston with the drive shaft via a hinge connection has the advantage that an all-round compensation must not be made by a displacement of the cylinder. Rather, is achieved by a different inclination of the piston relative to the drive shaft axis, which allows the hinge connection, the compensating movement.
  • the piston for this purpose with a spherical head which engages in a corresponding spherical recess of the drive shaft or a support plate connected to the drive shaft.
  • the support plate can be designed as a radial extension of the drive shaft itself, for example, as a one-piece forging. It is also conceivable to provide the drive shaft with a toothing, which is engaged with a separately prepared support plate and thus enters into a rotationally fixed connection with this.
  • tilting of the piston axis with respect to the drive shaft axis is possible.
  • an immediate, rotationally fixed connection between the drive shaft and the piston is achieved by the ball joint-shaped fixation of the piston on the support plate.
  • a conical section is formed between a sealing portion and the articulated connection to the piston.
  • the opening angle of the conical section preferably corresponds to the intended maximum angle of inclination of the cylindrical drum.
  • a centering of the cylinder drum is preferably achieved by a bearing which is formed on the drive shaft.
  • a central acts Through opening of the cylinder drum, which is preferably designed as a bore, with a arranged on the drive shaft bearing centering together.
  • the bearing is preferably formed by the drive shaft as a spherical drive shaft section.
  • the torque between the cylinder drum and the drive shaft can be effected by the piston arranged in the cylinder recesses.
  • a carrier element is provided between the spherical drive shaft section and the cylinder drum.
  • the driving element is fixed in the drive shaft and engages in a driving groove of the cylinder drum.
  • the driving element in the region of the spherical drive shaft section, it is also conceivable to arrange the driving element firmly in the cylinder drum. Accordingly, a catch groove is then arranged in the spherical drive shaft section. It can also be provided several, preferably uniformly distributed over the circumference driving elements.
  • piston rings are preferably arranged on the piston in a sealing portion of the piston.
  • the piston rings are z. B. designed as steel rings, which are inserted in a corresponding groove on the part of the piston in the region of the sealing portion.
  • the piston rings are preferably also made spherical.
  • Another way to improve the sealing effect between the piston and the corresponding cylinder recess is to form a thin-walled piston skirt in the region of the sealing portion.
  • Such a thin-walled piston skirt in the region of the sealing section allows the pressure prevailing in the interior of the cylinder to elastically expand the piston skirt, whereby its outer contour is sealingly applied to the cylinder recess. In a particularly simple manner, this can be done by a mounted on the side facing away from the hinge connection side recess in the piston.
  • a return plate which fixes the pistons to the carrier plate in the axial direction.
  • the retraction disc is arranged so that the inclination of the piston is not hindered relative to the carrier plate.
  • the retraction disc surrounds the pistons so that they act as part of the articulation.
  • recesses of the return pulley are provided, which hold the head of the piston and have a spherical contour.
  • FIG. 1 shows a longitudinal section through a first embodiment of a hydrostatic piston machine according to the invention.
  • FIG. 2 shows a longitudinal section through a second embodiment of a hydrostatic piston machine according to the invention
  • FIG. 3 is an enlarged view in the detail III of FIG. 2.
  • a longitudinal section through a first exemplary embodiment of a hydrostatic piston machine 1 according to the invention is shown in FIG. 1.
  • the hydrostatic piston engine 1 has a drive shaft 2, which is mounted in a housing formed from a first housing half 3 and a second housing half 4.
  • the first housing half 3 and the second housing half 4 are approximately pot-shaped.
  • a passage opening 5 is formed in the first housing half 3.
  • the passage opening 5 is executed in the illustrated embodiment as a stepped bore. Through the passage opening 5 projects with a toothing 6 provided end of the drive shaft 2 out.
  • a first drive shaft bearing 7 is arranged in the stepped through hole 5.
  • the first drive shaft bearing 7 is designed as a tapered roller bearing.
  • a sealing element is provided in the stepped passage opening 5, which seals the drive shaft 2 relative to the first housing part 3.
  • a stepped blind bore 8 is formed in the second housing part 4.
  • a second drive shaft bearing 9 is arranged, which is also designed as a tapered roller bearing.
  • the first housing part 3 and the second housing part 4 each have a peripheral flange 10 and 11, respectively.
  • the first housing part 3 and the second housing part 4 are screwed together by means of screws 12 to the flanges 10, 11.
  • a support plate 13 is arranged on the drive shaft 2.
  • the support plate 13 is made in one piece with the drive shaft 2.
  • spherical recesses 14, 15 introduced as joint sockets.
  • pistons 16, 17 are used with arranged at the piston ends spherical heads. The resulting joint connection between the piston and the support plate 13 will be explained in detail below with reference to FIG.
  • the pistons 16 and 17 are identical.
  • the reference numerals 16 and 17 respectively denote only one piston of the group of pistons which cooperate with a cylinder drum 20, 21.
  • the pistons 16, 17 project into cylinder recesses 18, 19 of a first cylinder drum 20 and a second cylinder drum 21, respectively.
  • a plurality are parallel to one another Cylinder recesses 18 and 19 arranged on a first and second circumferential circle.
  • the common circumferential circle of the first cylinder drum 20 and the common circumferential circle of the second cylinder drum 21 are preferably identical and correspond to the circumferential circles on which the spherical recesses 14, 15 are arranged on the support plate 13.
  • the cylinder drums 20, 21 are arranged inclined relative to the axis of rotation of the drive shaft 2. During a rotation of the cylinder drums 20, 21 and the drive shaft 2, the pistons 16 and 17 in the corresponding cylinder recesses 18 and 19, respectively, perform a lifting movement and reduce and thereby cyclically increase the enclosed cylinder volume.
  • the cylinder drums 20 and 21 are based on a respective swash plate 22 and 23 from.
  • the swash plates 22, 23 are fixed, so that a constant inclination angle of the first and second cylinder drum 20, 21 with respect to the axis of the drive shaft 2 sets.
  • Another possibility is to provide one of the cylinder drums 20 and 21 with a fixed angle and to provide the respective other cylinder drum 21, 20 with a changeable pivot angle.
  • the illustrated embodiments relate to double pumps or double motors. Features that are explained for one side only, are provided in the figures on the opposite side with a corresponding, painted reference numerals.
  • the first cylinder drum 20 has a running surface 25, with which it is supported on a support surface 24 of the swash plate 22. In order to secure the swash plate 22 against rotation, it is fixed with a dowel pin 27 in the first, cup-shaped housing part 3 at the bottom 30.
  • the cylinder recesses 18 are connected via cylinder openings 28 in a rotation of the cylinder drum 20 cyclically with control holes, not shown, in the swash plate 22 connectable.
  • each of the first swash plate 22 and the second swash plate 23 each set a fixed pivot angle for the first cylinder drum 20 and the second cylinder drum 21.
  • the inclination angle of the cylinder drums 20, 21 with respect to the axis of the drive shaft 2 is determined by a wedge shape of the swash plates 22, 23.
  • the swash plate 22 has a bearing surface 29, with which it rests against the bottom 30 of the first housing part 3.
  • the first cylinder drum 20 has a central passage opening 31, which is designed as a cylindrical bore. With the central passage opening 31, the first cylinder drum 20 is supported on a bearing of the drive shaft 2.
  • the bearing of the drive shaft 2 is formed as a spherical shape 32 of the outer contour of the drive shaft 2.
  • the spherical shape 32 is realized directly by the shape of the drive shaft 2 itself.
  • an attached element can be used as a bearing, which has a spherical outer contour.
  • different materials can be used to form the bearing and for the drive shaft 2 itself, for example, to achieve improved runflat in case of lack of lubrication.
  • a spring 33 is provided, which is also supported on a support body 34 to the bearing of the drive shaft 2.
  • the support body 34 has for this purpose a spherical recess in the region of its contact with the bearing of the drive shaft 2, which corresponds to the spherical shape 32 of the bearing of the drive shaft 2.
  • the outer diameter of the support body 34 formed as a ring corresponds to the inner diameter of the central passage opening 31 of the first cylinder drum 20.
  • the spring 33 is supported on a circlip 35, which in a groove of the cylinder drum 20th is used.
  • a return pulley 36 is provided.
  • the retraction disk 36 is screwed to the support plate 13, for example, and fixes the spherical heads 43 of the pistons 16 in the respective spherical recesses 14.
  • the retraction disk 36 has a number of openings 37 corresponding to the number of pistons 16, which are also spherically shaped and with the outer contour of the spherical head 43 of the piston 16 correspond.
  • the piston 16 is also spherical in its spherical projection over the spherical recess 14.
  • the pistons 16 have a lubricating oil bore 38 which extends from a piston crown 39 to an opposite flattened end 40 on the spherical head 43 of the piston 16. By the lubricating oil bore 38, a hydrostatic discharge of the piston 16 is achieved in the joint connection.
  • the hydrostatic piston machine 1 can be used both as a pump and as a motor.
  • the rotationally fixed with respect to a rotation about the axis of the drive shaft 2 with the support plate 13 connected pistons 16, 17 thus also perform a rotation about the axis of the drive shaft 2 from.
  • About the piston 16, 17 is a torque to the first cylinder drum 20 and the second cylinder drum 21 transmitted.
  • the cylinder drums 20, 21 thus perform a rotating movement about their relative to the axis of the drive shaft 2 inclined cylinder drum axes.
  • the spring 33, 33 ' the cylinder drum 20 and 21 is held in each case in contact with the swash plate 22 and 23 respectively. Due to the inclination of the axes of rotation of the drive shaft 2 to the cylinder drums 20, 21 perform the piston 16, 17 in the corresponding ZylinderausEnglishept 18, 19 strokes, wherein the promoted by the variable cylinder volume during a circulation pressure medium in the same or different hydraulic circuits are promoted can.
  • the required torque for rotating the cylinder drums 20, 21 is transmitted through the pistons 16 and 17, respectively, from the carrier plate 13 to the cylinder drums 20, 21.
  • the piston 16, 17 perform a tilting movement until a between a sealing portion 41 and 42 of the piston 16 and 17 and the spherical head 43 and 44 of the piston 16, 17 lying conical portion 45 and 46 in abutment with the Cylinder recesses 18 and 19 is.
  • the piston 16 Adjacent to the piston head, the piston 16 has a sealing portion 41.
  • the sealing portion 41 is thin-walled.
  • the thin-walled design of the sealing portion 41 is achieved in the illustrated embodiment by a recess 65 which is introduced from the side of the piston head into the piston 16.
  • the piston 16 is designed spherically in its sealing portion 41 at its outer periphery. Such a spherical outer contour can take place, for example, by introducing a cylindrical recess 65 into the piston bottom, whereupon the thin-walled wall section 66 is shaped to reach the spherical outer contour.
  • An alternative to the transmission of the torque between the drive shaft 2 and the cylinder drums 20, 21 is shown in FIG.
  • the same reference numerals designate in FIG. 2 the features already known from FIG. 1. In order to prevent unnecessary repetition, a detailed re-description of the entire piston engine 1 'is dispensed with.
  • Embodiment of FIG. 2 entrainment elements 50, 51 is provided.
  • the driving elements 50, 51 are made equal and act in the same way between the
  • embodiments are limited to the driving element 50 shown on the left in FIG. 2.
  • the driving element 50 has a cylindrical portion 52.
  • the cylindrical portion 52 is inserted in a recess 53.
  • the depth of the recess 53 is greater than the length of the cylindrical portion 52 of the driving element 50.
  • the driving element 50 extends beyond the spherical shape 32 of the bearing of the drive shaft 2 radially out, wherein the protruding part is formed as a radially extended portion 54.
  • An end face 55 of the entraining element 50 formed on the widened region 54 is likewise spherically shaped. In the direction of the longitudinal axis of the driving element 50, the end face 55 could be connected to the opposite end of the driving element 50 through a channel 57.
  • the radially expanded region 54 engages in a groove 56 of the cylinder drum 20.
  • the channel 57 could be connected via a connecting channel 58 to a volume formed in the spherical recess 14 by the flattened end 40 of the piston 16.
  • a connecting channel 58 to a volume formed in the spherical recess 14 by the flattened end 40 of the piston 16.
  • a connecting channel 59 with the corresponding volume, which is enclosed behind the piston 17 in the spherical recess 15, connected.
  • FIG. 3 shows a second alternative embodiment for a sealing section 41 ', 42' of the pistons 16, 17.
  • the piston 17 is formed as a solid piston 17'.
  • the solid piston 17 ' also has a spherical outer contour 67 at its end projecting into the cylinder recess 19.
  • a groove 68 is introduced into the sealing section 42 'of the solid piston 17'.
  • a sealing ring 69 is inserted, which cooperates sealingly with the wall of the cylinder recess 19.
  • the piston ring 69 is preferably made of steel, for example.
  • outer surface 70 of the piston ring 69 is preferably also spherically shaped.
  • the cylinder drums 20, 21 are each made in one piece.
  • the proportions of the relatively moving parts are drastically reduced and the high rigidity of the cylinder drums 20, 21 leads to a good absorption of the lateral forces, which occur both due to the centrifugal forces and due to the internal pressure in the cylinder recesses 18, 19.
  • the compensating movement of the pistons 16, 17, which is required due to the ellipsoidal movement of the sealing portions 41, 41 ', 42, 42' of the pistons 16 and 17, is in a simple manner by a hinge connection between the support plate 13 and the piston 16, 17th causes.
  • the pistons 16, 17 are arranged with a ball-joint-like connection in the support plate 13 and are fixed thereto to prevent axial movement during the suction stroke by a respective retraction disk 36 and 36 '.
  • the retraction disk 36, 36 'in turn forms part of the hinge connection by the recesses 37, 37' of the return pulleys 36, 36 'in turn cooperate with the spherical head 43 and 44 of the piston 16 and 17 respectively.
  • a hydrostatic relief of the joints of the piston 16, 17 is provided.
  • the flat sides of the radially expanded portion 54 of the driving element 50, 51 which engage in the groove 56, 56 'of the cylindrical drum 20, 21, could be pressure-lubricated.
  • a plurality of channel sections 72 can be provided in the driver elements 50, 51 distributed over the circumference of the driver elements 50, 51, which connect the circumferential groove 71 with the channel 57 or 60.
  • the pressure medium supplied via the connecting channel 59 to the channel 60 exits from the bore 73 of the widened region 54 'of the driving element 51 and ensures pressure-lubricated contact surfaces of the driving element 51 in the groove 56' of the cylindrical drum 21.
  • the invention is not limited to those shown

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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)

Abstract

L'invention concerne une machine à piston hydrostatique (1) comprenant un arbre d'entraînement (2) qui traverse une unité de tambour cylindrique. Dans l'unité de tambour cylindrique sont disposés des évidements cylindriques (18, 19). Des pistons (16, 17) sont connectés de manière solidaire en rotation à l'arbre d'entraînement (2) et sont disposés de manière à pouvoir coulisser dans les évidements cylindriques (18, 19). L'unité de tambour cylindrique est centrée sur un palier (32, 32') disposé sur l'arbre d'entraînement (2). L'unité de tambour cylindrique se compose d'un tambour cylindrique (20, 21) comprenant plusieurs évidements cylindriques (18, 19).
PCT/EP2006/010768 2005-11-11 2006-11-09 Machine a piston hydrostatique WO2007054319A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US12/093,163 US20080250920A1 (en) 2005-11-11 2006-11-09 Hydrostatic Piston Machine
EP06828992A EP1945949A1 (fr) 2005-11-11 2006-11-09 Machine a piston hydrostatique

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005053932.7 2005-11-11
DE102005053932 2005-11-11
DE102005058938A DE102005058938A1 (de) 2005-11-11 2005-12-09 Hydrostatische Kolbenmaschine
DE102005058938.3 2005-12-09

Publications (1)

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DE102016124048A1 (de) 2016-12-12 2018-06-14 Kamat Gmbh & Co. Kg Axialkolbenpumpe mit großer Fördermenge bei geringer Drehzahl und Verwendung einer Kolbenpumpe in einer Windkraftanlage

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US20160131118A1 (en) * 2014-11-06 2016-05-12 Robert Bosch Gmbh Tandem axial piston pump with shared cylinder block
BR112017009603A2 (pt) * 2014-11-08 2017-12-19 Money S R L máquina hidráulica com cilindros axiais oscilantes aperfeiçoados
DK3477102T3 (da) * 2017-10-25 2021-03-08 Innas Bv Hydraulisk anordning
EP4296504A1 (fr) * 2022-06-21 2023-12-27 Innas B.V. Dispositif hydraulique

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US4872394A (en) * 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
WO2005085635A1 (fr) * 2004-03-03 2005-09-15 Bosch Rexroth Ag Machine a piston axial

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Publication number Priority date Publication date Assignee Title
DE102016124048A1 (de) 2016-12-12 2018-06-14 Kamat Gmbh & Co. Kg Axialkolbenpumpe mit großer Fördermenge bei geringer Drehzahl und Verwendung einer Kolbenpumpe in einer Windkraftanlage
WO2018108894A1 (fr) 2016-12-12 2018-06-21 Kamat Gmbh & Co. Kg Pompe à pistons et utilisation de ladite pompe dans une éolienne

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DE102005058938A1 (de) 2007-05-16
EP1945949A1 (fr) 2008-07-23
US20080250920A1 (en) 2008-10-16
KR20080066910A (ko) 2008-07-17

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