EP2592273A2 - Agencement de pompe hydraulique - Google Patents

Agencement de pompe hydraulique Download PDF

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Publication number
EP2592273A2
EP2592273A2 EP12185270.1A EP12185270A EP2592273A2 EP 2592273 A2 EP2592273 A2 EP 2592273A2 EP 12185270 A EP12185270 A EP 12185270A EP 2592273 A2 EP2592273 A2 EP 2592273A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic pump
pump
hydraulic
inlet
transmission
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Withdrawn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
EP12185270.1A
Other languages
German (de)
English (en)
Other versions
EP2592273A3 (fr
Inventor
Günther Mair Am Tinkhof
Manuel Thiel
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.)
Walterscheid GmbH
Original Assignee
GKN Walterscheid 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 GKN Walterscheid GmbH filed Critical GKN Walterscheid GmbH
Publication of EP2592273A2 publication Critical patent/EP2592273A2/fr
Publication of EP2592273A3 publication Critical patent/EP2592273A3/fr
Withdrawn legal-status Critical Current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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms

Definitions

  • the invention relates to a hydraulic pump arrangement which has a hydraulic pump with two flow directions, the hydraulic pump having a first hydraulic connection and a second hydraulic connection.
  • the hydraulic pump arrangement is designed such that it promotes independent of direction of rotation, that is, in both possible directions of flow, hydraulic fluid through an outlet.
  • Such a hydraulic pump arrangement is known from the DE 10 2010 010804 A1 known.
  • the hydraulic pump disclosed therein is arranged in a housing flange part of a transmission, wherein the housing flange part covers a recess of the transmission housing.
  • the Gezzauseflanschteil an axially projecting extension, in which a plurality of modules of the hydraulic pump are arranged axially one behind the other.
  • bores and valves are also provided, which make it possible to promote the hydraulic fluid independent of direction of rotation.
  • Object of the present invention is to provide a special simple structure for a rotationally independent hydraulic interconnection of the hydraulic pump assembly.
  • the invention is achieved by a hydraulic pump arrangement, which comprises a hydraulic pump with two flow directions, wherein the hydraulic pump has a first hydraulic connection and a second hydraulic connection. Furthermore, the hydraulic pump arrangement comprises a first inlet and a first outlet, which are both connected to the first hydraulic connection. A second inlet and a second outlet are connected to the second hydraulic port, wherein a return lugging valve is arranged in each inlet and in each start-up.
  • the check valves in the inlets are designed to open in the direction of the respective hydraulic connection.
  • the check valves in the processes are designed to close in the direction of the respective hydraulic port. If the hydraulic pump is now operated in a direction in which the suction side is at the first hydraulic connection and the pressure side at the second hydraulic connection, the check valve opens in the first inlet, with the non-return valve closing in the first outlet since this closes in the direction of the first hydraulic connection is. Thus, hydraulic fluid is sucked in from the first inlet. On the pressure side, ie at the second hydraulic connection, the check valve opens in the first sequence. The check valve in the second inlet closes, since this is only in the direction of the second hydraulic port opening and thus closed by the hydraulic pressure against this direction.
  • the two processes are connected to a common outlet line, so that the hydraulic pump arrangement, in spite of the two processes, has a single outlet line and a single outlet port.
  • the hydraulic pump is a gear pump, a vane pump or a piston pump.
  • the object is further achieved by a transmission with a hydraulic pump arrangement mentioned above, wherein the inlets connected to an oil sump of the transmission are.
  • oil can be passed from the oil sump of the transmission to lubrication points of the transmission or to other components to be lubricated.
  • the hydraulic pump is driven by a drive shaft of the transmission, wherein the drive shaft of the transmission comprises at least one gear, that the transmission has a gear housing with a housing bottom, wherein in the housing bottom of the oil sump is arranged that in the housing bottom a receiving chamber for receiving the gear of the drive shaft is provided, wherein the receiving chamber divides the oil sump into a first sump chamber and a second sump chamber, and that the first supply line of the hydraulic pump assembly to the first sump chamber and the second supply line of the hydraulic pump assembly is connected to the second sump chamber.
  • the two sump chambers can be connected to one another via a connecting channel.
  • the receiving chamber for the gear of the drive shaft is required because for a compact design, the gear of the drive shaft must be arranged as close to the lower gear bottom of the gear housing. However, this would mean that without a receiving chamber, the gear of the drive shaft dips into the oil of the oil sump and this would spin by turning it up. In this case, there is the danger that air is sucked through the oil pump by the fluid stirred up. To avoid this, the receiving chamber should be provided, which extends to the level of the oil sump or to below the oil level of the oil sump.
  • the oil which runs down to lubricate the gears of the transmission due to gravity, will thus flow partly directly into the oil sump but also into the receiving space.
  • the oil is then thrown by rotation of the gear of the drive shaft upwards and preferably thrown over a wall of the receiving chamber to an outer wall of the transmission housing, from where the oil continues to flow directly into the oil sump.
  • no gearwheel of the gearbox submerges, so that there is a calming of the oil and there is no danger that air is sucked by the hydraulic pump assembly.
  • the hydraulic pump preferably has a pump housing, which is detachably connected to the transmission housing.
  • a pump housing which is detachably connected to the transmission housing.
  • the pump housing may also be part of the transmission housing, e.g. in the form of a housing extension.
  • the pump housing may have two inlet openings which are connected to holes leading to the sump chambers in the transmission housing, wherein the check valves of the inlets sit in the bores of the transmission housing.
  • the hydraulic pump may be modular and include an inlet module, a pump module and an outlet module, which are each releasably connected to each other.
  • inlet module connecting channels are provided as part of the inlets, which extend from inlets to the hydraulic pump.
  • the hydraulic pump in particular the gears of a gear pump, is provided.
  • outlet module connecting channels are provided as part of the processes that extend from the hydraulic pump to a common outlet of the processes.
  • the pump modules are not part of the transmission or the gear housing, no special castings must be provided, which must be adapted to the different pump capacities.
  • the individual modules are each sealed to the outside or sealed so that they represent their own housing. Depending on the pump capacity, the entire hydraulic pump consisting of the individual modules will be correspondingly different in length.
  • a pump drive shaft For driving the hydraulic pump, a pump drive shaft is provided, which is guided by the pump module through the inlet module.
  • the pump drive shaft is guided through a bore in the transmission housing and is releasably drive-connected within the transmission housing with a drive shaft of the transmission.
  • FIG. 1 schematically the hydraulic interconnection of a hydraulic pump assembly 1 according to the invention is shown to achieve a direction of rotation independent pumping action.
  • the hydraulic pump arrangement 1 comprises a hydraulic pump 2 in the form of a gear pump with a first hydraulic connection 3 and a second hydraulic connection 4.
  • the first hydraulic connection 3 is connected to a first inlet 5 and a first outlet 6.
  • the second hydraulic port 4 is connected to a second inlet 7 and a second outlet 8.
  • a check valve 9, 10, 11, 12 is arranged in each case.
  • the two inlets 5, 7 are connected either via a common supply line or separately with an oil sump 13 or an oil reservoir.
  • each outlet 6, 8 may also be provided with separate outlet lines.
  • the check valve 9 in the first inlet 5 opens in the direction of the first hydraulic port 3 and closes in the direction of the oil sump 13.
  • the check valve 11 in the second inlet 7 opens to the second hydraulic port 4 and closes in the direction of the oil sump 13.
  • the check valve 10 in the second outlet 8 opens to the outlet line 14 and closes in the direction of the second hydraulic connection 4.
  • the check valve 12 of the first outlet 6 opens in the direction of the outlet line 14 and closes in the direction of the first hydraulic connection 3.
  • both check valves 10, 12 close both processes 6, 8 respectively in the direction of the hydraulic pump 4 and open in the direction of the outlet 14th
  • first direction of rotation hydraulic fluid is pumped from the first hydraulic connection 3 to the second hydraulic connection 4.
  • the first hydraulic connection 3 thus represents the suction side and the second hydraulic connection 4 the pressure side.
  • a negative pressure arises at the first hydraulic connection 3, which opens the check valve 9 of the first inlet 5 in the direction of the first hydraulic connection 3.
  • the check valve 12 of the first drain 6 is closed due to the negative pressure at the first hydraulic port 3.
  • the check valve 11 of the second drain 8 in the direction of the hydraulic pump 2 is closed.
  • the check valve 11 is opened in the second inlet 7 in the direction of the second hydraulic connection 4, so that hydraulic oil is conveyed from the oil sump 13 via the second inlet 7 to the second hydraulic connection 4.
  • the check valve 9 of the first inlet 5 is closed due to the overpressure in the direction of the oil sump 13.
  • the check valve 13 of the first outlet 6 is opened in the direction of the outlet line 14, so that the hydraulic fluid is conveyed from the first hydraulic connection 3 further via the first start 6 to the outlet line 14.
  • oil is conveyed either from the first inlet 5 to the second inlet 8 or from the second inlet 7 to the first outlet 6. In both directions of rotation, however, it is ensured that the oil is conveyed from the oil sump 12 to the outlet line 14. Thus, oil is always conveyed regardless of the driving direction of rotation of the hydraulic pump 2.
  • FIG. 2 shows a partial cross-section through a gear 15 with a gear housing 16.
  • a drive shaft 18 is rotatably mounted with a gear 24, among other waves, which is led out of the gear housing 16 sealed.
  • the drive shaft 18 is designed as a hollow shaft, wherein a drive pin 19 is inserted into the hollow shaft drive shaft 18.
  • the drive pin 19 is used to connect the drive shaft 18 with a drive unit for driving the transmission 15. This is preferably the PTO of a tractor, which is connected via a hinge shaft with the drive pin 19.
  • the gear housing 16 On the drive pin 19 opposite side, the gear housing 16 has a bore 20 which is closed by the hydraulic pump assembly 1.
  • the hydraulic pump assembly 1 is flanged to the transmission housing 16 via fastening screws 17.
  • the hydraulic pump assembly 1 has a pump drive shaft 21 for driving the hydraulic pump 2.
  • the pump drive shaft 21 is inserted through the bore 20 in the interior of the transmission housing 16, where it via a shaft-hub connection 22 directly to the drive shaft 18 is drive connected.
  • the hydraulic pump 2 is directly driven by the drive shaft 18 of the transmission 15 and thus directly from the drive 15 driving the drive unit.
  • the transmission housing 16 has a transmission bottom 23, in which the oil sump 13 is formed. In the oil sump 13, the oil is collected and has within a receiving chamber 63 (s. FIG. 7 ) to an oil level 25, which is indicated by the broken line.
  • FIGS. 3 to 6 show the hydraulic pump assembly 1 and its items in detail and will be described together below.
  • the hydraulic pump arrangement has a modular design and has an inlet module 26, a pump module 27 and an outlet module 28.
  • the individual modules 26, 27, 28 are connected via dowel pins 29, 30 and connecting screws 31, 32 with each other.
  • the FIG. 4 shows a cross section of the pump module 27.
  • the hydraulic pump 2 is arranged in the form of a gear pump with a first gear 35 and a second gear 36, wherein the two gears 35, 36 mesh with each other.
  • the hydraulic pump 2 is designed as a conventional gear pump.
  • the first hydraulic connection 3 and the second hydraulic connection 4 are formed in the pump module 27.
  • the first gear 35 is drivingly connected to the pump drive shaft 21 and thus constitutes the driven gear 25.
  • the second gear 26 is driven via the first gear 25 and is supported via a bearing shaft 37, the bearing shaft 37 held in the inlet module 26 and in the outlet module 28 or stored.
  • FIG. 5 shows a plan view of the inlet module 26.
  • a first inlet opening 33 is provided, which is aligned with a first bore in the transmission housing 16 of the transmission 15 and thus hydraulically connected thereto.
  • the first inlet opening 33 is connected via a connecting channel in the form of a first Bore 38 is connected to a first outlet opening 39, wherein the first outlet opening 39 is aligned with the first hydraulic port 3 of the pump module 27 and is hydraulically connected thereto.
  • the first inlet opening 33, the first bore 38 and the first outlet opening 39 are part of the first inlet 5 according to FIG FIG. 1 ,
  • the check valve 9 of the first inlet 5 is located in the first bore of the transmission housing 16, which is also part of the first inlet 5.
  • the inlet module 26 comprises a second opening 34, which is connected via a connecting channel in the form of a second bore 40 with a second outlet opening 41.
  • the second inlet opening is aligned with a second bore of the transmission housing 16 and is thus hydraulically connected thereto.
  • the second outlet opening 41 is aligned with the second hydraulic port 4 of the pump module 27, and the hydraulic pump 2 and is thus connected to this hydraulically.
  • the second inlet opening 34, the second bore 40 and the second outlet opening 41 are part of the second inlet 7 according to FIG FIG. 1 , wherein the check valve 11 is disposed in the second bore of the transmission housing 16, which are also part of the second inlet 7.
  • a plurality of connecting holes 44, 45, 46, 47 are further provided, which receive the dowel pins 29, 30 and the connecting screws 31, 32.
  • these connecting screws further screws, not shown, are provided.
  • fastening bores 48, 49 are provided on the inlet module 26 through which the fastening screws 17 (FIG. FIG. 2 ) can be passed in order to flange the inlet module 26 to the transmission housing 16 can.
  • a through bore 42 serves to pass the pump drive shaft 21 into the transmission housing 16.
  • a bearing bore 43 serves to receive the bearing shaft 37.
  • FIG. 6 shows a cross section through the outlet module 28.
  • This has a first Inlet opening 50, which is hydraulically connected to a connecting channel in the form of a first bore 52 which extends from the outside to the first inlet opening 50.
  • the first inlet opening 50 is aligned with the first hydraulic port 3 of the pump module 27.
  • the check valve 10 according to FIG. 1 arranged.
  • the first inlet opening 50, and the first bore 52 are part of the first outlet 8 according to FIG FIG. 1
  • the outlet module 28 comprises a second inlet opening 21, which is hydraulically connected to a connecting channel in the form of a second bore 53.
  • the second bore 53 is identical to the first bore 52 and formed parallel to this.
  • the check valve 10 sits in accordance FIG. 1 ,
  • the second inlet port 51 is aligned with the second hydraulic port 4 of the hydraulic pump 2 in the pump module 27.
  • the second inlet port 51 and the second bore 53 are part of the second flow 8 according to FIG FIG. 1 ,
  • the two holes 52, 53 are hydraulically connected to a transverse to this outlet line 54 in the form of a bore.
  • the first bore 52 and the second bore 53 traverse the outlet line 54.
  • the openings of the bores 52, 53 at the inlet openings 50, 51 opposite ends are closed by blind plugs 56, 57.
  • the outlet conduit 54 opens into an outlet opening 55.
  • the outlet module 28 comprises bearing bores 58, 59 for receiving the pump drive shaft 21 and the bearing shaft 37.
  • a connecting bore 60 is shown, in which one of the connecting screws 32 can be screwed.
  • FIG. 7 is a cross section of the gear housing 16 in the region of the oil sump 13 is shown.
  • two inner housing walls 61, 62 extend from the housing bottom 23 directed upward and form a receiving chamber 63 for receiving the gear 24 of the drive shaft 18.
  • the receiving chamber 63 is open at the top to allow a tooth engagement of the gear 24 with another gear 64 of the transmission.
  • two sump chambers 67, 68 are formed, in which the oil is collected, the oil levels are indicated by the dashed lines 69, 70.
  • Oil that flows into the receiving chamber 63 is thrown upwards by the gear 24 of the drive shaft 18, so that it is thrown over the inner housing walls 61, 62 and then can flow into the sump chambers 67, 68.
  • the receiving chamber 63 and in the sump chambers 67, 68 set different oil levels, which also vary in time. These serve as calming chambers in order to avoid suction of air into the hydraulic pump arrangement.
  • each of the sump chambers 67, 68 each have a bore 72, 73 can be seen, which are connected to the inlet openings of the hydraulic pump assembly and in which the check valves 9, 11 of the inlets 5, 7 sit.
  • a connecting channel 71 for connecting the two sump chambers 67, 68 is provided, which extends transversely to the drive shaft 18 and in FIG. 2 is recognizable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP12185270.1A 2011-11-10 2012-09-20 Agencement de pompe hydraulique Withdrawn EP2592273A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011055194.8A DE102011055194B4 (de) 2011-11-10 2011-11-10 Hydraulikpumpenanordnung

Publications (2)

Publication Number Publication Date
EP2592273A2 true EP2592273A2 (fr) 2013-05-15
EP2592273A3 EP2592273A3 (fr) 2013-12-18

Family

ID=46963530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12185270.1A Withdrawn EP2592273A3 (fr) 2011-11-10 2012-09-20 Agencement de pompe hydraulique

Country Status (3)

Country Link
US (1) US20130121854A1 (fr)
EP (1) EP2592273A3 (fr)
DE (1) DE102011055194B4 (fr)

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US8702373B1 (en) * 2013-07-15 2014-04-22 United Technologies Corporation Lubrication of journal bearing during clockwise and counter-clockwise rotation
DE102014111133A1 (de) * 2014-08-05 2016-02-11 Robert Bosch Automotive Steering Gmbh Filterung für reversierbare Zahnradmaschine
DE102015219503A1 (de) * 2015-10-08 2017-04-13 Zf Friedrichshafen Ag Antriebsstrang für ein Kraftfahrzeug mit einer Pumpeneinrichtung
DE102015220535A1 (de) * 2015-10-21 2017-04-27 Zf Friedrichshafen Ag Hydrauliksystem zur Kühlung eines Automatikgetriebes
DE102016200960B4 (de) * 2016-01-25 2018-02-15 Festo Ag & Co. Kg Pumpvorrichtung
US20190011046A1 (en) * 2017-07-05 2019-01-10 GM Global Technology Operations LLC Hydraulic circuit to enable unidirectional flow under forward and reverse positive displacement pump rotation
US11162494B2 (en) * 2019-01-23 2021-11-02 Pratt & Whitney Canada Corp. Scavenge pump
DE102019132711A1 (de) * 2019-12-02 2021-06-02 Fte Automotive Gmbh Flüssigkeitspumpe, insbesondere zur Versorgung eines Getriebes oder einer Kupplung im Antriebsstrang eines Kraftfahrzeugs
GB202005916D0 (en) * 2020-04-23 2020-06-10 Rolls Royce Plc Gas turbine engine lubrication system
DE102021132217A1 (de) * 2021-12-07 2023-06-07 Schwäbische Hüttenwerke Automotive GmbH Fluidfördersystem mit lastabhängiger Drehzahlumkehr einer Rotationspumpe

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DE102010010804A1 (de) 2010-03-09 2011-09-15 Sew-Eurodrive Gmbh & Co. Kg Anordnung zum Schmieren eines Getriebes, Getriebe und Baukasten

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Also Published As

Publication number Publication date
US20130121854A1 (en) 2013-05-16
EP2592273A3 (fr) 2013-12-18
DE102011055194B4 (de) 2018-01-18
DE102011055194A1 (de) 2013-05-16

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