EP1174617A2 - Machine hydrostatique à pistons axiaux - Google Patents

Machine hydrostatique à pistons axiaux Download PDF

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Publication number
EP1174617A2
EP1174617A2 EP01117151A EP01117151A EP1174617A2 EP 1174617 A2 EP1174617 A2 EP 1174617A2 EP 01117151 A EP01117151 A EP 01117151A EP 01117151 A EP01117151 A EP 01117151A EP 1174617 A2 EP1174617 A2 EP 1174617A2
Authority
EP
European Patent Office
Prior art keywords
control
pressure
piston
cylinder
throttle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01117151A
Other languages
German (de)
English (en)
Other versions
EP1174617B1 (fr
EP1174617A3 (fr
Inventor
Josef Riedhammer
Erich Eckhardt
Franz-Josef Schwede
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.)
Liebherr Machines Bulle SA
Original Assignee
Liebherr Machines Bulle SA
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 Liebherr Machines Bulle SA filed Critical Liebherr Machines Bulle SA
Publication of EP1174617A2 publication Critical patent/EP1174617A2/fr
Publication of EP1174617A3 publication Critical patent/EP1174617A3/fr
Application granted granted Critical
Publication of EP1174617B1 publication Critical patent/EP1174617B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B1/2042—Valves

Definitions

  • the invention relates to a hydrostatic axial piston machine with a drum-shaped Cylinder block that is mounted on a drive or output shaft so that it cannot rotate and provided concentrically and parallel to the center line with cylinder bores is in which axially displaceable pistons are arranged, which are spherical Heads on a housing-fixed, preferably adjustable in their helix angle, Support the swashplate, with the swashplate opposite Cylinder openings such as kidney-shaped low-pressure and high-pressure control openings of a control body, between which there are reversing areas with additional holes.
  • the volumes that are decisive for the pressure build-up in the cylinder space namely the dead volume plus the stroke volume, from the swivel angle of the Swashplate, the volumes to be added to build up pressure the pressure in the high pressure control port and the available one Time interval for pressure changeover and thus depend on the speed, is an optimal pressure reversal with a constant notch in the reversal area or with the reversing areas through channels with the low-pressure and high-pressure control openings connecting channels across the entire operating range not possible.
  • the object of the invention is to provide a hydrostatic axial piston machine specified type to create, in which in the or the changeover areas located additional bores, which increase or decrease the pressure Influence the passage of the cylinder openings over the reversing areas, depending on of the operating conditions, namely the pressure, the speed and the Swivel angle of the swash plate are controlled. Furthermore, a hydrostatic Axial piston machine can be created that is simple and reliable Way even with changed operating conditions when running through Cylinder openings over the reversal areas an undesirable sudden increase or prevent pressure drops in the cylinders.
  • this object is achieved in that at least one Reversal area of the control body opens a hole through a line is connected to the high pressure side or the high pressure control opening, and that in the line a throttle controlled by the high pressure is arranged, which in the line opens a throttle opening corresponding to the high pressure.
  • a throttle controlled by the high pressure is arranged, which in the line opens a throttle opening corresponding to the high pressure.
  • About Strokes the open cylinder side the bore flows out of this under higher Pressure oil in the cylinder opening, so that the pressure in the passage through the reversal range and a continuous in the cylinder Pressure increase until the open cylinder side enters the high pressure control opening he follows. Unwanted sudden pressure increases and changes in the flow are avoided.
  • the hole expediently opens into an area of the reversing area, which faces the high pressure control opening.
  • At least one the region of a reversing area of the low pressure control opening Control body opens a hole through a line with the low pressure control opening is connected, and that in the line one controlled by the high pressure Throttle is arranged, which corresponds to the high pressure in the line Throttle opening releases.
  • the two bores are expediently located in the reversing area Pass through each cylinder opening concurrently covered by this. Conveniently, point the two holes in the reversal area or areas equal distances to the low pressure and high pressure control openings.
  • the controlled throttle from a cylindrical bore in the control body or one in the Control body-held cylinder, in which or by a compression spring loaded control piston is slidably guided, the pressure spring opposite High pressure side in the high pressure control port is that in the cylinder bore or the cylinder at an axial distance from each other to the bore of the reversing area and to the high pressure control opening or lines leading to the low-pressure control opening and that the control piston has different sizes according to its displacement Throttle openings opposite the line leading to the reversing area releases.
  • the line of the reversing area opening into the control cylinder can be through an axial groove with a changing cross section of the control piston with the the high-pressure control opening or the low-pressure control opening leading line be connected.
  • the changing cross section is due to Adapted calculations or experiences of the respective axial piston machine.
  • connection of the Control cylinder to the line leading to the reversing area from one Slit exists, which the control piston due to its displacement releases the high pressure on one side in different lengths.
  • the approved length corresponds to the respective flow cross section of the controlled Throttle, which is adapted to the respective axial piston machine.
  • control piston acted upon on one side by at least two compression spring enclosing each other of which the springs following or following the first spring are successive corresponding to the displacement of the control piston in the direction of the springs are used, that is, they load the control piston with their force.
  • the swash plate For example, with constant power and a reduced swivel angle increases the swash plate the pressure with a correspondingly reduced volume flow.
  • the pressure change and the change in the volume flow when the helix angle changes Taking into account swashplate must have a certain control characteristic with regard to the throttle opening which can be changed in cross section, which takes into account the special spring characteristics and spring characteristic.
  • the Swivel angle of the swash plate changed is also taking this change into account Throttle opening control required.
  • control piston is shifted in the control cylinder by an actuator whose Travel from a control device, for example a computer, depending of the high pressure, the speed and the swivel angle of the swash plate is determined.
  • a control device for example a computer
  • the values influencing the travel of the control piston, the for the respective axial piston machine from the variable high pressure, the variable speed and the variable swivel angle result be stored in tables (ROM) in the memory unit of the computer, so that the computer according to the respectively measured high pressure, the respectively measured Speed and the respective swivel angle of the swashplate Control piston adjusted.
  • control piston is designed as a stepped piston, the annular piston surface and the disc-shaped piston surface of the high pressure and another from one of the set helix angle of the swash plate speaking pressure are applied.
  • the helix angle of the swashplate corresponding pressure can be, for example, from the pressure in one Derive the actuating cylinder that adjusts the swash plate and is proportional to the angle adjustment the swash plate is.
  • control piston is designed as a three-stage piston, through the two ring surfaces and the central disk-shaped piston surfaces formed by each Pressures applied to the high pressure in the high pressure control port, correspond to the helix angle of the swash plate and the speed.
  • the the Pressure corresponding to the rotational speed can be achieved, for example, by one of the axial piston machines driven auxiliary pump are derived, the a speed proportional pressure generated.
  • each inlet throttle has at least two throttle cross sections on, the one choke a constant choke in the control plate and the other choke or chokes near the control surface of the control body or housed in the control body itself are, the cross section or the cross sections of the controllable chokes controlled according to the operating conditions of the axial piston machine will or can be controlled that the pressure build-up and pressure reduction in the controlled Cylinder space takes the desired course.
  • the high pressure side i.e. the high pressure control openings
  • a certain volume of the pressure oil is removed, which is then missing from the flowing pressure medium. Missing pressure medium on the high pressure side can in turn lead to undesirable ones Cause pulsations.
  • the controlled throttle Pressure oil is supplied from an external pressure oil source.
  • a control body 1 is shown schematically in FIGS. 1 and 2, of which in FIG. 1 only the control surface with the high pressure control opening 2 and the low pressure control opening 3 and those in the reversal areas between the low pressure and High-pressure control openings located throttle bores 4, 5 and 6, 7 shown are.
  • the control surface of the control body is formed by the approximately oval Openings 8 of the cylinder 9 are swept, which are shown in broken lines in FIG. 1 are.
  • the hydraulic connections of the low-pressure and high-pressure control openings 2, 3 are of a common type and are therefore not shown.
  • the throttle openings 4 to 7 have a constant cross section and form thus, as can be seen from FIG. 2, constant chokes.
  • Controlled throttle 12 One for controlling the pressure media flowing through the constant throttles Controlled throttle 12 is provided, which will be described with reference to FIG. 5.
  • a control piston 16 is arranged displaceably in the cylinder.
  • This control piston is loaded by a compression spring 17 which between the bottom of the cylinder 15 and the side of the control piston 16 facing this is clamped.
  • the opposite Side of the control piston is acted on by the high pressure, that is the pressure in the high-pressure control opening 2 of the control body 1 prevails.
  • the high pressure could also be from are derived from another location of the axial piston machine.
  • the control piston 16 is provided with an axially closed bore 20 at its ends, which communicates with radial bores or slots 21, 22.
  • the radial one Bore 21 is via line 18 and an annular space 23 with the pressure of Pressurized medium in the high pressure control opening 2.
  • the hole or preferably the slot 22 communicates with an annular space 24, from which a line 25 to the throttle opening 5 in the control surface of the control body 1 leads.
  • the piston 16 is in the cylinder bore 15 through the right piston surface acting high pressure shifted against the force of the compression spring 17, a control slot of different lengths depending on the displacement path 22 is controlled, each of the length covered by the annular space 24 of the control slot.
  • control piston 16 has an axial Provide slot that has a variable cross-section, so that accordingly the displacement of the control piston leading to the throttle opening 5 Throttle cross-sections of different sizes can be opened.
  • the controlled throttle can the volume flowing into the control time can be influenced in such a way that the desired one Pressure curve in the cylinder bore is reached. Influencing the Throttle cross section can on the relationship between that in the control openings prevailing pressure and the open throttle cross section both over the compression spring and the shape of the throttle can be reached.
  • both the Throttle openings 5 constant cross-section on the low-pressure and high-pressure control openings 2, 3 facing sides with controlled throttles 12.
  • the controlled throttles 12 are in both cases on their compression springs 17 opposite sides of the high pressure, which preferably in the form shown in dashed lines via lines from the high pressure control opening 2 is derived.
  • a special feature of the invention can be seen in the fact that the preferably oval cylinder openings over the control surfaces of the control body the cylinder opening 8 covers both throttle openings 4, 5, so that it becomes one smoothing pressure equalization comes.
  • throttle bores 5 are arranged which via the controlled throttles 12 in connection with variable throttle openings stand so that an optimal pressure equalization when the cylinder openings overflow can take place via the reversing areas.
  • control piston is a compression spring 30 acted on, which encloses a compression spring 31 of shorter length in the manner that this only on the control piston after a predetermined displacement 16 attacks and thereby changes the spring characteristic and a hyperbolic Course attacks.
  • a displacement device 33 which displaces the control piston 16 via a tappet 34, the displacement device 33 controlled by a control device, for example a computer which is a travel for the plunger 34 from the pressure of the high pressure side, the speed and the swivel angle are calculated.
  • a control device for example a computer which is a travel for the plunger 34 from the pressure of the high pressure side, the speed and the swivel angle are calculated.
  • the path of the throttle piston is controlled by a proportional magnet, d. H. the positioning force of the magnet depends on the size of the electrical applied Tension. The relationship between tension and the compression spring - Travel made.
  • This proportional magnet can be of any electrical Signals are controlled. This allows the pressure curve in the cylinder bore depending on different sizes, for example pressure, Swivel angle and speed can be influenced.
  • control piston 16 is a stepped piston executed, wherein the annular surface 36 of the stepped piston from the pressure of the high pressure side and the piston surface 37 of the piston with a smaller cross section of a liquid pressure is applied, which is the helix angle of the swash plate equivalent.
  • control piston 16 has three stages Piston formed, the annular surfaces 36 and 38 of the high pressure and one the pressure corresponding to the helix angle of the swash plate and the Face 39 of the piston section with the smallest cross section of a pressure is applied, which is proportional to the speed of the axial piston machine.
  • the controlled Throttle 12 a pressure medium via line 40 from an external pressure medium source is fed.
  • Fig. 11 shows an embodiment in which both throttle openings in the Reversal area are controlled by controlled throttles, the oil supply the throttle opening 5 facing the high-pressure control opening 2 by a external pressure oil supply.
  • all of the holes are in the two Reversal areas provided with controlled throttles, the high pressure side controlled throttles from an external pressurized oil source with pressurized Medium are supplied.
  • the supply of pressure oil from external pressure oil sources can be beneficial in certain cases. Firstly, through the external Pressure oil supply, the pulsation in the high pressure control opening can be reduced and on the other hand, the higher pressure can supply the throttle system another desired pressure characteristic in the cylinder bores can be achieved.
  • 13 and 14 show known control bodies in which the reversing areas with the adjacent low pressure and high pressure control openings connected by wedge-shaped narrowing slots or notches 50 are.
  • FIGS. 15 and 16 Known control bodies can also be seen from FIGS. 15 and 16, at which the low-pressure and high-pressure control openings with the throttle bores are connected directly by lines 51 in the reversing area.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Actuator (AREA)
  • Hydraulic Motors (AREA)
EP01117151A 2000-07-18 2001-07-13 Machine hydrostatique à pistons axiaux Expired - Lifetime EP1174617B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10034857A DE10034857A1 (de) 2000-07-18 2000-07-18 Hydrostatische Axialkolbenmaschine
DE10034857 2000-07-18

Publications (3)

Publication Number Publication Date
EP1174617A2 true EP1174617A2 (fr) 2002-01-23
EP1174617A3 EP1174617A3 (fr) 2003-05-07
EP1174617B1 EP1174617B1 (fr) 2004-11-10

Family

ID=7649293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01117151A Expired - Lifetime EP1174617B1 (fr) 2000-07-18 2001-07-13 Machine hydrostatique à pistons axiaux

Country Status (4)

Country Link
US (1) US6736048B2 (fr)
EP (1) EP1174617B1 (fr)
JP (1) JP2002070716A (fr)
DE (2) DE10034857A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2199609A3 (fr) * 2008-12-16 2012-11-28 Robert Bosch GmbH Machine à piston axial dotée d'une réduction de pulsations

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10232513B4 (de) * 2002-07-18 2014-02-06 Linde Hydraulics Gmbh & Co. Kg Pulsationsoptimierte hydrostatische Verdrängermaschine, insbesondere Axial- oder Radialkolbenmaschine
DE10232983A1 (de) * 2002-07-19 2004-02-05 Brueninghaus Hydromatik Gmbh Kolbenmaschine mit Pulsation
DE10343222A1 (de) * 2003-09-18 2005-04-14 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine der Schrägscheiben- oder Schrägachsen-Bauart
DE102004007933B3 (de) * 2004-02-18 2005-06-16 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine mit einer Vorsteuerungseinrichtung zur Dämpfung von Strömungspulsationen und Herstellungsverfahren
DE112006000312T5 (de) 2005-02-10 2007-12-13 Komatsu Ltd. Hydraulische Kolbenpumpe
GB2440155A (en) * 2006-07-18 2008-01-23 Agco Gmbh An axial piston pump or machine of the swashplate or bent axis type
US20080307956A1 (en) * 2007-06-18 2008-12-18 Sauer-Danfoss Inc. Web-less valve plate
US20100150741A1 (en) * 2008-12-17 2010-06-17 Mehta Viral S Hydraulic unit having orifice plate displacement control
DE102014208406A1 (de) * 2014-05-06 2015-11-12 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
JP6267598B2 (ja) * 2014-08-01 2018-01-24 川崎重工業株式会社 液圧回転機
US10227964B2 (en) * 2015-08-28 2019-03-12 Caterpillar Inc. Hydraulic pump port plate with variable area metering notch
DE102018218548A1 (de) * 2018-10-30 2020-04-30 Robert Bosch Gmbh Hydrostatische Kolbenmaschine
US11946462B2 (en) * 2019-12-02 2024-04-02 Danfoss Power Solutions, Inc. Hydraulic axial piston unit and method for controlling of a hydraulic axial piston unit
DE102022107860A1 (de) 2022-04-01 2023-10-05 Danfoss Power Solutions Inc. Hydraulische Axialkolbeneinheit und Verfahren zum Steuern einer hydraulischen Axialkolbeneinheit

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US3180274A (en) * 1962-06-04 1965-04-27 Francis J Sisk Silent variable delivery hydraulic pump
GB1367512A (en) * 1970-10-21 1974-09-18 Citroen Sa Hydrostatic machines with cylinder capacity variation control by distributor rotation
US5555726A (en) * 1995-03-31 1996-09-17 Caterpillar Inc. Attenuation of fluid borne noise from hydraulic piston pumps
US5572919A (en) * 1992-12-22 1996-11-12 Kabushiki Kaisha Komatsu Seisakusho Apparatus for controlling pressure in a cylinder chamber of a hydraulic pump-motor
US5634776A (en) * 1995-12-20 1997-06-03 Trinova Corporation Low noise hydraulic pump with check valve timing device
EP0953767A2 (fr) * 1998-04-27 1999-11-03 Mannesmann Rexroth AG Machine hydrostatique
EP1013928A2 (fr) * 1998-12-22 2000-06-28 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

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US3283726A (en) * 1964-12-14 1966-11-08 American Brake Shoe Co Construction for pump/motor devices
JPS6085267A (ja) * 1983-09-05 1985-05-14 Daikin Ind Ltd アキシアル・ピストン機械
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JPH05321815A (ja) * 1992-05-22 1993-12-07 Nachi Fujikoshi Corp 液圧ポンプモータ
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DE19706114C9 (de) * 1997-02-17 2014-02-06 Linde Hydraulics Gmbh & Co. Kg Vorrichtung zur Pulsationsverminderung an einer hydrostatischen Verdrängereinheit
JPH10331996A (ja) * 1997-06-03 1998-12-15 Koyo Seiko Co Ltd 可変絞り弁
DE19804374B4 (de) * 1998-02-04 2004-09-30 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit Mitteldrucköffnung
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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3180274A (en) * 1962-06-04 1965-04-27 Francis J Sisk Silent variable delivery hydraulic pump
GB1367512A (en) * 1970-10-21 1974-09-18 Citroen Sa Hydrostatic machines with cylinder capacity variation control by distributor rotation
US5572919A (en) * 1992-12-22 1996-11-12 Kabushiki Kaisha Komatsu Seisakusho Apparatus for controlling pressure in a cylinder chamber of a hydraulic pump-motor
US5555726A (en) * 1995-03-31 1996-09-17 Caterpillar Inc. Attenuation of fluid borne noise from hydraulic piston pumps
US5634776A (en) * 1995-12-20 1997-06-03 Trinova Corporation Low noise hydraulic pump with check valve timing device
EP0953767A2 (fr) * 1998-04-27 1999-11-03 Mannesmann Rexroth AG Machine hydrostatique
EP1013928A2 (fr) * 1998-12-22 2000-06-28 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2199609A3 (fr) * 2008-12-16 2012-11-28 Robert Bosch GmbH Machine à piston axial dotée d'une réduction de pulsations

Also Published As

Publication number Publication date
DE50104460D1 (de) 2004-12-16
US6736048B2 (en) 2004-05-18
EP1174617B1 (fr) 2004-11-10
US20020108489A1 (en) 2002-08-15
JP2002070716A (ja) 2002-03-08
EP1174617A3 (fr) 2003-05-07
DE10034857A1 (de) 2002-01-31

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