EP1378665A1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP1378665A1
EP1378665A1 EP03013008A EP03013008A EP1378665A1 EP 1378665 A1 EP1378665 A1 EP 1378665A1 EP 03013008 A EP03013008 A EP 03013008A EP 03013008 A EP03013008 A EP 03013008A EP 1378665 A1 EP1378665 A1 EP 1378665A1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
pressure
vane pump
medium flow
pump according
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
EP03013008A
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German (de)
English (en)
Other versions
EP1378665B1 (fr
Inventor
Johann Merz
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.)
Robert Bosch Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1378665A1 publication Critical patent/EP1378665A1/fr
Application granted granted Critical
Publication of EP1378665B1 publication Critical patent/EP1378665B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C2/3446—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 the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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
    • F04C2/3446—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 the inner and outer member being in contact along more than one line or surface
    • F04C2/3447—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 the inner and outer member being in contact along more than one line or surface the vanes having the form of rollers, slippers or the like

Definitions

  • the invention relates to a vane pump for generating a pressure medium flow to a consumer according to the preamble of claim 1.
  • a generic vane pump is known from DE 41 36 150 A1.
  • the generic vane pump has one in a pump housing non-rotatably mounted cam ring.
  • a rotor inside the cam ring arranged which has a plurality of slots which are substantially radially outward are directed. Wings are movably guided in the slots, their movement controlled by the inner contour of the cam ring when the rotor rotates becomes.
  • the working chambers each have a suction and pressure zone.
  • In each of the two Suction zones is an inlet chamber and one in each of the two pressure zones Outlet chamber arranged.
  • the two pressure medium flows from the two Outlet chambers parallel at low pump speeds and at higher ones Pump speeds connected in series.
  • the pump known from DE 41 36 150 A1 is used, for example, for a Power steering of a motor vehicle used.
  • To the very different Speeds of the drive motor to the pressure medium requirements of the consumer To adapt, such vane pumps with a flow control valve fitted. This is to ensure that the liquid flow for power steering at a high pump speed the liquid flow at a low pump speed.
  • the displacement volume of the vane pump can be chosen to be large, to ensure the minimum power consumption of the consumer. The consequence of which is that at high engine speeds, a correspondingly high flow rate is circulated unused, which deteriorates the overall efficiency of the system becomes.
  • the generic document describes a vane pump in the the pressure medium flows from the two outlet chambers at high speeds can be connected in series.
  • the structure of the vane pump is disadvantageous relatively complex with the special flow control valve.
  • an actuation of the flow control valve is only achieved when a corresponding one There is resistance at the throttle point. This requires a high one Volume flow are promoted, which requires corresponding power and a causes undesirable heat generation.
  • Double-bladed vane pumps are known from the further prior art, which are usually not regulated or have bypass control. Vane pumps are also known in which one vane side is short-circuited. However, the efficiency of these vane pumps is less and the volume flow control to a consumer is still less precise, than in the generic vane pump, which are already improvements for this has proposed.
  • the known vane pumps usually convey a high volume is performed against a throttle or against a resistance and, if necessary is traceable through a flow control valve and a bypass line.
  • the Losses go directly into temperature and heat it up Pressure medium circuit clearly. This makes the use of appropriate Coolers necessary, the size of which increases proportionally with the pressures. Because in particular more and more hydraulic power is required in the automotive sector is, the resulting from the previously known vane pumps Performance losses that are directly reflected in fuel consumption, clearly on.
  • the object of the present invention is a vane pump to create, which solves the aforementioned disadvantages of the prior art, in particular significantly improves efficiency at high speeds and at a cost-effective, compact design, simple power control and enables precise volume flow control to a consumer.
  • the pressure medium flow from a first outlet chamber through a Solenoid valve can be fed directly to the pump suction side (short-circuited) achieve an advantageous power control.
  • the solenoid valve can in a simple manner based on the pump speed and / or the steering torque and / or the steering angle and / or other parameters that save energy cause to be controlled.
  • the control of the solenoid valve by means of the pump speed, the Steering angle and the steering torque is advantageous because it is also the strength of the Deflection and the steering angle can be taken into account.
  • a medium pump speed and a small steering movement is a lower one Volume of the pressure medium flow sufficient, while at the same pump speed a strong deflection of the vehicle wheels an increased volume of the pressure medium flow required.
  • the vane pump it is also possible to use the vane pump to be controlled independently of the pump speed or in addition to the pump speed to consider the steering torque, the steering angle or a steering request.
  • the size of the desired deflection of the vehicle wheels can thus be taken into account.
  • the relevant data can be in simple Result from the steering angle signal, for example, the ZSP signal or be calculated.
  • pump speed can short-circuit a first outlet chamber become, i.e. the pressure medium flow is fed back directly to the pump suction side because the power steering does not have a pressure medium flow for control the vehicle wheels needed.
  • the outlet chambers train asymmetrically. It can be provided that the permanently promotes smaller outlet chamber and thus minimal delivery, especially if there is no steering torque.
  • the big outlet chamber thus represents the first outlet chamber controlled by the solenoid valve For example, when a corresponding steering torque or the large outlet chamber can be used for maneuvers with low pump speeds can be switched on by the solenoid valve.
  • the solenoid valve optimizes the efficiency of the vane pump and enables a compact and inexpensive design.
  • the energetic advantages of the solution according to the invention result in essentially from the fact that a lower volume flow is promoted by the system becomes.
  • the fact that the volume flow is reduced results in a lower one Idling pressure.
  • the idle pressure arises, i.e. the pressure in System at the idle speed of the pump, through the orifice, the orifice in the expansion hose, the steering valve (acts like an orifice), the return orifice, the oil cooler and the return filter. If the control current of the pump is reduced, the idle pressure drops and thus the power consumption of the pump.
  • the volume flow of the switched off Side does not flow through the control throttle or the orifice plate. From it too this results in a lower idle pressure.
  • Another reason for the energetic Advantages of the solution according to the invention is that the flow cross sections the pump are generally very small. By the invention Control of the pressure medium flow and the additional channels are created lower flow resistance.
  • the solenoid valve can have essentially two switching positions, whereby conveyed into the pressure chamber in a switching position via a check valve and in the other switching position the pressure medium is depressurized to the pump suction side flows. It is special in terms of a compact design advantageous if the pressure medium is on the shortest route to the pump suction side is guided and with the suction connection or a suction nozzle an injector forms.
  • the use of the solenoid valve advantageously enables that Switching between the switch positions can be done by any parameter can. In addition, the shortest switching times can be achieved without that a "switching pressure" must be accumulated beforehand.
  • the solenoid valve enables a particularly simple and compact design, since there are no pressure medium conveying lines or to control the solenoid valve the like must be installed.
  • the pressure medium flow from the first outlet chamber in a closed switching position of the solenoid valve via a check valve Pressure chamber or the main pressure line and in an open position of the Solenoid valve can be fed directly to the pump suction side or the suction connection is.
  • the open switch position in which the pressure medium flow of the first outlet chamber is short-circuited or is fed directly to the pump suction side, is preferably at high pump speeds or when there is no or only a small steering torque is present or no or only a small steering movement required is.
  • the in an open switch position of the solenoid valve recirculated or short-circuited pressure medium flow the first outlet chamber by means of an intersection formed as an injector can be injected into the pressure medium flow of the suction connection.
  • the energy that the short-circuited or recirculated pressure medium flow with brings, can thus to charge the pressure medium flow of the suction port be used.
  • the one from the suction connection and the intersection The injector formed ensures that the returned pressure medium flow is optimal the pump suction side is supplied without the pressure medium inflow from the outside is hindered. This results in further energetic advantages for the Vane pump.
  • the solenoid valve is integrated in a pump cover.
  • the check valve in arranged an end plate and preferably designed as a diaphragm valve is.
  • An arrangement of the check valve in an end plate through which the working chambers of the vane pump are limited on the face side also particularly advantageous with regard to a simple and compact Design highlighted.
  • Existing channels and holes in the Face plate can be used.
  • An embodiment of the check valve as a diaphragm valve has been found to be particularly suitable.
  • the vane pump has a pump suction side 1 with a suction port 2 and a pump pressure side 3, which is not one leads consumers shown.
  • The is particularly suitable Vane pump for supplying an auxiliary power steering system of a motor vehicle.
  • a drive shaft 4 mounted with one on it located rotor 5 is connected.
  • the rotor 5 has radially arranged slots 6, in which wings 7 are guided.
  • wings 7 may be provided.
  • the blades 7 and the rotor 5 are of a cam ring 8, the non-rotating is connected to the pump housing, enclosed. Between the cylindrical Circumferential surface of the rotor 5 and the elliptical bore of the There are two working chambers 9 in the cam ring 8.
  • the working chambers 9 are generally crescent-shaped.
  • the funding volume results itself from the largest possible sickle segment between two wings 7 and Width of the rotor 5 or the wing 7.
  • the working chambers 9 are of the same size.
  • the invention can also be provided for the working chambers 9 are asymmetrical and therefore have a large and a small working chamber 9 is provided.
  • each working chamber 9 has an inlet chamber 10 and 11 and an outlet chamber 12 and 13 respectively.
  • the pressure medium flows out the outlet chambers 12, 13 are in a known and for reasons of clarity pressure chamber or a main pressure line not shown in the drawing 14 feasible to the consumer.
  • the vane pump has a rear vane oil channel 15, which only basically shown channels 15a, 15b or bores and grooves with the Pump pressure side 3 or the pressure chamber is connected.
  • the function of the Rear wing oil channel 15 is well known and therefore not in the following described in more detail.
  • the pressure medium flow is from the first Outlet chamber 12 by means of an electro valve 16, which is preferably in a Pump cover, not shown, is integrated, controllable.
  • the pressure medium flow can be based on certain values, e.g. the pump speed, a steering torque, a steering angle or generally a steering request are controlled such that the pressure medium flow to the pressure chamber or Main pressure line 14 or the pump suction side 1 (short-circuited) supplied becomes.
  • the pump speed can be used to easily determine how high the available volume of one or both outlet chambers 12, 13 is.
  • the values "steering torque” and “steering angle” can be used to determine whether deflection of the vehicle wheels is desired and how much Volume of the pressure medium in the main pressure line 14 or the pressure chamber should be.
  • These values or in simple configurations also depending on individual values (e.g. only the pump speed) can thus control the solenoid valve 16 such that the first outlet chamber 12 the pressure medium flow directly on the pump suction side 1 or the pressure chamber or the main pressure line 14.
  • the solenoid valve 16 can also have other parameters that save energy are suitable to be used.
  • the solenoid valve 16 can have an open / close circuit be formed and have a piston 17.
  • the solenoid valve 16 designed as an electromagnetic valve.
  • the solenoid valve 16 has also a spring 18. Solenoid valves with an on / off circuit are well known, which is why the different possible embodiments is not discussed in more detail.
  • the exemplary embodiment provides that the pressure medium flow from the first outlet chamber 12 in a closed switching position of the electrovalve 16 to the pressure chamber via a check valve 19 or the main pressure line 14 can be fed.
  • Check valve 19 can advantageously in a front plate, the working chambers 9 on the end limited, be arranged.
  • the check valve 19 can preferably be designed as a diaphragm valve.
  • the check valve 19 prevents the pressure medium flow from flowing out the second working chamber 13 and the pressure chamber or the main pressure line 14th
  • the pressure medium flow from the first outlet chamber 12 in an open position of the solenoid valve 16 directly the pump suction side 1 or the suction port 2 can be fed.
  • the recirculated or short-circuited pressure medium flow from the first outlet chamber 12 is by means of an intersection 20 in the pressure medium flow of the Suction port 2 injected.
  • the intersection is an injector 20 educated.
  • the inlet chambers 10, 11 by two Inlet chamber lines 21 are supplied with a pressure medium stream.
  • this pressure medium from the inlet chambers 10, 11 conveyed to the outlet chambers 12, 13.
  • the pressure medium in an uncontrolled outlet line 22nd drained in the direction of the main pressure line 14.
  • the pressure medium flow from the first outlet chamber 12 is drained into a controlled outlet line 23, which branches in the direction of the solenoid valve 16. Is the solenoid valve 16 closed (as shown in Fig. 2), the pressure medium flow flows from the controlled outlet line 23 through the check valve 19 into the main pressure line 14.
  • the solenoid valve 16 When the solenoid valve 16 is open, the pressure medium flow flows from the first outlet chamber 12 or the controlled outlet line 23 to the pump suction side 1.
  • the check valve 19 prevents in this case an outflow of the pressure medium flow from the second outlet chamber 13 or from the main pressure line 14 back to the pump suction side 1.
  • the pressure medium flow from the first outlet chamber 12 flows after leaving of the electrovalve 16 through a return line 24 to the injector 20.
  • the pressure medium flow of the first outlet chamber 12 into one Pressure medium flow is injected from an oil container line 25 of an oil container 26.
  • bypass line 28 There is a control orifice in the main pressure line 14 leading to the consumer 27 arranged to control a bypass line 28 with a flow control piston 29 corresponds.
  • the bypass line 28 should have an excess Guide the pressure medium flow back to the pump suction side 1. This ensures that a constantly regulated pressure medium flow reaches the consumer.
  • the consumer is an auxiliary power steering system is a falling course of the pressure medium flow to the consumer sensible, since at a higher pump speed the driving speed is correspondingly higher, so that a higher steering resistance the driving dynamics and improves the driving experience.
  • the flow control piston 29 is configured such that the flow control piston 29 the bypass line 28 only opens from a certain, predetermined pressure.
  • the pressure that keeps the flow control piston 29 closed is determined by a Flow control piston spring 30 and a flow control line 31 constructed.
  • the Current control line 31 is with the pressure of the pressure medium to the consumer applied.
  • the pressure that opens the flow control piston 29 is determined by the Main pressure line 14 is applied or there is a differential pressure when flowing through the control orifice 27 generated, the reduced pressure on the side acts with the flow control piston spring 30. As the volume flow increases the differential pressure and opens the bypass line 28.
  • the bypass line 28 forms with a suction line 32, into which it may already be before the pressure medium was injected from the return line 24, one Bypass injector 33.
  • the bypass line 28 can, for example, be an intersection be introduced into the suction line 32.
  • the working chambers 9 of the vane pump can, as in the embodiment shown, via a common pump suction side 1 with pressure medium be supplied. In alternative embodiments, however, can also be provided be that the working chambers 9 by two separate pump suction sides 1 be supplied with pressure medium.
  • FIGS. 3a and 3b show a diagram of the volume flow as a function of the speed and a diagram of the pressure in the system as a function of the speed for a conventional vane pump according to the prior art.
  • FIGS. 4a and 4b show a graph of the volume flow as a function of the speed and a graph of the pressure in the system as a function of the speed for the vane pump according to the invention.
  • n L denotes the idling speed.
  • the pressure in the system at the idling speed of the pump is significantly lower in the vane pump according to the invention than in the conventional vane pumps.
  • V norm volume flow that is sufficient for this is promoted
  • the control orifice 27 which controls the bypass line 28.
  • the conventional vane pumps must guarantee a volume flow for normal operation V norm even at idling speed (ie fast steering movements must be possible).
  • the volume flow for normal operation (V norm ) is shown in diagrams 3a and 4a by the horizontal line.
  • Fig. 3a shows that the volume flow that the conventional vane pump promotes increases substantially in proportion to the speed.
  • the conventional vane pump is designed such that the volume flow (V norm ) required for normal operation is achieved at the idling speed n L of the conventional vane pump.
  • the volume flow delivered by the vane pump naturally increases as the speed increases, but the control orifice 27 prevents an increase in the volume flow to the power steering system.
  • the diagram shown in FIG. 3b results, in which the pressure in the system increases in proportion to the speed or to the volume flow until it is limited by the control orifice 27 in the direction of the consumer when the idle speed n L of the conventional vane pump is reached.
  • FIG. 4a shows that the volume flow delivered by the vane pump according to the invention is significantly lower at the idling speed n L of the vane pump. Consequently, the pressure in the system shown in FIG. 4b is also significantly lower.
  • Fig. 4a shows two lines increasing proportionally to the speed, the flatter line representing the delivery of the volume flow from only one outlet chamber 13 (the unregulated outlet chamber), while the steeply rising line shows the volume flow that the vane pump produces towards the consumer when the first, ie the controlled outlet chamber 12 is switched on.
  • the volume flow V Norm required for normal operation is in the range of the idling speed n L when both outlet chambers 12, 13 convey towards the consumer, ie the first outlet chamber 12 is not short-circuited.
  • the vehicle wheels are not actuated, so that the first outlet chamber 12 can be switched off and thus the lower volume flow represented by the flat line with the resulting pressure (FIG. 4b) results .
  • the volume flow V Norm or the corresponding pressure (which corresponds to the idle pressure according to FIG. 3b) required for normal operation is only present at significantly higher speeds when the first outlet chamber 12 is short-circuited.
  • the volume flow V Norm required for normal operation is only reached at a pump speed which corresponds to twice the idle speed of the pump.
  • this value can be changed as desired.
  • a vane pump with a delivery volume of 11 ccm / rev is conceivable, in which the uncontrolled working chamber delivers 3 cmm / rev and the controlled working chamber 8 ccm / rev. If one assumes an idle speed of the vane pump of 730 revolutions, the vane pump according to the invention does not reach the volume flow required for the normal operating state and thus the corresponding pressure until about 2,660 revolutions.
  • the full functionality of the steering at the idle speed of the vane pump is made possible by switching on the first (controlled) working chamber 9 or the first outlet chamber 12. This results in considerable energetic advantages that enable a reduction in fuel consumption of 0.1 to 0.3 l.
  • the volume flow in normal operation V Norm can represent, for example, a volume flow of 8 l / min.
  • the max. Pressure in the system (to the consumer) is, for example, 7 bar (horizontal line in FIGS. 3b and 4b).
  • the idea according to the invention can also be used in general for Rotary vane pumps, especially for roller cell pumps.
  • the vane pump described can consequently also be a roller cell pump represent.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20030013008 2002-07-03 2003-06-10 Pompe à palettes Expired - Fee Related EP1378665B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002129809 DE10229809A1 (de) 2002-07-03 2002-07-03 Flügelzellenpumpe
DE10229809 2002-07-03

Publications (2)

Publication Number Publication Date
EP1378665A1 true EP1378665A1 (fr) 2004-01-07
EP1378665B1 EP1378665B1 (fr) 2005-10-05

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20030013008 Expired - Fee Related EP1378665B1 (fr) 2002-07-03 2003-06-10 Pompe à palettes

Country Status (3)

Country Link
EP (1) EP1378665B1 (fr)
DE (2) DE10229809A1 (fr)
ES (1) ES2250787T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103225608A (zh) * 2012-01-30 2013-07-31 Zf操作系统有限公司 泵
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011054028A1 (de) 2011-09-29 2013-04-04 Zf Lenksysteme Gmbh Verdrängerpumpe
DE102011056849A1 (de) 2011-12-22 2013-06-27 Zf Lenksysteme Gmbh Verdrängerpumpe
DE102012103888A1 (de) 2012-05-03 2013-11-21 Zf Lenksysteme Gmbh Verdrängerpumpe
DE102012104804A1 (de) 2012-06-04 2013-12-05 Zf Lenksysteme Gmbh Verdrängerpumpe
DE102018118838A1 (de) * 2018-08-02 2020-02-06 Volkswagen Aktiengesellschaft Schaltbare und regelbare Register-Flügelzellenpumpe

Citations (4)

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Publication number Priority date Publication date Assignee Title
DE1528973A1 (de) * 1951-01-28 1969-09-25 Bosch Gmbh Robert Verdraengerpumpe
EP0522505A2 (fr) * 1991-07-09 1993-01-13 Toyoda Koki Kabushiki Kaisha Pompe à palettes à déplacement variable
WO2001053701A1 (fr) * 2000-01-21 2001-07-26 Delphi Technologies, Inc. Pompe a palettes pour fluide hydraulique
EP1318304A2 (fr) * 2001-12-07 2003-06-11 ZF Lenksysteme GmbH Pompe à palettes

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US3953153A (en) * 1974-05-17 1976-04-27 Sundstrand Corporation Multiple displacement pump system and method
DE3837599A1 (de) * 1988-11-05 1990-05-10 Daimler Benz Ag Zahnradpumpe mit zwei im pumpengehaeuse nebeneinander angeordneten zahnradpaaren
JPH02252988A (ja) * 1988-12-02 1990-10-11 Jidosha Kiki Co Ltd オイルポンプ
DE4136150A1 (de) * 1991-11-02 1993-05-06 Zf Friedrichshafen Ag, 7990 Friedrichshafen, De Fluegelzellenpumpe
GB2287756B (en) * 1994-03-19 1998-04-08 Acg France Rotary vane pump

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Publication number Priority date Publication date Assignee Title
DE1528973A1 (de) * 1951-01-28 1969-09-25 Bosch Gmbh Robert Verdraengerpumpe
EP0522505A2 (fr) * 1991-07-09 1993-01-13 Toyoda Koki Kabushiki Kaisha Pompe à palettes à déplacement variable
WO2001053701A1 (fr) * 2000-01-21 2001-07-26 Delphi Technologies, Inc. Pompe a palettes pour fluide hydraulique
EP1318304A2 (fr) * 2001-12-07 2003-06-11 ZF Lenksysteme GmbH Pompe à palettes

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103225608A (zh) * 2012-01-30 2013-07-31 Zf操作系统有限公司 泵
CN112648181A (zh) * 2020-12-04 2021-04-13 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵
CN112648181B (zh) * 2020-12-04 2022-04-01 江苏湖润泵业科技有限公司 具有内凹式叶片的叶片泵

Also Published As

Publication number Publication date
DE10229809A1 (de) 2004-01-15
ES2250787T3 (es) 2006-04-16
DE50301288D1 (de) 2006-02-16
EP1378665B1 (fr) 2005-10-05

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