WO2011095148A2 - Tandempumpe - Google Patents
Tandempumpe Download PDFInfo
- Publication number
- WO2011095148A2 WO2011095148A2 PCT/DE2011/000014 DE2011000014W WO2011095148A2 WO 2011095148 A2 WO2011095148 A2 WO 2011095148A2 DE 2011000014 W DE2011000014 W DE 2011000014W WO 2011095148 A2 WO2011095148 A2 WO 2011095148A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- pump shaft
- shaft
- tandem
- pressure plate
- Prior art date
Links
Classifications
-
- 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
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
-
- 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
- F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
- F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
-
- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
Definitions
- the invention relates to a tandem pump for a motor vehicle, with a first pump and a second pump, which can be driven or driven individually or together by an electric motor.
- a vehicle device with a drive motor is known to which at least two ancillaries are assigned, such as a power steering pump or an anti-lock pump system.
- the ancillary units are driven electrically and intermittently only if this is necessary for the operation management. It is envisaged that the two auxiliary units is assigned a single electric motor and that one or at least one of the auxiliary units by means of a freewheel is temporarily not in rotational drive to the electric motor.
- the object of the invention is to provide a tandem pump for a motor vehicle, with a first pump and a second pump, which can be driven or driven individually or together by an electric motor, which is simple in construction and inexpensive to produce.
- the object is achieved in a tandem pump for a motor vehicle, with a first pump and a second pump, which are driven individually or together by an electric motor or driven, achieved in that between the two pumps, a switchable coupling is arranged, through which the second pump if necessary, drivingly connected to the first pump.
- the first pump is permanently driven by the electric motor.
- the second pump is switched on with the help of the switchable coupling if necessary the first pump.
- a preferred embodiment of the tandem pump is characterized in that the first pump has a first pump shaft which is integrally connected to an electric motor shaft. This makes it possible to store the first pump or the first pump shaft over the electric motor shaft flying. In the flying storage no additional bearings are required for the first pump shaft or the first pump.
- a further preferred embodiment of the tandem pump is characterized in that the electric motor shaft is mounted outside the first pump.
- the bearing of the electric motor shaft is preferably carried out by two bearings, one of which is designed as a fixed bearing and the other as a floating bearing.
- a further preferred embodiment of the tandem pump is characterized in that the first pump has a first rotor which is non-rotatably connected to the first pump shaft.
- the non-rotatable connection enables a torque transmission from the first pump shaft to the rotor.
- the first rotor is preferably non-rotatably connected to the first pump shaft, for example by a positive connection between the first rotor and the first pump shaft in the form of a shaft-hub connection.
- a further preferred embodiment of the tandem pump is characterized in that the first pump shaft by the switchable coupling rotatably connected to a second pump shaft is connected, which is associated with the second pump.
- the non-rotatable connection between the two pump shafts can be done, for example, positive or frictional.
- tandem pump is characterized in that the second pump shaft is supported by means of two bearings in a coupling housing body.
- the camps are for example around rolling bearings. Between the bearings, a coil for electromagnetic actuation of the clutch may be arranged.
- tandem pump is characterized in that the second pump shaft is an actuating piston of the switchable coupling.
- the actuating piston is preferably actuated hydraulically.
- a further preferred embodiment of the tandem pump is characterized in that the second pump shaft in the axial direction between a closed position in which the two pump shafts are rotatably connected to each other, and an open position is reciprocally movable in which decouples the second pump shaft of the first pump shaft is.
- the second pump shaft has two functions according to an essential aspect of the invention. On the one hand, the second pump shaft serves to transmit a torque from the first pump shaft to the second pump. Second, the second pump shaft is used to actuate the shiftable clutch. In the closed position, the second pump is driven by the electric motor shaft via the first pump shaft and the second pump shaft. In the open position, only the first pump shaft is driven via the electric motor shaft. The second pump shaft is not driven in the open position.
- a further preferred embodiment of the tandem pump is characterized in that the second pump shaft has at its first pump shaft end facing at least one coupling element which is non-rotatably connectable with at least one coupling element at the second pump shaft facing the end of the first pump shaft.
- the connection between the two coupling elements is preferably positive.
- the coupling member on the second pump shaft may include a protrusion that engages a recess provided in the first pump shaft for torque transmission.
- a further preferred embodiment of the tandem pump is characterized in that the second pump shaft has at its end remote from the first pump shaft end a pressure surface which defines an actuating pressure chamber. borders.
- the actuating pressure chamber is filled with hydraulic medium, through which the pressure surface on the second pump shaft can be acted upon by an increased actuating pressure in order to axially displace the second pump shaft from its open position into its closed position.
- a further preferred embodiment of the tandem pump is characterized in that the second pump shaft is arranged with its play in a second rotor of the second pump before its end remote from the first pump shaft.
- the game causes the acted upon by the actuating pressure hydraulic fluid from the actuating pressure chamber also passes between the second pump shaft and the second rotor.
- a further preferred embodiment of the tandem pump is characterized in that the second rotor has an axial internal toothing, in which engages an external axial toothing of a toothed portion of the second pump shaft to rotatably but axially to couple the second pump shaft with the second rotor.
- a design-related gear play leads to the actuation pressure applied hydraulic medium from the actuating pressure chamber in the region of the axial toothing between the second pump shaft and the second rotor passes.
- a further preferred embodiment of the tandem pump is characterized in that the second pump shaft has a collar on which a spring engages, by which the second pump shaft is biased in its open position.
- the spring is designed, for example, as a helical compression spring, which is clamped in the axial direction between the collar and a bearing for the second pump shaft in the coupling housing body.
- a further preferred embodiment of the tandem pump is characterized in that the collar abuts in the open position of the second pump shaft at one of the bearings, through which the second pump shaft is mounted in the coupling housing body. On the second pump shaft, a paragraph provided be, which abuts in the closed position of the second pump shaft to the other bearing.
- a further preferred embodiment of the tandem pump is characterized in that a first stroke ring of the first pump is arranged between a first and a second pressure plate.
- the first cam ring radially outwardly of the first rotor defines a first working space of the first pump, which is divided by wings in vanes.
- a further preferred embodiment of the tandem pump is characterized in that a second lifting ring of the second pump is arranged between a third and a fourth pressure plate.
- the second lifting ring radially outwardly of the second rotor of the second pump defines a second working space, which is divided by wings into vanes.
- a further preferred embodiment of the tandem pump is characterized in that the coupling housing body is arranged between the second and the third pressure plate.
- the coupling housing body may have two concentric through holes, in particular bores, which serve to center the second pump, in particular the second pump shaft, in the coupling housing body.
- a further preferred embodiment of the tandem pump is characterized in that a seal is arranged in the third pressure plate, which seals the interface between the second pump shaft and the third pressure plate relative to the actuating pressure chamber at the end of the second pump shaft facing away from the first pump shaft.
- the seal prevents unwanted leakage from the operating pressure chamber.
- tandem pump Another preferred embodiment of the tandem pump is characterized in that the two pumps are designed as vane pumps.
- the two vane pumps can easily by a single Electric motor shaft to be driven.
- the two pumps are preferably combined with the switchable coupling in a slide-in unit or slide-in cartridge.
- Figure 1 is a tandem pump according to the invention in longitudinal section
- Figure 3 is a similar printing plate as in Figure 2 according to another
- Electric motor 4 is driven.
- the electric motor 4 comprises an electric motor shaft 5, which is supported by means of two bearings 8, 9.
- the two bearings 8, 9 are preferably designed as rolling bearings and arranged outside the tandem pump 1.
- One of the bearings, for example bearing 8, is designed as a fixed bearing.
- the other camp, for example, the bearing 9, is designed as a floating bearing.
- the electric motor shaft 5 of the electric motor 4 serves to drive a first pump 11, which is designed as a vane pump.
- a second pump 12 which is also designed as a vane pump, can be driven with the aid of a clutch 4 if necessary together with the first pump 1 1 by the electric motor shaft 5 of the electric motor 4.
- the first pump 1 1 comprises a first pump shaft 16, which according to a
- a first rotor 18 is rotatably connected to the first pump shaft 16.
- the first rotor 18 has radially extending slots in which (not shown) wings are guided displaceably.
- the first rotor 18 is rotatable with the wings within a first cam ring 20, which is also referred to as a contour ring.
- the first rotor 18 and the first cam ring 20 limited work spaces, which are also referred to as vane, change their volume to suck a hydraulic medium, which is acted upon in the first pump 11 with pressure.
- the first rotor 18 is arranged together with the vanes and the first cam ring 20 in the axial direction between a first pressure plate 21 and a second pressure plate 22.
- the second pump 12 includes a third pressure plate 23 and a fourth pressure plate 24 through which a second pump shaft 26 extends.
- the second pump shaft 26, according to an essential aspect of the invention by means of the clutch 14 when necessary rotatably connected to the first pump shaft 16 connectable.
- a second rotor 28 of the second pump 12 is arranged together with (not shown) wings and a second cam ring 30 between the third pressure plate 23 and the fourth pressure plate 24.
- the second pump 12 is also designed as a vane pump.
- the second pump shaft 26 is mounted in a clutch housing body 33 by means of two bearings 3, 32, which are preferably designed as rolling bearings. According to one essential aspect of the invention, the second pump shaft 26 in the axial direction, that is displaceable in the direction or parallel to a rotation axis 34 of the second pump shaft 26. Thus, the second pump shaft 26 acts simultaneously as an actuating element for the clutch 14.
- the first pump shaft 16 is rotatable about the same axis of rotation 34 as the second pump shaft 26th
- the second pump shaft 26 has, at its end facing the first pump shaft 16, a coupling element 35 which cooperates with a coupling element 38 which is provided at the end of the first pump shaft 16 facing the second pump shaft 26.
- the coupling element 35 is designed, for example, as a projection, which can engage in a depression, which forms the coupling element 38, for the rotationally fixed connection of the two pump shafts 16, 26.
- the second pump shaft 26 is shown in its open position, in which the second pump shaft 26 is not rotatably connected to the first pump shaft 16. In the open position, the second pump shaft 26 is decoupled from the first pump shaft 16. When the first pump shaft 16 rotates, this rotational movement is not transmitted to the second pump shaft 26.
- the second pump shaft 26 When the second pump shaft 26 is axially displaced from the open position shown in FIG. 1 onto the first pump shaft 16 to the left to a closed position (not shown), the two coupling elements 35, 38 engage each other around the two pump shafts 16, 26 rotatably connect with each other. In the closed position of the clutch 14, the second pump shaft 26 is driven by the electric motor shaft 5 via the first pump shaft 16.
- the second pump shaft 26 has at its end facing away from the first pump shaft 16 a pressure surface 40 which limits an actuating pressure chamber 42 in the fourth pressure plate 24.
- the actuating pressure chamber 42 is filled with hydraulic medium and, if necessary, can be acted upon by an actuating pressure, by means of which the second pump shaft 26 representing an actuating piston of the clutch 14 is moved from the open position shown in FIG. 1 into its closed position.
- the second rotor 28 is provided with an inner toothing 44, with which an external toothing 46 meshes, which in the region of the second rotor 28 on the second pump shaft 26 is provided.
- the two gears 44, 46 are designed as complementary gears.
- the second pump shaft 26 has a collar 50 which abuts the bearing 32 in the open position of the second pump shaft 26 shown in FIG.
- a spring 52 which is designed for example as a helical compression spring, is clamped in the axial direction between the bearing 31 and the collar 50 so that the second pump shaft 26 is biased in its illustrated open position.
- the movement of the second pump shaft 26 toward the first pump shaft 16 may be limited by the size and shape of the coupling elements 35, 38.
- the axial movement of the second pump shaft 26 may be limited by a shoulder on the second pump shaft 26, which abuts against the bearing 31 when the second pump shaft 26 has reached its closed position.
- the hydraulic pressure prevailing in the actuating pressure chamber 42 due to a design-related play between the second pump shaft 26 and the second rotor 28 acts on a shoulder 53 which is provided in the region of the third pressure plate 23 on the second pump shaft 26.
- a game related cavity between the actuating pressure chamber 42 and the shoulder 53 of the second rotor 28 is acted upon by the actuating pressure.
- Further advance of the hydraulic medium from the actuating pressure chamber 42 is prevented by a seal 55, which seals the interface between the second pump shaft 26 and the third pressure plate 23.
- the seal 55 is disposed adjacent to the bearing 32 in the axial direction.
- an actuating element for the clutch 14 performing second pump shaft 26 is actuated hydraulically via the actuating pressure in the actuating pressure chamber 42.
- the second pump shaft 26 are also actuated by a coil 60, which is indicated within the coupling housing body 33 in the axial direction between the two bearings 31, 32.
- the second pump shaft 26 is preferably designed as a solenoid, which is electromagnetically actuated by the coil 60.
- a first pressure chamber 61 of the first pump 11 Radially outside the first cam ring 20 and the second pressure plate 22, a first pressure chamber 61 of the first pump 11 is indicated.
- a first sealing element 64 is arranged on the first pressure plate 21 and a second sealing element 65 is arranged on the coupling housing body 33.
- a second pressure chamber 67 of the second pump 12 is provided as an annular space on the side facing away from the second rotor 28 of the fourth pressure plate 24.
- the second pressure chamber 67 is sealed by a third sealing element 68 radially outward. Radially inwardly, the second pressure chamber 67 is sealed by a fourth sealing element 69 relative to the actuating pressure chamber 42.
- the tandem pump 1 has a suction connection 72, which communicates with a suction chamber 74 of the first pump 11 and with a suction chamber 75 of the second pump 12.
- the suction chambers 74, 75 and the pressure chambers 61, 67 of the tandem pump 1 are bounded radially outwards by a housing body, which is indicated in FIG. 1 by two dot-dash lines 78, 79.
- the tandem pump 1 according to the invention provides a compact insertion solution with a low space requirement and low production costs.
- the second pressure plate 22 is shown in a side view from the right.
- the suction space 74 is arranged diametrically opposite a pressure space 81 in the second pressure plate 22.
- a suction chamber 83 is formed as an annular space between the first pump shaft 16 and the second pressure plate 22.
- a connecting channel 82 shown in dashed lines is indicated that the two suction chambers 74 and 83 are in communication.
- a seal 84 is disposed in the axial direction between the second pressure plate 22 and the clutch housing body 33. The gasket 84 is configured to surround the suction spaces 74 and 83 to seal against the pressure space 81. As a result, an undesirable leakage from the pressure chamber 81 into the suction chambers 74 and 83 is prevented.
- tandem pump 1 has, inter alia, the advantage that only the first pressure plate 21 and the coupling housing body 33 have a concentric outer centering. Consequently, only the components mentioned undergo a complex turning.
- the second pump 12 is centered on the bearing 32 via the coupling housing body 33.
- the axial seal 84 Due to the design of the axial seal 84 in the second pressure plate 22, despite an axial filling of both pumps 11, 12 a sufficient axial compression of the entire pump is given.
- the axial seal 84 which is preferably designed as a molded seal, the larger pressure range is separated from the smaller suction area and from the non-pressurized space around the second pump shaft 26 around. This provides the advantage that the internal pressure forces of the first pump 11 are optimally compensated with the corresponding pressure force on the sealing side of the second pressure plate 22.
- the outflow from the first pump 11 can take place axially via channels in the coupling housing body 33 or directly radially through recesses in the first cam ring 20, that is, despite the necessary axial surface for the axial filling opening sufficient axial pressure surface for the high pressure is available to to press the second pressure plate 22 against the first cam ring 20.
- the components of the two pumps 11, 12 are pressed by the pressure area between the second pressure plate 22 and the coupling housing body 33 and need not be mechanically biased. Furthermore, this pressure range results in a pressure-dependent deflection of the second pressure plate 22, as a result of which the axial gaps of the first pump 11 are reduced in a pressure-dependent manner. In operating states in which the axial force of the fourth pressure plate 24 is greater, the fourth pressure plate 24 takes over the compression of the entire pump parts.
- the fourth printing plate 24 is designed so that a pressure-dependent reduction of the axial column of the second pump 12 is achieved.
- FIG. 3 shows a similar pressure plate 22 as in FIG. 2 according to a further exemplary embodiment.
- the same reference numerals are used.
- the seal 94 has the shape of a circular disk whose outer circumference coincides with the outer circumference of the pressure plate 22.
- the seal 95 surrounds the two suction chambers 74 and 83.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112011100440T DE112011100440A5 (de) | 2010-02-04 | 2011-01-10 | Tandempumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010006795 | 2010-02-04 | ||
DE102010006795.4 | 2010-02-04 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2011095148A2 true WO2011095148A2 (de) | 2011-08-11 |
WO2011095148A3 WO2011095148A3 (de) | 2012-06-21 |
Family
ID=43859801
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2011/000014 WO2011095148A2 (de) | 2010-02-04 | 2011-01-10 | Tandempumpe |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112011100440A5 (de) |
WO (1) | WO2011095148A2 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012002672A1 (de) | 2011-11-02 | 2013-05-02 | Dieter Voigt | Registerpumpe |
DE102015221891A1 (de) * | 2015-11-06 | 2017-05-11 | Continental Automotive Gmbh | Fördereinrichtung zur Förderung von Öl |
DE102018113677A1 (de) | 2018-06-08 | 2019-12-12 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | KFZ-Pumpenanordnung |
DE102021114710A1 (de) | 2021-06-08 | 2022-12-08 | Schaeffler Technologies AG & Co. KG | Hydrauliksystem und Verfahren zum Betreiben eines Hydrauliksystems |
RU2816962C1 (ru) * | 2023-05-15 | 2024-04-08 | Алексей Сергеевич Стороженко | Насосная станция |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19514929A1 (de) | 1994-05-09 | 1995-11-16 | Luk Fahrzeug Hydraulik | Fahrzeugeinrichtung mit einem Antriebsmotor und mindestens zwei Nebenaggregaten |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE946386C (de) * | 1944-05-16 | 1956-08-02 | Demag Ag | Zweistufiger Umlaufverdichter der Vielzellenbauart |
JPS59147895A (ja) * | 1983-02-14 | 1984-08-24 | Hitachi Ltd | 複数シリンダロ−タリ式圧縮機 |
DE4134219A1 (de) * | 1990-10-29 | 1992-04-30 | Volkswagen Ag | Zahnradpumpe mit veraenderbarem foerdervolumen |
DE19950206A1 (de) * | 1999-10-19 | 2001-04-26 | Bayerische Motoren Werke Ag | Vorrichtung mit antriebskombinierten Umlaufverdrängerpumpen, insbesondere außenverzahnte Zahnradpumpen, vor allem für Brennkraftmaschinen |
KR100427567B1 (ko) * | 2001-04-12 | 2004-04-17 | 주식회사 우성진공 | 로터리 베인형 진공펌프의 로터 |
DE102005032226A1 (de) * | 2005-07-09 | 2007-01-18 | Daimlerchrysler Ag | Schmiermittelversorgungssystem eines Kraftfahrzeugs |
-
2011
- 2011-01-10 WO PCT/DE2011/000014 patent/WO2011095148A2/de active Application Filing
- 2011-01-10 DE DE112011100440T patent/DE112011100440A5/de not_active Withdrawn
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19514929A1 (de) | 1994-05-09 | 1995-11-16 | Luk Fahrzeug Hydraulik | Fahrzeugeinrichtung mit einem Antriebsmotor und mindestens zwei Nebenaggregaten |
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012002672A1 (de) | 2011-11-02 | 2013-05-02 | Dieter Voigt | Registerpumpe |
DE102012002672B4 (de) * | 2011-11-02 | 2014-07-24 | Dieter Voigt | Registerpumpe |
DE102015221891A1 (de) * | 2015-11-06 | 2017-05-11 | Continental Automotive Gmbh | Fördereinrichtung zur Förderung von Öl |
US11078815B2 (en) | 2015-11-06 | 2021-08-03 | Vitesco Technologies GmbH | Conveying device for conveying oil |
EP3371423B1 (de) * | 2015-11-06 | 2023-03-22 | Vitesco Technologies GmbH | Fördereinrichtung zur förderung von öl |
DE102018113677A1 (de) | 2018-06-08 | 2019-12-12 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | KFZ-Pumpenanordnung |
US11168675B2 (en) | 2018-06-08 | 2021-11-09 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Motor vehicle pump arrangement |
DE102021114710A1 (de) | 2021-06-08 | 2022-12-08 | Schaeffler Technologies AG & Co. KG | Hydrauliksystem und Verfahren zum Betreiben eines Hydrauliksystems |
RU2816962C1 (ru) * | 2023-05-15 | 2024-04-08 | Алексей Сергеевич Стороженко | Насосная станция |
Also Published As
Publication number | Publication date |
---|---|
DE112011100440A5 (de) | 2012-11-29 |
WO2011095148A3 (de) | 2012-06-21 |
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