EP2004996A1 - Machine a piston hydrostatique avec disque de commande rotatif - Google Patents

Machine a piston hydrostatique avec disque de commande rotatif

Info

Publication number
EP2004996A1
EP2004996A1 EP07724052A EP07724052A EP2004996A1 EP 2004996 A1 EP2004996 A1 EP 2004996A1 EP 07724052 A EP07724052 A EP 07724052A EP 07724052 A EP07724052 A EP 07724052A EP 2004996 A1 EP2004996 A1 EP 2004996A1
Authority
EP
European Patent Office
Prior art keywords
control
control plate
slots
ring
hydrostatic piston
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Withdrawn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
EP07724052A
Other languages
German (de)
English (en)
Inventor
Rainer Stölzer
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.)
Brueninghaus Hydromatik GmbH
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
Publication of EP2004996A1 publication Critical patent/EP2004996A1/fr
Withdrawn legal-status Critical Current

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
    • F04B1/22—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
    • 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
    • F03C1/0644—Component parts
    • F03C1/0652—Cylinders
    • 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
    • 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
    • F04B1/14—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 stationary cylinders
    • F04B1/16—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 stationary cylinders having two or more sets of cylinders or 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
    • F04B1/20—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
    • 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
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • 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

Definitions

  • the invention relates to a hydrostatic piston machine, which is provided for delivery in two hydraulic circuits.
  • the axial piston machine has a cylinder drum arranged rotatably in a housing. In the cylinder drum, a first group of cylinder bores and a second group of cylinder bores is arranged. In the cylinder bores each longitudinally displaceable pistons are arranged, which are supported for generating a piston stroke on a swash plate.
  • the swash plate is tiltable about a first pivot axis and about a second pivot axis, so that the delivery volume for the first and the second hydraulic circuit can be adjusted.
  • the first and the second pivot axis are preferably perpendicular to each other. Accordingly, in a control plate, which allows the two-part connection of the cylinder bores with the terminals of the first and the second hydraulic circuit, control slots are arranged.
  • the two control slots for the first group of cylinder bores and the two control slots for the second group of cylinder bores are rotated by 90 ° to each other, so that in each case an inclination about the first pivot axis, a change of the delivery volume in the first hydraulic circuit and a slope of the swash plate around the second pivot axis a change of Flow volume causes in the second hydraulic circuit.
  • the invention is therefore an object of the invention to provide a hydrostatic piston engine, which is improved in terms of their efficiency with a simultaneous promotion in the first and the second cycle.
  • the hydrostatic piston machine has a housing in which a cylinder drum is rotatably arranged.
  • a first group of cylinder bores and a second group of cylinder bores are arranged in the cylinder drum.
  • the first group of cylinder bores communicates via first control slots, which are arranged in a control plate, with a rotation of the cylinder drum temporarily with the terminals of a first hydrostatic circuit.
  • the first group of cylinder bores is thus connected via the first control slots to a suction-side or a pressure-side connection of the first hydraulic circuit during one revolution of the cylinder drum.
  • a second group of cylinder bores which are also arranged in the cylinder drum, temporarily connected via second control slots of the control plate with a second circuit conveyor or suction side.
  • pistons are arranged longitudinally displaceably in the cylinder bores of the first group as well as the cylinder bores of the second group.
  • the pistons are supported on a swashplate to produce a piston stroke when the cylinder drum rotates.
  • the swash plate is tiltable about at least one pivot axis.
  • the control slots can each be oriented so that the arranged between the control slots dead center in the control plate in the region of the top and bottom dead center of the pistons are arranged. This ensures that while the cylinder bores of the first and the second group are in communication with the respective control slots, a pure suction stroke, or a pure pressure stroke is performed by the piston without the piston exceed the top or bottom dead center. The reversal of a suction stroke to a pressure stroke in the region of the upper and the lower dead center is thus carried out in a between the first control slots or between the second control slots lying dead center of the control plate.
  • Control slots and for the second control slots is the same.
  • Such an embodiment may, for. B. be advantageous if the two hydraulic circuits an engine or a cylinder are supplied with pressure medium. Another example of this is the combination of a traction drive in one hydraulic circuit with a working hydraulics in the other hydraulic circuit.
  • the two control plate rings have different diameters, so that preferably the second control plate ring is arranged in the first control plate ring and centers it.
  • the first control plate ring comprises the first control slots and the second control plate ring, the second control slots.
  • a preferred embodiment results when the first control plate ring is formed as a spur gear and / or the second control plate ring is formed as a ring gear and at least one of the two control plate rings with a toothing of a
  • Actuating element cooperates. In this way, the adjustment of the relative position can be done either via the first control plate ring or via the second control plate ring.
  • the first control plate ring as a spur gear and the second
  • Control plate ring designed as a ring gear, so also an independent adjustment can be performed by one adjusting element.
  • the first control plate ring is designed as a ring gear of a planetary gear and the second control plate ring as a sun gear of the planetary gear. In this way, it is sufficient to adjust either the first control plate ring or the second control plate ring by an actuator.
  • the housing side fixed planetary gears By reversing the direction of rotation, transfer the adjusting movement to the other control plate ring.
  • Fig. 1 is a sectional view of a
  • Axial piston machine for conveying in two separate hydraulic circuits
  • Fig. 2 is an enlarged view of the engine of the axial piston machine of Fig. 1;
  • FIG. 3 shows a schematic representation with a swash plate inclined about a first pivot axis
  • FIG. 4 shows a schematic representation with a swash plate inclined about a second pivot axis
  • Fig. 5 is a schematic representation of an adjustable control plate for a hydrostatic piston engine
  • Fig. 6 is a schematic representation of the back side of the adjustable control plate shown in Fig. 1;
  • Fig. 7 shows a second embodiment of an adjustable control plate and Fig. 8 shows a third embodiment of an adjustable control plate.
  • a common drive shaft 2 is supported by a roller bearing 3 at one end of a housing 4.
  • the common drive shaft 2 is mounted in a sliding bearing 6, which is arranged in a connection plate 5, which closes the housing 4 at the opposite end.
  • connection plate 5 In the connection plate 5 is a, the connection plate 5 completely penetrating in the axial direction recess 7 is formed, in which on the one hand the sliding bearing 6 is arranged and which is penetrated to the other of the common drive shaft 2.
  • an auxiliary pump 8 On the side facing away from the housing 4 side of the connection plate 5, an auxiliary pump 8 is inserted into a radial extension of the recess 7.
  • the common drive shaft 2 has a toothing 9, which is in engagement with a corresponding toothing of an auxiliary pump shaft 10.
  • the auxiliary pump shaft 10 is in the recess 7 by a first auxiliary pump slide bearing 11 and supported by a second auxiliary pump slide bearing 12 in an auxiliary pump connection plate 13.
  • an auxiliary pump gear 14 is arranged, which is in engagement with an auxiliary pump ring gear 15.
  • the auxiliary pump ring gear 15 which is rotatably disposed in the auxiliary pump connection plate 13, also driven by the auxiliary pump shaft 10 and thus ultimately by the common drive shaft 2.
  • Auxiliary pump connection plate 13 the suction and the pressure-side connection for the auxiliary pump 8 are formed.
  • the auxiliary pump 8 is fixed by a cover 16, which is mounted on the connection plate 5, in the radial extension of the recess 7 of the connection plate 5.
  • the inner ring of the roller bearing 3 is fixed in the axial direction on the common drive shaft 2.
  • the inner ring is on the one hand on a collar 17 of the common
  • Circlip 19 determines that is inserted into a circumferential groove of the shaft opening 20.
  • the roller bearing 3 On the other side is the roller bearing 3, on a housing shoulder, not shown, of the housing 4.
  • a sealing ring 21 and finally a further locking ring 22 is disposed in the shaft opening 20, wherein the locking ring 22 is inserted into a circumferential groove of the shaft opening 20.
  • a drive toothing 23 is formed, via which the hydrostatic piston engine is driven by a drive machine, not shown.
  • a cylinder drum 24 is arranged, which has a central passage opening 25, which is penetrated by the common drive shaft 2.
  • a driving teeth 26 the cylinder drum 24 is secured against rotation, but slidably connected in the axial direction with the common drive shaft 2, so that a rotary motion of the common drive shaft 2 transmits to the cylinder drum 24.
  • a first support plate 28 In a formed in the central through hole 25 circumferential groove another circlip 27 is used, on which a first support plate 28 is applied.
  • the first support disk 28 forms a first spring bearing for a compression spring 29.
  • a second spring bearing for the compression spring 29 is formed by a second support plate 30, which is supported on the end face of the driving teeth 26. The compression spring 29 thus exerts on the one hand on the common
  • the compression spring 29 acts on the cylinder drum 24, which is formed with a formed on the end face of the cylinder drum 24 spherical Recess 31, is held in abutment against a control plate 32.
  • the control plate 32 in turn bears sealingly against the connection plate 5 with the side remote from the cylinder drum 24. Due to the spherical recess 31, which corresponds to a corresponding spherical shape of the control plate 32, the cylinder drum 24 is centered.
  • the control plate 32 may also be designed as a flat disk, if, for example, by an otherwise realized centering of the cylinder drum 24 together with a spherical control plate 32 would lead to over-determination.
  • cylinder bores 33 are distributed over a common pitch circle introduced, in which pistons 34 are arranged in the
  • Cylinder bores 33 are longitudinally displaceable. At the end remote from the spherical recess 31, the pistons 34 protrude partially out of the cylinder drum 24. At this end, a sliding shoe 35 is attached to the piston 34, via which the pistons 34 are supported on a running surface 36 of a swash plate 37.
  • the swash plate 37 can this purpose by a
  • Adjustment 38 are adjusted in their inclination. To absorb the forces that are transmitted by the sliding blocks 35 on the swash plate 37, the swash plate 37 is mounted in the housing 4.
  • connection plate For connecting the hydrostatic piston machine 1 to a first hydraulic circuit and to a second hydraulic circuit are in the connection plate. 5 schematically a first port 39 and a second port 39 'are shown, which are connected in a manner not shown on the control plate 32 with the cylinder bores 33.
  • FIG. 2 An enlarged view of the cooperating in the interior of the housing 4 components is shown in Fig. 2.
  • the swash plate 37 is coupled to a sliding block 44, which rotates in a manner not shown, the swash plate 37 about an axis lying in the plane of the pivot axis.
  • the cylinder bores generally indicated at 33 in FIG. 1 are subdivided into a first group of cylinder bores 33. 1 and a second group of cylinder bores 33. 2.
  • a sliding shoe 35 is arranged on the end of the piston 34 facing away from the control plate 32 in each case.
  • the shoe 35 is fixed with a recess on a spherical head of the piston 34 so that the shoe 35 is movably fixed to the piston 34 and tensile and compressive forces are transferable.
  • a sliding surface 45 is formed, with which the sliding shoe 35 and thus the piston 34 is supported on the running surface 36 of the swash plate 37.
  • Lubricating oil grooves are formed in the sliding surface 45 and are connected to the cylinder bores 33 formed in the cylinder barrel 24 via a lubricating oil passage 46 formed in the sliding shoe 35, which is continued in the piston 34 as a lubricating oil bore 46 '.
  • first connection channels 47.1 and second connection channels 47.2 are connected to the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2.
  • the first and second connection channels 47.1 and 47.2 extend from the cylinder bores of the first group 33.1 and the cylinder bores of the second group 33.2 to the spherical recess 31 which is formed on an end face 48 of the cylinder drum 24.
  • first control slots 50 and 51 are formed, which penetrate the control plate 32 in the axial direction.
  • Control slots formed which are not visible because of the position of the cutting plane in Fig. 2. While the first control slots 50 and 51 are connected via the connection plate 5 with working lines of the first hydraulic circuit, the second control slots are connected in a corresponding manner to the two working lines of the second hydraulic circuit.
  • the first control slots 50 and 51 have an identical first distance R 1 from the central axis 40 of the cylinder drum 24 which is greater than the distance R 2, which in turn is identical for the second control slots.
  • the first connection channels 47.1 are connected successively to the first control kidney 50 and the second control kidney 51, so that due to the lifting movement of the arranged in the cylinder bores 33.1 of the first group piston 34, the pressure medium on the one first
  • Control slot 51 is sucked and pumped via the other first Steuerschitz 50 in the pressure-side working line of the first hydraulic circuit.
  • the first connection channels 47.1 are arranged in the cylinder drum 24, that the first distance R 1 of the orifice at the end face 48 is greater than the second distance R 2 , in which the second connection channels 47.2 open at the end face 48.
  • the second connection channels 47.2 have a radial direction component and accordingly open out at the end face 48 of the cylinder drum 24 with the second distance R 2 , which corresponds to the distance of the second control slots from the central axis 40.
  • the cylinder bores of the second group 33.2 are thus alternately connected via the second connection channels 47.2 to the two second control slots.
  • a retraction plate 52 In order to prevent lift-off of the sliding shoes 35 from the running surface 36 of the swash plate 37 during a suction stroke, a retraction plate 52 is provided, which guides the sliding shoes 35 on a shoulder provided for this purpose embraces.
  • the retraction plate 52 has z. B. a spherical, central recess 53, with which it is supported on a retraction ball 54 which is disposed at the end facing away from the end face 48 of the cylinder drum 24.
  • Fig. 3 it is shown how starting from an axial piston machine of Figs. 1 and 2, with a swash plate 37 ', an independent adjustment of the flow rates for the two hydraulic circuits can be achieved.
  • the swash plate 37 ' is tiltable about a first pivot axis 55 and about a second pivot axis 56.
  • the first and second pivot axes 55 and 56 are in the plane of the tread 36 of the swash plate 37 and, when the axial piston machine is set to zero delivery volume in both hydraulic circuits, with the central axis 40 at an angle of 90 °.
  • Fig. 3 it is shown that the swash plate 37 'is inclined about the second pivot axis 56. This is an effective stroke for conveying pressure medium z. B. generated in the second hydraulic circuit. As an effective stroke while a movement of the piston 34 is referred to, which leads to an actual conveying of pressure medium.
  • the second connecting channels 47.2 move during half a revolution of the cylinder drum 24 from the bottom dead center to the top dead center substantially along the one second control slot 57, so that the pressure medium is pressed into the pressure-side working line of the second hydraulic circuit.
  • the second connection channels 47.2 move on the way from the top dead center to the bottom dead center substantially along the other second control slot 58 and perform a suction stroke.
  • first pivot axis 55 and the second pivot axis 56 are arranged at a right angle to each other.
  • a promotion in the first hydraulic circuit does not take place in the illustrated deflection of the swash plate 37 '.
  • the position of the first control slots 50 and 51 is symmetrical with respect to the position of the top and bottom dead center, so that in spite of the use of the common swash plate 37 'in the first hydraulic circuit only a pulsation is generated, as long as the swash plate 37' is not in addition to the first pivot axis 55 is inclined.
  • the first and the second control slots 50, 51, 57, 58 are preferably arranged rotated by 90 ° relative to one another in the control plate 32.
  • the second control slots 57, 58 are formed symmetrically to a projection 56 'of the second pivot axis 56 in the plane of the control plate 32.
  • the first control slots 50, 51 are correspondingly formed symmetrically with respect to a (not shown) projection of the first pivot axis 55.
  • this is disadvantageous for a variable adjustment of the flow rates of both circuits.
  • first pivot axis 55 and the second pivot axis 56 are in FIG arranged at right angles to each other, wherein both pivot axes 55 and 56 lie in the plane of the tread 36.
  • the intersection of the first pivot axis 55 with the second pivot axis 56 coincides with the intersection of the two pivot axes 55 and 56 with the central axis 40.
  • the swash plate 37 ' On its side facing away from the running surface 36, the swash plate 37 'is designed hemispherical at least in a region 59 adjacent to the running surface 36.
  • a bearing a ball bearing or a plain bearing can be provided to support the swash plate 37 'and to allow their rotation.
  • the hemispherical region 59 is bounded by a flat 63 preferably formed parallel to the running surface 36.
  • the adjustment of the inclination of the swash plate 37 ' can be done either via a separate adjustment for each pivot axis 55 and 56, wherein in Fig. 1, only the adjustment for the pivot axis 55 is shown and the adjustment for the pivot axis 56 in the sectional view can not be seen , or via a common adjusting device, via which a resulting inclination angle of the swash plate 37 'is set.
  • Fig. 4 it is shown that the swash plate 37 'is with respect to the second pivot axis 56 in its neutral position, with respect to its first pivot axis 55, however, is inclined.
  • an effective stroke is generated only for those pistons 34, which via the first connection channels 47.1 during one revolution the cylinder drum 24 are alternately connected to the one first control slot 50 and the other first control slot 51.
  • Connecting channels 47.2 connectable to the second control slots 57 and 58 respectively, perform only a movement around the bottom dead center or around the top dead center in the region in which a connection with the respective hydraulic circuit is made, which in turn only a small Pulsation generated in the working lines of the second hydraulic circuit.
  • an embodiment of an adjustable control plate 32 ' is shown.
  • the control plate 32 ' includes a first control plate ring 70 and a second control plate ring 71.
  • the first control plate ring 70 and the second control plate ring 71 are arranged in a common plane and together form the control plate 32'.
  • the outer diameter of the second control plate ring 71 is dimensioned such that the second control plate ring 71 can be arranged in a central recess of the first control plate ring 70.
  • the first control plate ring 70 and the second control plate ring 71 form a ring gear or a sun gear of a planetary gear.
  • a first toothing 72 is formed on the outer end face.
  • a second toothing 73 is formed over part of the thickness of the first control plate ring 70.
  • a third toothing 74 is formed on the second control plate ring 71, set back in the radial direction relative to the outer peripheral edge of the second control plate ring 71.
  • planetary gears 75.1, 75.2 and 75.3 are arranged between the second toothing 73 of the first control plate ring 70 and the third toothing 74 of the second control plate ring 71 .
  • the planet gears 75.1, 75.2 and 75.3 are rotatable about their central axes but fixedly arranged in the housing 4 of the piston engine 1.
  • the two first control slots 50 and 51 are formed on their side facing the connection plate 5 by four control slot parts 50.1 to 50.4 or 51.1 to 51.4. Accordingly, the second control slots 57 and 58 are formed by control slot parts 57.1 to 57.4 or 58.1 to 58.4. Between the control slot parts 50.1 to 50.4 and the control slot parts 51.1 to 51.4 first dead center areas 86 and 87 are formed. In a corresponding manner, second dead center areas 88 and 89 are formed between the second control slot parts 57.1 to 57.4 and 58.1 to 58.4.
  • the position of these first dead center regions 86, 87 or second dead center regions 88 and 89 is adapted to the upper and lower dead center positions resulting from the inclination of the swash plate 37.
  • the adjustment of the dead center areas 86, 87 and 88, 89 takes place in opposite directions.
  • the direction of rotation of the first control plate ring 70 is in the planetary gear, in which the planet gears 75.1 to 75.3 are arranged stationary, transferred in the reverse direction to the second control plate ring 71 for this purpose.
  • an actuating element 76 is provided to generate the drive torque to the first control plate ring 70.
  • the adjusting element 76 has a shaft 77, which carries a first spur gear 78 at a first end and a second spur gear 79 at its second end.
  • the two spur gears 78 and 79 are rotatably connected to the shaft 77, which is mounted in a manner not shown in the connection plate 5 of the hydrostatic piston machine 1.
  • a rotational movement of the shaft 77 is transmitted to the first control plate ring 70 via the first spur gear 78, which engages with the first gearing 72 of the first control plate ring 70.
  • the rotational movement of the shaft 77 is generated at the second spur gear 79, wherein the frontal toothing of the second spur gear 79 cooperates with a rack 80.
  • the rack 80 is preferably arranged axially displaceably in the connection plate 5 and can be acted on at its two end faces 81, 82, for example, by a hydraulic force.
  • the rack 80 is preferably in the region of its opposite ends by a first guide portion 83 and a second guide portion 84 sealing in the connection plate fifth stored.
  • pressure chambers are formed in the connection plate 5, through which the first end face 81 and / or the second end face 82 can be acted upon by a hydraulic force.
  • FIG. 6 shows the arrangement of FIG. 5 from the rear side.
  • the side of the control plate 32 'oriented toward the cylinder drum 24 is shown.
  • the first control slot parts 50.1 to 50.4 and 51.1 to 51.4 on this side are connected to first control slots 50 and 51, respectively.
  • the second control slot parts 57.1 to 57.4 or 58.1 to 58.4 are connected to second control slots 57 and 58, respectively.
  • the first dead center areas 86 ', 87' and between the second control slots 57, 58 the second dead center areas 88 ', 89' are clearly visible.
  • FIG. 6 shows the arrangement of FIG. 5 from the rear side.
  • the inner diameter di of the first Control plate ring 70 corresponds to the outer diameter D 2 of the second control plate ring 71, so that the first control plate ring 70 centered on the second control plate ring 71.
  • FIG. 7 A second embodiment of an adjustable control plate is shown in FIG. 7.
  • the first toothing 72 of the first control plate ring 70 cooperates with a first actuating element 76 '.
  • the first actuating element 76 is driven by the drive element 80 in the same way as has already been explained with reference to FIG. 5.
  • the dependent adjustment of the first control plate ring 70 'and the second control plate ring 71' but not by forming the first control plate ring 70 'as a ring gear and the second control plate ring 71' as a sun gear of a planetary gear, but by a second actuator 90, the second control plate ring 71th 'drives.
  • the second control plate ring 71 ' is provided for this purpose at its inner periphery with a fourth toothing 91, which cooperates with a first spur gear 92 of the second actuating element 90.
  • the second control element 90 is also constructed with a shaft 93, at the opposite ends of which the first spur gear 92 and a second spur gear 94 of the second control element 90 are arranged.
  • the two adjusting elements 76 and 90 are preferably constructed identically. In order to transmit a rotational movement of the first actuating element 76 to the second actuating element 93, the second spur gears 79 and 94 of the first actuating element 76 and of the second Control element 90 connected to each other via a spur gear.
  • the spur gear comprises a single intermediate gear 95.
  • the idler gear 95 is also arranged in the connecting plate 5 in a manner not shown.
  • the second actuator 90 is adapted to the first actuator 76 in that the resulting rotational movement of the first control plate ring 70 and the second control plate ring 71 is identical.
  • each control plate ring 70 ', 71' is assigned its own control element 76 or 90.
  • a separate rack 80 is provided as the drive element or 96 for driving the adjusting elements 76 and 90, respectively.
  • the second drive element 96 cooperates via a spur gear with the further spur gear 95 '.
  • adjustable control plates 32 ' it is possible to adapt the position of the first and second dead center regions 86, 87, 88, 89 to the respective operating state of the piston engine 1.
  • the resulting pivot axis which results from the inclination of the swash plate 37 about the first pivot axis 55 and the second pivot axis 56 is variable. Accordingly, the position of the upper and lower dead center of the pistons 34 in the cylinder bores 33.1, 33.2 of the first and second groups changes.
  • adjustable control plate 32 With the aid of the adjustable control plate 32 'according to one of the embodiments of Figures 5 to 8 is an adjustment of the position of the first control slots 50, 51 and the position of the second control slots 57, 58 and thus the first dead center areas 86, 87 and the second dead center 88, 89 to the position of the upper and lower dead centers of the piston 34 possible.
  • the invention is not limited to the illustrated embodiments. In particular, it is possible to combine individual features of the individual embodiments in any way with each other.

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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)

Abstract

L'invention concerne une machine à piston hydrostatique. La machine à piston hydrostatique comprend un boîtier, dans lequel un tambour de cylindre est monté de manière rotative. Dans le tambour de cylindre, un premier groupe de perçages de cylindre et un deuxième groupe de perçages de cylindre sont disposés. Dans les perçages de cylindre, des pistons sont respectivement disposés de manière à coulisser longitudinalement, lesquels sont en appui sur un plateau oscillant pouvant s'incliner sur au moins un axe de pivotement. Le premier groupe de perçages de cylindre est ponctuellement en liaison, via des premières lumières de distribution (50, 51) d'un plateau de commande pendant une rotation du tambour de cylindre, avec un premier circuit hydraulique. De manière correspondante, les perçages de cylindre du deuxième groupe sont en liaison ponctuelle, via des deuxièmes lumières de distribution (57, 58) du plateau de commande (32') lors d'une rotation du tambour de cylindre, avec un deuxième circuit hydraulique. La position relative des premières et/ou deuxièmes lumières de distribution (50, 51 ; 57, 58) par rapport à l'au moins un axe de pivotement du plateau oscillant peut varier.
EP07724052A 2006-04-10 2007-04-05 Machine a piston hydrostatique avec disque de commande rotatif Withdrawn EP2004996A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006016771 2006-04-10
DE102006021570A DE102006021570A1 (de) 2006-04-10 2006-05-09 Hydrostatische Kolbenmaschine mit drehbarer Steuerscheibe
PCT/EP2007/003111 WO2007118624A1 (fr) 2006-04-10 2007-04-05 Machine a piston hydrostatique avec disque de commande rotatif

Publications (1)

Publication Number Publication Date
EP2004996A1 true EP2004996A1 (fr) 2008-12-24

Family

ID=38121965

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Application Number Title Priority Date Filing Date
EP07724052A Withdrawn EP2004996A1 (fr) 2006-04-10 2007-04-05 Machine a piston hydrostatique avec disque de commande rotatif

Country Status (6)

Country Link
US (1) US20090084258A1 (fr)
EP (1) EP2004996A1 (fr)
JP (1) JP2009531590A (fr)
KR (1) KR20080108078A (fr)
DE (1) DE102006021570A1 (fr)
WO (1) WO2007118624A1 (fr)

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NL2005504C2 (nl) * 2010-10-12 2012-04-16 Innas Bv Hydraulische inrichting met een spiegelplaat.
FR3000768B1 (fr) * 2013-01-08 2016-07-15 Technoboost Machine hydraulique comportant une chambre de pre-compression et un deuxieme angle d'inclinaison
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EP3246566B1 (fr) 2016-05-19 2018-12-19 Innas B.V. Dispositif hydraulique, procédé de fabrication d'un dispositif hydraulique et groupe de dispositifs hydrauliques
EP3246567B1 (fr) 2016-05-19 2022-03-09 Innas B.V. Dispositif hydraulique
EP3246565B1 (fr) 2016-05-19 2019-09-18 Innas B.V. Dispositif hydraulique
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Also Published As

Publication number Publication date
JP2009531590A (ja) 2009-09-03
US20090084258A1 (en) 2009-04-02
DE102006021570A1 (de) 2007-10-18
KR20080108078A (ko) 2008-12-11
WO2007118624A1 (fr) 2007-10-25

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