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
  • F04B1/24—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 inclined to the main shaft axis
• • 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
  • F03C1/0642—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 inclined on main shaft axis
• • 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
  • F03C1/0678—Control
  • F03C1/0694—Control by changing the inclination of the axis of the cylinder barrel in relation to the axis of the actuated element
• • 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
  • F04B1/2078—Swash plates
  • F04B1/2085—Bearings for swash plates or driving axles
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
  • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F04B1/26—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
  • F04B1/328—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 axis of the cylinder barrel relative to the swash plate

Definitions

• the invention relates to an axial piston machine in a bent-axis design according to the closer defined in the preamble of claim 1. Art.
• axial piston machines are used to drive a variety of hydraulically actuated devices and the conversion of torque.
• Axial piston machines are provided, for example, as hydraulic drives for hydraulically operated machines, such as excavator arms and excavator buckets, loaders of wheel loaders, telehandlers, bulldozers, load dumpers of dump trucks and the like.
• hydraulically operated machines such as excavator arms and excavator buckets, loaders of wheel loaders, telehandlers, bulldozers, load dumpers of dump trucks and the like.
• axial piston machines in travel drives such machines, the axial piston machines represent parts of hydrostatic transmission of single-wheel drives or power-split continuously variable transmissions.
• adjustable axial piston machines are preferably used in swash plate or Schrägachsenbauweise, where designed as swash plate axial piston machines are usually realized by design with a maximum adjustment angle of +/- 21 degrees. Due to the design-related limited Verstellwinkel Anlagenes swash plate machines are characterized by a low power density and therefore relatively large perform in order to provide a corresponding performance or to convert to the desired extent.
• swash plate machines also have low efficiencies, since piston elements slide on a swash plate by means of sliding blocks and the piston elements are thereby subjected to transverse forces.
• the transverse forces acting on the piston elements result in the connection area between the piston elements and the piston elements.
• elements respectively associated cylinders during operation occurring frictional forces that adversely affect the efficiency.
• leakage currents which adversely affect the volumetric efficiency of a swashplate machine arise in the region of gaps between the piston elements and the respective associated cylinders.
• Axial piston machines in Schrägachsenbauart are compared to swash plate machines with higher efficiencies operable, with conventionally executed Schrägachsenhowen a maximum adjustment angle is about 25 degrees.
• bent axis units are usually notteurschwenkbar.
• bent axis units are operated as pumps, they are usually used in open circuits. In order to be able to display a changing oil delivery direction in the area of a bent axis unit, the direction of rotation of a bent axis unit must be changed.
• Axial piston pumps are in Schrägachsenbauart without a torque leading portion and a cylinder connecting synchronous joint executed by piston elements disadvantageously transverse forces between the cylinder device and the torque leading area to be transmitted to support occurring between the cylinder device and a valve plate frictional forces can. Piston ends of the piston elements are usually trapped in calottes and transmit there the piston force in an axial force and in a circumferential force.
• bent axis units Although the efficiencies of such bent axis units are higher than the efficiencies of the above-described swash plate units, a power density of bent axis units is still below a desired range due to the constructional circumstances briefly explained below.
• bent-axis units in particular inclined-axis pumps, are usually designed with a fixed drive shaft axis and pivotably designed cylinder device.
• An oil guide between one standing housing and the pivotally running cylinder device is usually done via a sliding carriage.
• an appropriate seal In order to ensure the oil supply with the lowest possible leakage volume flows, an appropriate seal must be provided. However, the seal limits a maximum pivot angle of the cylinder device, of which a maximum displacement and thus a power density of a bent axis unit is dependent, such that a power density is low.
• the cylinder device is mounted in a pivotable yoke housing.
• the cylinder to be supplied and flowing out of the cylinder device oil is respectively removed in the region of a Jochlagerung in a complex manner a housing side trained hydraulic system or supplied to this.
• the respectively funded by piston elements in the cylinder device or sucked oil between the cylinder device or between the cylinder device and the piston elements each limited piston chambers and a yoke bearing over relatively long oil channels to lead, however, cause undesirable high pressure losses and thus deteriorate efficiency.
• bent axis units have better efficiencies than the oblique axes executed with a pivoting angle of approximately 25 degrees.
• the production costs are higher than that of the efficiency-degraded bent axis machines.
• the present invention is therefore based on the object to provide a cost-manufacturable axial piston machine in oblique axis design available, which is operable with high efficiency and is characterized by a high power density.
• the axial piston machine according to the invention in a bent-axis design is designed with a plurality of longitudinally movably guided piston elements in a rotatable cylinder device and with a region operatively connected to the piston elements and carrying a torque.
• the torque carrying area is one
• Swivel axis pivotally mounted and a displacement of the axial piston varies depending on the pivotal movement of the torque-conducting area, which an efficiency of the axial piston impairing oil ducts and manufacturing costs increasing sealing measures in the axial piston according to the invention are not provided.
• a swivel angle range of the axial piston machine according to the invention is limited by the unnecessary complicated seal to a lesser extent, thus the axial piston machine according to the invention can be executed with a higher power density than known axial piston machines.
• the torque-guiding region is a bevel gear which can be brought into engagement with a further bevel gear.
• a likewise structurally simple and cost-effective embodiment of the axial piston machine according to the invention is characterized in that the torque-guiding region is rotatably supported by a bearing pivotable about the pivot axis via a bearing axially and radially bearing means in the region preferably a pivoting movement generating device to initiate a pivoting force can.
• the pivot axis of the torque leading portion is arranged perpendicular to a rotation axis of the cylinder device and / or an axis of rotation of the torque leading portion at a displacement of the axial piston machine equal to zero in coincidence with the axis of rotation of the cylinder device.
• the axial piston machine according to the invention with a low-efficiency forced lubrication executable over which only limited areas are to be supplied with lubricating and cooling fluid.
• the axial piston according to the invention in comparison to known axial piston machines, in which rotating components are arranged completely in an oil bath, in a structurally simple manner with a higher efficiency operable.
• Housing-side hydraulic channels are in another operable with little control and regulation effort embodiment of Axialkolbenma- machine depending on the rotational movement of the cylinder device in each case engageable by the piston elements and the cylinder means limited piston chambers in operative connection.
• the axial piston machine can be embodied with a swivel angle range enabling a high power density.
• the piston elements during operation of the axial piston according to the invention are substantially free of transverse forces, whereby a high sealing effect in the region between the piston elements and the cylinder device can be ensured at the same time little effort ,
• the axial piston machine according to the invention can be operated with high efficiency since the cylinder device is connected between the valve plate and the cylinder device In the operation of the axial piston machine adjusting thin oil film with low frictional forces relative to the valve plate is rotatable.
• FIG. 1 is a highly schematic representation of an embodiment of the axial piston machine according to the invention in a bent-axis design in a first operating state.
• Fig. 2 is a representation corresponding to Fig. 1 of the axial piston machine in a second pivoted operating state of a torque conducting area.
• the axial piston machine 1 shows a functional diagram of an embodiment of an adjustable axial piston machine 1 in a bent-axis design.
• the axial piston machine 1 is designed with a plurality of piston elements 3 which are guided longitudinally movably in a rotatable cylinder device 2 and with a region 4 which is operatively connected to the piston elements 3 and carries a torque.
• the piston elements 3 are sealed in the cylinder device 2 by means of suitable seals.
• the axial piston machine 1 is presently designed as axial piston pump in a bent-axis design, which is to operate in a closed circuit.
• the cylinder device 2 is rotatably mounted about a rotation axis 5 in a housing 6, wherein the cylinder device 2 is rotatably mounted in the housing 6 via a bearing axial and radial forces bearing means 7.
• the axial forces of the cylinder device 2 are transmitted to the housing 6.
• the bearing device 7 is arranged radially between between the piston elements 3 and the cylinder device 2 limited piston chambers 8 in a favorable manner.
• the torque-guiding region 4 is designed as a bevel wheel which meshes with a further bevel gear 9 and is provided with a pivoting gear.
• Axle 10 from the zero position shown in Fig. 1 in a first in Fig. 2, which is the axial piston machine 1 from a in Fig. 1 by the arrow II marked in more detail view, shown pivoting position is pivotable.
• In the zero position of the ring gear 4 is a stroke of the piston elements 3 in the cylinder device 2 and a displacement of the axial piston machine 1 is substantially equal to zero.
• a swivel angle between the axis of rotation 5 of the cylinder device 2 and a rotation axis 1 1 of the torque-conducting region 4 corresponds in the operating state of the axial piston machine 1 illustrated in FIG. 2 substantially to approximately + 45 degrees.
• the torque leading area is 4 around the
• Swivel axis 10 from the zero position shown in Fig. 1 in a second pivot position, not shown in the drawing by a pivot angle of -45 degrees pivot.
• the torque-guiding region or the bevel gear 4 is rotatably supported by a bearing device 12 accommodating axial and radial forces in a cage 13 pivotable about the pivot axis 10, the bearing device 12 in the present case comprising a tapered roller bearing 14 and a cylindrical roller bearing 15.
• the wave-like element 17 and the synchronous steering, the speed synchronization between the ring gear 4 with the piston shoes 16 and the cylinder device 2 is provided, helps in the region between the housing side fixed valve plate 18 and the cylinder device 2 to support occurring frictional forces and to move the piston elements 3 in the cylinder device 2 substantially free of lateral forces.
• the valve plate 18 is non-rotatably operatively connected to the housing 6.
• valve plate 18 is provided as a sliding and sealing surface, wherein the oil flow between the housing 6 and the cylinder device 2 takes place via the two valve plate-side regions 21 and the hydraulic channels 20, which are kidney-shaped at least in regions.
• the hydraulic channels 26 and 27 with respect to a low pressure loss optimally executed.
• the valve-plate-side hydraulic channels 20 are alternately in operative connection with the piston chambers 8 bounded by the piston elements 3 and the cylinder device 2 as a function of the rotational movement of the cylinder device 2, for example, to supply hydraulic pressure to a desired extent to a hydraulically actuated excavator arm.
• a stroke of the piston elements 3 in the cylinder device 2 increases up to a maximum stroke value is equivalent to a maximum displacement of the axial piston machine 1.
• the axis of rotation 5 of the cylinder device 2 and close the axis of rotation 12 of the torque leading portion 4 and the ring gear an angle of 45 degrees.
• the pivot axis 10 of the ring gear 4 and also of the cage 13 is perpendicular to the axis of rotation 5 of the cylinder device 2.
• the pivot axis 10 of the ring gear 4 simultaneously corresponds to a rotation axis of the further plate wheel 9 or a shaft 22 rotatably connected thereto, which is connected to a non-illustrated mechanical transmission via a spur gear 23 and which in the present case is rotatably mounted in a main housing 24 via a likewise axial and radial forces receiving bearing means 25.
• the pivot axis 10 corresponds to the drive of the plate wheel 4 by the further ring gear 9 without affecting the power transmission over the teeth of the ring gear 4 and the other ring gear 9 even during pivoting of the cage 13 feasible.
• the spur gear 23 instead of the spur gear 23, to provide another suitable shaft connection, such as a flange connection or the like, in order to introduce a torque applied to the plate rim 4 into the mechanical gear or to transfer it from the mechanical gear to the ring gear 4 .
• a suitable shaft connection such as a flange connection or the like
• the circumferential force in the tooth engagement of the two bevel gears 4 and 9 is supported by the adjusting device of the cage 13.
• the adjusting device In addition to this circumferential force, the adjusting device must also support the not 100% balanced piston forces.
• Pivot axis of the torque-guiding area Rotary axis of the torque-carrying area. Bearing device of the torque-bearing area. Cage
• Hydraulic channel on the housing side

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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)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

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Citations (7)

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• 2011
  • 2011-05-02 DE DE102011075077A patent/DE102011075077A1/de not_active Withdrawn
• 2012
  • 2012-03-13 EP EP12709590.9A patent/EP2705250B1/de not_active Not-in-force
  • 2012-03-13 US US14/114,973 patent/US20140060317A1/en not_active Abandoned
  • 2012-03-13 CN CN201280021566.1A patent/CN103502634A/zh active Pending
  • 2012-03-13 WO PCT/EP2012/054322 patent/WO2012150069A1/de active Application Filing
  • 2012-03-13 JP JP2014508721A patent/JP2014513240A/ja active Pending
  • 2012-03-13 KR KR1020137028693A patent/KR20140022854A/ko not_active Application Discontinuation

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