EP0534067B1 - Hydrostatische Maschine mit Leckölabführung - Google Patents

Hydrostatische Maschine mit Leckölabführung Download PDF

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Publication number
EP0534067B1
EP0534067B1 EP92110949A EP92110949A EP0534067B1 EP 0534067 B1 EP0534067 B1 EP 0534067B1 EP 92110949 A EP92110949 A EP 92110949A EP 92110949 A EP92110949 A EP 92110949A EP 0534067 B1 EP0534067 B1 EP 0534067B1
Authority
EP
European Patent Office
Prior art keywords
hydrostatic machine
oil
pump
machine according
connection
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.)
Expired - Lifetime
Application number
EP92110949A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0534067A2 (de
EP0534067A3 (en
Inventor
Norbert Rückgauer
Werner Hörmann
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 EP0534067A2 publication Critical patent/EP0534067A2/de
Publication of EP0534067A3 publication Critical patent/EP0534067A3/de
Application granted granted Critical
Publication of EP0534067B1 publication Critical patent/EP0534067B1/de
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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/04—Draining

Definitions

  • the invention relates to a hydrostatic machine, in particular an axial piston machine, with a housing, the interior of which houses an engine and comprises a leakage oil-receiving leakage oil chamber which is connected to the tank via a leakage oil connection, a pumping device for sucking out leakage oil from the leakage oil connection and the tank the leak oil chamber is arranged.
  • the internal leakage occurring during operation is responsible for the fact that the leakage oil space is constantly filled with leakage oil via a with the leakage oil connection connected drain line to the tank is discharged. Due to the flow resistance in this leakage oil line, the leakage oil in the leakage oil chamber is under pressure, so that the engine parts rotating in it cause correspondingly high splashing losses.
  • the pump device of the known hydrostatic machine is, however, rigidly connected to the drive shaft of this machine.
  • the leakage oil suction pump is thus also continuously in operation when the hydrostatic machine assigned to it is in operation, its speed depending linearly on the speed of the assigned hydrostatic machine.
  • the leakage oil suction pump is thus continuously operated by the machine, although suctioning of the leakage oil is only necessary if the hydrostatic machine reaches such a high speed that the splashing losses caused by the immersion of the engine parts in the leakage oil are no longer negligible. This leads to unnecessary energy losses, since the pump power required to extract the leak oil is lost even in the low speed range, in which no significant splash losses occur, the output power of the hydrostatic machine is lost.
  • the immersion of the engine parts in the leak oil can be quite advantageous, because an improved lubrication of the engine parts can be achieved.
  • the present invention is therefore based on the object of improving the efficiency in the case of leak oil extraction on a hydrostatic machine.
  • a speed sensor arranged on the shaft of the hydrostatic machine, which is set to the speed of the hydraulic motor at which splashing losses due to its engine parts rotating in the leakage oil are no longer negligible, and a valve connected to the speed sensor that is in a working position switches as soon as the hydrostatic machine reaches the set speed, so that the pump device sucks the leak oil out of the leak oil chamber.
  • the critical speed of the hydraulic motor provided for generating a control signal must be determined empirically in individual cases. Below this critical speed, the splashing losses of the engine parts rotating in the leakage oil play a subordinate role, so that the additional work to be carried out for sucking off the leakage oil would not be offset by a corresponding reduction in the splashing losses.
  • the efficiency of the hydrostatic machine is therefore improved if the drainage of the leakage oil only begins in a speed range in which the splashing losses have a demonstrable influence on the dynamics of the hydrostatic machine. In the subcritical speed range, on the other hand, the engine parts immersed in the leak oil can improve the lubrication of the slewing gear.
  • the pump device according to the invention can comprise either a jet pump or a displacement pump.
  • a jet pump When using a jet pump, it is advantageous to connect its propellant connection to a propellant source which generates a volumetric flow corresponding to the volumetric flow of the hydrostatic machine.
  • this is an auxiliary pump assigned to the hydrostatic machine.
  • a flushing oil connection is also favorable, which leads to bearings for the engine via a duct system for the purpose of supplying them with lubricating oil and is connected to a valve device, which has two switch positions for switching the flushing oil supply to the hydrostatic machine on and off.
  • valve device for actuating the water jet pump and the valve device for releasing the flushing oil connection in a 2-way valve, which is arranged between the propellant source for the jet pump and the flushing oil connection of the hydrostatic machine. In this way, both the leak oil extraction and the flushing oil supply to the hydrostatic machine are switched on or off simultaneously.
  • the pump device advantageously comprises a valve device which is designed as a 3-way valve which is arranged in a leak oil line connecting the leak oil connection of the hydrostatic machine to the tank and which connects the leak oil line in one switching position to the suction connection of the displacement pump and in the other switching position connected to the tank.
  • the pump device comprises a throttling control valve for controlling the volume flow generated by the displacement pump designed as a constant pump and driven at a constant speed depending on a control parameter.
  • a throttling control valve connected to a flushing connection of the hydrostatic machine can be provided for controlling the flushing oil supply to the hydrostatic machine as a function of a control parameter.
  • the hydrostatic transmission shown in the drawing comprises a hydraulic pump 1 driven by a diesel engine, not shown, in an axial piston design with two delivery directions and variable delivery volume, a hydraulic motor in an axial piston design with two flow directions and constant displacement, an auxiliary pump 2 mechanically connected to the hydraulic pump 1 in an axial piston design with one Current direction and constant delivery volume as well as the control of the leakage oil discharge according to the invention.
  • the hydraulic pump 1 and the hydraulic motor are connected to one another in a closed circuit via two working pressure lines 3, 4.
  • a line 5 with two check valves 6 connects both working pressure lines 3, 4.
  • the auxiliary pump 2 is connected to the tank 9 via a line 7 and a filter 8. It serves as a feed pump and is connected via a feed line 10 to line 5, into which it opens between two check valves 6. Both check valves 6 block in the direction of this junction.
  • a pressure relief valve 11 is connected to the feed line 10 to secure the maximum feed pressure and leads via a relief line 12 to the tank 9.
  • a leakage oil connection of the hydraulic pump 1 is connected via a line 13 to the relief line 12.
  • the hydraulic motor is shown in FIGS. 4 and 5 in two different configurations and each comprises a cylindrical housing 14, in the interior of which an engine is rotatably supported by means of bearings 15.
  • the hydraulic motor shown in FIG. 4, designated by the reference numeral 16, is a swashplate motor of conventional construction, the swashplate 17 of which is connected to the housing 14 in the region of its one end wall and its rotation Engine comprises a drive shaft 18 which is rotatably mounted with the help of the bearings 15 in the swash plate 17 and the opposite end wall of the housing, a cylinder block 19 arranged non-rotatably thereon with pistons 21 which can be reciprocated in corresponding axial bores 20, and sliding shoes 22 via which the pistons 21 support on the swash plate 17.
  • the bearings 15 are connected to a flushing oil connection 24 in the cylinder wall of the housing 14 via a channel system 23 for the purpose of supplying lubricating oil.
  • the hydraulic motor shown in FIG. 5, designated by the reference numeral 25, is designed as an oblique-axis motor of conventional construction, which differs in principle from the hydraulic motor 16 according to FIG on the housing-cylinder wall rotatably mounted drive shaft 18 includes the swash plate 17, which is designed as a drive shaft flange and on which the cylinder block 19 with its pistons 21 and also with a non-rotatably arranged central pin 26 is supported directly, that is, without the interposition of sliding shoes .
  • the part of the housing interior that is not filled by the respective engine serves as a leak oil chamber 29 for receiving the leak oil that occurs during operation of the respective hydraulic motor 16 or 25.
  • the leak oil chamber 29 is connected to the tank 9 via a leak oil connection 30 and a further leak oil line 31.
  • Both hydraulic motors 16, 25 are provided for horizontal installation; the leak oil port 30 is formed in the housing cylinder wall at its lowest point.
  • the housing 14 has a vent connection (only shown schematically in FIGS. 1 to 3), which leads via a vent line 32 to a vent valve 33 which can be actuated in a manner not shown.
  • the hydrostatic transmission according to FIG. 1 comprises the hydraulic motor 16 shown in FIG. 4 and a jet pump 34 of conventional construction with a housing in which a nozzle 35 and a diffuser 36 aligned thereon are arranged.
  • the housing is provided with a propellant connection aligned with the nozzle 35, a pressure medium connection aligned with the diffuser 36 and a suction connection opening into the space between the nozzle 35 and the diffuser 36.
  • the latter is connected via a first line section 37 of the leak oil line 31 to the leak oil connection 30 of the hydraulic motor 16.
  • a second line section 38 the leak oil line 31 connects the pressure connection of the jet pump 34 to the tank 9.
  • a propellant line 39 leads from the propellant connection of the jet pump 34 to a 2/2-way valve 43, which is used to switch the jet pump on and off.
  • the auxiliary pump 2 is used as the blowing agent source.
  • the hydraulic pump 1 can also be used as a source of propellant.
  • the directional control valve 43 is held by a spring 46 in the rest position shown in FIG. 1, in which both connections are blocked. It is transferred to the working position by electromagnetic actuation, in which both connections are connected to each other.
  • the control of its electromagnet takes place via a signal line 47 by means of an electrical signal which is generated by a speed sensor 48 arranged on the output shaft of the hydraulic motor 16.
  • This speed sensor 48 is set so that the directional control valve 43 switches to the working position when a critical speed of the hydraulic motor is reached, at which the splashing losses in the hydraulic motor 16 are no longer negligible, so that propellant is supplied from the feed line 10 to the jet pump 34.
  • the outlet of the 2/2-way valve 43 is also connected to the flushing oil connection 24 of the hydraulic motor 16 via a flushing oil line 44 provided with a throttle 45.
  • a flushing oil line 44 provided with a throttle 45.
  • the hydrostatic transmission according to FIG. 2 has the same structure as that according to FIG. 1.
  • the pump device here comprises a displacement pump 50 driven by a drive motor 49 at a constant speed, for example in an axial piston design with a delivery direction and constant delivery volume, and a 3/2-way valve 51 which is arranged between this displacement pump 50 and the hydraulic motor 25 used here.
  • a first connection of this directional control valve 51 leads via the first line section 37 of the leak oil line 31 to the leak oil connection 30 of the hydraulic motor 25.
  • a second connection is connected via a line section 52 to the suction connection of the displacement pump 50, the pressure connection of which via the second line section 38 of the leak oil line 31 to the tank 9 leads.
  • a bypass line 53 bypassing the displacement pump 50 connects the third connection of the 3/2-way valve 51 to the second line section 38 of the leakage oil line 31 3/2-way valve 51 is held in the rest position shown in FIG. 2 by a spring 54, in which the connection to the displacement pump 50 is blocked and the two remaining connections are connected to one another. It is transferred to the working position by electromagnetic actuation, in which the connection to the bypass line 53 is blocked and the two remaining connections are connected to one another.
  • the control of the electromagnet takes place in the same manner, already described in connection with FIG. 1, via a signal line 55, which is connected to the speed sensor 48 arranged on the output shaft of the hydraulic motor 25.
  • the function of the pump device designed as a displacement pump 50 is as follows:
  • the speed sensor 48 is set to the speed of the hydraulic motor 25 at which the churning losses due to its engine parts 17, 18, 19, 21 rotating in the leak oil are no longer negligible. Below this set speed, the 3/2-way valve 51 is in its rest position, so that the leak oil chamber 29 of the hydraulic motor 25 is relieved via the bypass line 53 to the tank 9.
  • the speed sensor 48 emits an electrical signal and switches the 3/2-way valve 51 into the working position, so that the displacement pump 50, driven by the drive motor 49 at a constant speed, releases the leakage oil sucks from the leak oil chamber 29.
  • the delivery capacity of the displacement pump 50 is designed so that even at the highest speed of the hydraulic motor 25, a leakage oil level in the leakage oil chamber 29 below the rotating engine parts 17, 18, 19, 21 is set and in this way over the entire operating range of the hydraulic motor 25 splashing losses are avoided will.
  • the lubricating oil supply to the bearings 15 is ensured in the hydraulic motor 16 used here in that pressure oil flows out of the internal oil circuit after lubrication of the bearings 15 into the leak oil chamber 29 and is extracted as part of the leak oil.
  • the hydrostatic transmission according to FIG. 3 differs from that according to FIG. 2 in otherwise the same construction in that instead of the hydraulic motor 25, the hydraulic motor 16 and the 2/2-way valve 43 arranged in the flushing oil line 44 and connected to the speed sensor 48 via the signal line 47 1 and the 3/2-way valve in the leak oil line 31 is designed as a throttling control valve 56 with intermediate positions.
  • the speed sensor 48 is set to the critical speed of the hydraulic motor 16 which causes the beginning of a lack of lubricating oil supply to the bearings 15.
  • the 2/2-way valve 43 is switched to the working position and thus the flushing oil supply to the hydraulic motor 16 for the purpose of supplying the bearings 15 with lubricating oil set.
  • control valve 56 begins to open, so that the displacement pump 50 sucks a leakage oil flow which is proportional to the control valve opening cross section set from the leakage oil chamber 29 of the hydraulic motor 16.
  • the control valve 56 is designed in such a way that an approximately identical leakage oil level in the leakage oil chamber 29 below the rotating engine parts 18, 19, 21, 22 is maintained over the entire speed range of the hydraulic motor 16. If, at the critical speed of the hydraulic motor 16 to which the speed sensor 48 is set, there are already no negligible splash losses in the hydraulic motor 16, the control valve 56 can be controlled by a second speed sensor set to the lower speed required to avoid the splash losses.
  • the displacement pump 50 can also be either a variable displacement pump driven with a constant or variable speed, which, by changing the speed or the delivery volume, enables direct control of the leakage oil flow without control valve 56.
  • a volume flow / voltage converter can also be used.
  • the 2-way valve 43 or 57 and / or the 3-way valve 51 or 56 can be designed or controlled in such a way that they switch on or interrupt the leakage oil extraction and, if necessary, the flushing oil supply, independently of the control parameters.
  • the hydraulic pump 1 can also be connected to the pump device for the hydraulic motor or to a separate pump device for sucking off the leak oil.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Gearings (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP92110949A 1991-08-28 1992-06-29 Hydrostatische Maschine mit Leckölabführung Expired - Lifetime EP0534067B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4128615A DE4128615C1 (fi) 1991-08-28 1991-08-28
DE4128615 1991-08-28

Publications (3)

Publication Number Publication Date
EP0534067A2 EP0534067A2 (de) 1993-03-31
EP0534067A3 EP0534067A3 (en) 1994-05-25
EP0534067B1 true EP0534067B1 (de) 1997-10-22

Family

ID=6439351

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92110949A Expired - Lifetime EP0534067B1 (de) 1991-08-28 1992-06-29 Hydrostatische Maschine mit Leckölabführung

Country Status (3)

Country Link
EP (1) EP0534067B1 (fi)
JP (1) JP3485585B2 (fi)
DE (2) DE4128615C1 (fi)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012012973A1 (de) 2012-06-29 2014-04-24 Robert Bosch Gmbh Hydrostatische Maschine mit Leckageölabführung

Families Citing this family (21)

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Publication number Priority date Publication date Assignee Title
DE4215869C2 (de) * 1992-05-14 1996-01-11 Hydromatik Gmbh Hydrostatische Maschine mit Leckölabführung
DE4420942C2 (de) * 1993-08-17 1999-12-02 Minster Machine Co Ölkontrollsystem für eine mechanische Presse
DE4414509C1 (de) * 1994-04-26 1995-10-19 Sauer Sundstrand Gmbh & Co Verfahren zur Leckflüssigkeitsentfernung aus dem Gehäuse einer hydrostatischen Maschine sowie mit dem Verfahren arbeitende hydrostatische Maschine
DE29503060U1 (de) * 1995-02-23 1995-04-06 Brueninghaus Hydromatik GmbH, 89275 Elchingen Axialkolbenmaschine
US5984315A (en) * 1996-10-09 1999-11-16 Denison Hydraulics Inc. Reclamation system for a hydraulic pump system
DE19829060B4 (de) * 1998-06-29 2007-01-04 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit Rückstaueinrichtung im Schmierkanal
FI107075B (fi) * 2000-02-28 2001-05-31 Ideachip Oy Insinoeoeritoimist Hydraulimoottorin vuotoöljyn palautuslaite
FI112528B (fi) * 2001-11-05 2003-12-15 Ideachip Oy Menetelmä ja laite hydraulimoottorin vuotoöljyn palauttamiseksi
DE102007022022A1 (de) * 2007-05-08 2008-11-13 Claas Selbstfahrende Erntemaschinen Gmbh Hydrostatische Maschine und diese verwendender Wandler
EP1990100B1 (de) * 2007-05-10 2009-09-16 BAUER Maschinen GmbH Baumaschine zum Erzeugen von Schwingungen
DE202008001060U1 (de) * 2008-01-24 2009-01-08 Stehr, Jürgen Hydraulische Antriebsvorrichtung
DE102009048099B4 (de) 2009-10-02 2013-09-26 Sauer-Danfoss Gmbh & Co. Ohg Hydraulisches System mit Leckageölabführung
DE102011102451B4 (de) 2011-05-24 2022-02-17 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem
JP5891064B2 (ja) * 2012-02-22 2016-03-22 Ｋｙｂ株式会社 液圧モータ
DE102012021843A1 (de) * 2012-10-26 2014-04-30 Hydac Filtertechnik Gmbh Hydrauliksystem mit zumindest einer hydrostatischen Verdrängereinheit
DE102013108407A1 (de) 2013-08-05 2015-02-05 Linde Hydraulics Gmbh & Co. Kg Hydrostatische Axialkolbenmaschine
DE102014210774B4 (de) 2014-06-05 2020-03-26 Danfoss Power Solutions Gmbh & Co. Ohg Hydraulischer Antrieb mit einer verstellbaren hydraulischen Axialkolbenmaschine in Dry-Case Bauweise
DE102014212600B4 (de) * 2014-06-30 2019-04-25 Danfoss Power Solutions Gmbh & Co. Ohg Integrierte Schmierpumpe
IT201800010097A1 (it) 2018-11-07 2020-05-07 Seppi M Ag S P A Sistema per l’azionamento di una testa di trinciatura o simile mediante un motore idraulico e kit per la modifica di un motore idraulico
EP3745002A1 (en) 2019-05-31 2020-12-02 Dana Motion Systems Italia S.R.L. Hydrostatic transmission system
DE202019005783U1 (de) 2019-05-31 2022-01-24 Dana Motion Systems Italia S.R.L. Hydrostatisches Getriebesystem

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US2452704A (en) * 1943-08-07 1948-11-02 Sundstrand Machine Tool Co Hydraulic transmission and control
US3877224A (en) * 1973-12-21 1975-04-15 Caterpillar Tractor Co Single pump hydrostatic transmission control and supply system
DE2909878C2 (de) * 1979-03-14 1982-12-23 Carl Schenck Ag, 6100 Darmstadt Vorrichtung zur Abführung des Leckflusses eines hydraulischen Lagermediums
DE2931641A1 (de) * 1979-08-01 1981-02-05 Mannesmann Ag Hydrostatischer axialkolbenmotor in schraegachsenbauweise, insbesondere fuer fahrgetriebe
DE3638890A1 (de) * 1986-07-31 1988-02-04 Hydromatik Gmbh Axial-kolbenmaschine mit einer einrichtung zum spuelen des kreislaufs

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012012973A1 (de) 2012-06-29 2014-04-24 Robert Bosch Gmbh Hydrostatische Maschine mit Leckageölabführung

Also Published As

Publication number Publication date
JP3485585B2 (ja) 2004-01-13
DE4128615C1 (fi) 1993-01-14
DE59208983D1 (de) 1997-11-27
EP0534067A2 (de) 1993-03-31
JPH05202842A (ja) 1993-08-10
EP0534067A3 (en) 1994-05-25

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