EP1378665B1 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP1378665B1
EP1378665B1 EP20030013008 EP03013008A EP1378665B1 EP 1378665 B1 EP1378665 B1 EP 1378665B1 EP 20030013008 EP20030013008 EP 20030013008 EP 03013008 A EP03013008 A EP 03013008A EP 1378665 B1 EP1378665 B1 EP 1378665B1
Authority
EP
European Patent Office
Prior art keywords
flow
pressure medium
pressure
vane cell
pump
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 - Fee Related
Application number
EP20030013008
Other languages
German (de)
English (en)
Other versions
EP1378665A1 (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 in a pump housing a rotatably mounted cam ring on. Inside the cam ring is a rotor arranged, which has a plurality of slots, which is substantially radially outwardly are directed. In the slots, wings are movably guided, their movement controlled upon rotation of the rotor by the inner contour of the cam ring becomes. Between the cam ring, the rotor and the front sides of laterally adjacent housing parts working chambers are formed. 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. By a equipped with three pairs of control edges Flow control valve, the two pressure medium flows from the two Outlet chambers at low pump speeds in parallel and at higher Pump speeds connected in series.
  • DE 41 36 150 A1 pump is, for example, for a Power steering system used a motor vehicle.
  • a Power steering system used a motor vehicle.
  • vane pumps with a flow control valve fitted. This is intended to ensure that the liquid flow for power steering at a high pump speed the liquid flow at a low pump speed corresponds.
  • the generic document describes this purpose a vane pump in the the pressure medium flows from the two outlet chambers at high speeds be connected in series.
  • the structure of the vane pump with the special flow control valve relatively expensive.
  • an actuation of the flow control valve is only reached when a corresponding Resistor at the throttle point is applied.
  • a high Volume flow are required, which requires performance and a corresponding unwanted heat development caused.
  • the known vane pumps usually promote a high volume, the is guided against a throttle or against a resistor and optionally is traceable by a flow control valve and a bypass line.
  • the Losses go directly into temperature and heat the Fluid circuit clearly. This makes the use of appropriate Coolers necessary whose size increases proportionally with the pressures. In particular in the automotive sector more and more hydraulic power required is, the rise from the previously known vane pumps Power losses, which are directly reflected in fuel consumption, clearly at.
  • the present invention is based on the object of a vane pump to solve, which solves the aforementioned disadvantages of the prior art, in particular the efficiency at high speeds significantly improved and at a cost-effective, compact design a simple power control and allows accurate flow control to a consumer.
  • the pressure medium flow from a first outlet chamber by a Electric valve directly to the pump suction can be fed (short-circuited) leaves to achieve an advantageous power control.
  • the electrovalve can do this in a simple manner based on the pump speed and / or the steering torque and / or the steering angle and / or other parameters that provide energy savings cause, be controlled.
  • the control of the solenoid valve by means of the pump speed, the Steering angle and the steering torque is advantageous because thus the strength of the Deflection and the steering angle can be considered.
  • a medium pump speed and low steering movement is a lesser 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 requires.
  • Such a control based on various Parameters, with no restriction on the parameters steering torque and steering movement is necessary, can be with an electric valve realize advantageous.
  • the vane pump regardless 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 become easier Way out of the steering angle signal, for example, the ZSP signal result or calculated.
  • a first outlet chamber are, i. the pressure medium flow fed back directly to the pump suction be because the power steering system no pressure medium flow to control the vehicle wheels needed.
  • the outlet chambers asymmetric form. It can be provided that the smaller outlet chamber permanently promotes and thus a minimum promotion, especially when no steering torque is applied, guaranteed.
  • the big outlet chamber thus provides the controlled by the solenoid valve first outlet chamber For example, when applying a corresponding steering torque or during shunting with low pump speeds, the large outlet chamber be switched by the solenoid valve.
  • the solenoid valve optimizes the efficiency of the vane pump and allows a compact and cost-effective design.
  • the energetic advantages of the solution according to the invention result in essential from the fact that a lower volume flow promoted by the system becomes.
  • the idling pressure i. the pressure in the System at the idle speed of the pump, through the orifice plate, the aperture in the expansion hose, the steering valve (acts like a panel), the return panel, the oil cooler and the return filter. If the control current of the pump is lowered, decreases the idling pressure and thus the power consumption of the pump.
  • Energetically advantageous is also that the flow of the disconnected Page does not flow through the control throttle or orifice plate. Also from it results in a lower idling pressure. Another reason for the energetic Advantages of the solution according to the invention is that the flow cross sections The pumps are generally very small. By the invention Control of the pressure medium flow and the additional channels arise lower flow resistance.
  • the solenoid valve may have substantially two switching positions, wherein conveyed in a switching position via a check valve in the pressure chamber and in the other switching position, the pressure medium without pressure to the pump suction flows. It is particularly in terms of a compact design advantageous if the pressure medium on the shortest route to the pump suction is guided and with the suction port or a suction nozzle an injector forms.
  • the use of the solenoid valve allows advantageously that the Switching between the switching positions by any parameters done can. In addition, shortest switching times can be achieved without previously a "switching pressure" must be accumulated.
  • the electrovalve allows a particularly simple and compact design, because for controlling the solenoid valve no pressure medium conveying lines or the like must be installed.
  • the solenoid valve as an electromagnetic valve with a On / off circuit is formed.
  • an embodiment as an electromagnetic valve with substantially two switching positions can be the solution according to the invention in particular realize a simple and cost-effective way.
  • the closed position of the solenoid valve at low Pump speeds or analogous to large steering moments, large Steering movements or other such parameters is present.
  • the on-switch position, in which the pressure medium flow of the first outlet chamber shorted or the pump suction is fed directly, is preferably at high pump speeds on or when no or low steering torque is applied or no or only a small steering movement required is.
  • the solenoid valve recycled 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 port.
  • the energy, the short-circuited or recycled pressure medium flow with can bring, thus can be used to charge the pressure medium flow of the suction port be used.
  • the from the suction connection and the intersection formed injector causes the recirculated pressure medium flow optimally the pump suction is supplied without the Druckstoffzufluß from the outside is hampered. This results in further energy benefits for the Vane pump.
  • the electrovalve is integrated in a pump cover.
  • the check valve in arranged a front plate and preferably designed as a diaphragm valve is.
  • An arrangement of the check valve in a face plate, through which the working chambers the vane pump frontally limited, has become also as particularly advantageous in terms of a simple and compact Design exposed. Already 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 structure of a vane pump is basically, for example, from DE 41 36 150 A1, known. Below are therefore only those for the invention necessary features described in more detail.
  • the vane pump has a pump suction side 1 with a suction port 2 and a pump pressure side 3, not to a detailed consumer leads, on.
  • the Vane pump for supplying a power steering system of a motor vehicle.
  • a drive shaft 4 mounted, with one on her located rotor 5 is connected.
  • the rotor 5 has radially arranged slots 6, in which wings 7 are guided displaceably. This can, for example eight wings 7 may be provided.
  • the wings 7 and the rotor 5 are of a cam ring 8, the rotation is connected to the pump housing, enclosed.
  • the working chambers 9 are designed generally sickle-shaped. The delivery volume results from the largest possible sickle segment between two wings 7 and the Width of the rotor 5 and the wings 7.
  • the working chambers 9 are the same size.
  • the invention may also be provided that the working chambers. 9 are formed asymmetrically and thus 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 off the outlet chambers 12, 13 are in a known and for clarity in the drawing, not shown pressure chamber or a main pressure line 14 feasible to the consumer.
  • the vane pump has a Händlölkanal 15, over only shown in principle channels 15a, 15b or holes and grooves with the Pump pressure side 3 and the pressure chamber is connected.
  • the function of the Schuerielölkanals 15 is well known and therefore not hereafter described in more detail.
  • the pressure medium flow can be determined by certain values, e.g. the pump speed, a steering torque, a steering angle or generally a steering request be controlled so that the pressure medium flow to the pressure chamber or the Main pressure line 14 or the pump suction 1 (short-circuited) supplied becomes. Based on the pump speed can be easily determined how high the available volume of one or both outlet chambers 12, 13 is.
  • the values "steering torque” or “steering angle” can be used to determine whether a deflection of the vehicle wheels is desired and how high the Volume of the pressure medium in the main pressure line 14 and the pressure chamber should be. Depending on these values or in simple configurations also depending on individual values (for example, only the pump speed) can thus be carried out the control of the solenoid valve 16 so that the first outlet chamber 12 the pressure medium flow directly to the pump suction 1 or the pressure chamber or the main pressure line 14 feeds. For controlling of the solenoid valve 16 may also have other parameters that help to save energy are suitable to be used.
  • the solenoid valve 16 with an open / close circuit be formed and have a piston 17.
  • the solenoid valve 16 formed as an electromagnetic valve.
  • the electric valve 16 has also a spring 18.
  • the pressure medium flow from the first outlet chamber 12 in an on-switching position of the solenoid valve 16 via a check valve 19 the pressure chamber or the main pressure line 14 can be fed.
  • the check valve 19 can advantageously in a face plate, the working chambers 9 frontally limited, be arranged.
  • the check valve 19 may preferably be designed as a diaphragm valve.
  • the check valve 19 prevents drainage of the pressure medium flow 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 and the suction port 2 can be fed.
  • the recirculated or compressed pressure fluid from the first outlet chamber 12 is by means of an intersection 20 in the pressure medium flow of Suction connection 2 injected.
  • the intersection is as injector 20 educated.
  • the solenoid valve 16 When the solenoid valve 16 is opened, the pressure medium flow flows from the first outlet chamber 12 and the controlled outlet 23rd to the pump suction side 1.
  • the check valve 19 prevents in this case a flow of the pressure medium flow from the second outlet chamber 13 and from the main pressure line 14 back to the pump suction 1.
  • the pressure medium flow from the first outlet chamber 12 flows after leaving of the solenoid valve 16 through a return line 24 to the injector 20.
  • bypass line 28 In the leading to the consumer main pressure line 14 is a control panel 27 arranged to control a bypass line 28 with a flow control piston 29 corresponds.
  • the bypass line 28 is an excess Forward the pressure medium flow back to the pump suction side 1. This ensures that that a constantly regulated pressure medium flow reaches the consumer.
  • the flow control piston 29 is designed such that the flow control piston 29th the bypass line 28 opens only from a certain, predetermined pressure.
  • the pressure that keeps the flow control piston 29 closed is characterized by a Flow control piston spring 30 and a power control line 31 constructed.
  • the Flow control line 31 is connected to the pressure of the pressure medium to the consumer applied.
  • the pressure that opens the flow control piston 29 is through Main pressure line 14 is applied or it is a differential pressure when flowing through the control orifice 27 generates, the reduced pressure on the side with the flow control piston spring 30 acts. With increasing volume flow increases the differential pressure and opens the bypass line 28th
  • the bypass line 28 forms with a suction line 32, in the possibly already before the pressure medium from the return line 24 has been injected, a Bypassinjektor 33.
  • the working chambers 9 of the vane pump can, as in the embodiment represented, via a common pump suction 1 with pressure medium be supplied. In alternative embodiments, however, can also be provided be that the working chambers 9 through two separate pump suction 1 are supplied with pressure medium.
  • FIGS. 3a and 3b show a graph of volumetric flow versus speed and a graph of system pressure versus speed for a conventional prior art vane pump.
  • FIGS. 4a and 4b show a graph of the volume flow as a function of the rotational speed and a graph of the pressure in the system as a function of the rotational speed for the vane pump according to the invention.
  • n L denotes the idle speed.
  • the pressure in the system at the idle speed of the pump, the so-called idling pressure, in the vane pump according to the invention is substantially lower than in the conventional vane pumps.
  • V standard a volume flow is conveyed at this pump speed, which is sufficient for this purpose
  • An increase in the pressure in the system or an excessively high volume flow is thereby prevented from this speed through the control aperture 27, which controls the bypass line 28.
  • the conventional vane pumps must already at idle speed a flow for normal operation V standard (ie fast steering movements must be possible) to ensure.
  • the flow rate for normal operation (V norm ) is shown in the diagrams 3a and 4a by the horizontal line.
  • Fig. 3a shows that the volume flow, which promotes the conventional vane pump increases substantially in proportion to the speed.
  • the conventional vane pump is designed such that the required for normal operation volume flow (V norm ) is achieved at the idle speed n L of the conventional vane pump.
  • V norm normal operation volume flow
  • the volume flow delivered by the vane pump will continue to rise as the speed increases, but the control orifice 27 will prevent the volume flow from increasing to the power steering system.
  • the graph shown in Fig. 3b in which the pressure in the system increases in proportion to the speed or the flow rate, until it is limited on reaching the idle speed n L of the conventional vane pump through the control panel 27 in the direction of the consumer.
  • Fig. 4a shows two rising in proportion to the speed of the line, the flatter line represents the promotion of the flow from only one outlet 13 (the uncontrolled outlet chamber), while the steeply rising line shows the flow that generates the vane pump in the direction of the consumer when the first, ie the controlled outlet chamber 12 is switched on.
  • the volume flow in normal operation V standard can represent, for example, a volume flow of 8 l / min.
  • the max. Pressure in the system (to the consumer) for example, be 7 bar (horizontal line of Figures 3b and 4b).
  • the idea according to the invention can also be generalized in the same way Rotary vane pumps, especially for roller cell pumps to be implemented.
  • the described vane pump can therefore 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)

Claims (14)

  1. Pompe à palettes pour la production d'un courant de fluide sous pression vers un consommateur, notamment une direction assistée d'un véhicule automobile, ayant les caractéristiques suivantes :
    la pompe à palettes présente deux chambres de travail (9) ;
    les chambres de travail (9) présentent, pour la formation d'un côté aspiration de la pompe, une chambre d'entrée respective (10 ou 11) et pour la formation d'un côté refoulement de la pompe, une chambre de sortie respective (12 ou 13) ;
    les chambres d'entrée (10, 11) pouvant être alimentées en fluide sous pression par le biais d'un raccord d'aspiration et les courants de fluide sous pression pouvant être guidés hors des chambres de sortie (12 ; 13) dans un espace de pression ou une conduite de pression principale (14) pouvant être connectée au consommateur,
    caractérisée par les caractéristiques suivantes :
    la conduite de pression principale (14) présente une chicane de régulation (27) et peut être connectée au côté aspiration de la pompe (1) par le biais d'une conduite de dérivation (28) ;
    dans la conduite de dérivation (28) est intégré un piston de régulation du courant (29), qui est en liaison coopérante avec la chicane de régulation (27) ;
    la conduite de dérivation (28) présente un injecteur de dérivation (33) ;
    une première chambre de sortie (12) est en liaison coopérante avec une électrovanne (16) ;
    la première chambre de sortie (12) peut être connectée au côté aspiration de la pompe (1) ou à l'espace de pression ou à la conduite de pression principale (14) ;
    dans une conduite de retour (24) est intégré un dispositif d'intersection (20) ;
    entre les chambres de sortie (12, 13) et la conduite de pression principale (14) est disposée une soupape anti-retour (19).
  2. Pompe à palettes selon la revendication 1,
    caractérisée en ce que
    l'électrovanne (16) est réalisée sous la forme d'une vanne électromagnétique à ouverture/fermeture.
  3. Pompe à palettes selon la revendication 1 ou 2,
    caractérisée en ce que
    pour la commande de l'électrovanne (16), la vitesse de la pompe et/ou un couple de direction et/ou un angle de direction et/ou d'autres paramètres qui sont appropriés pour l'économie d'énergie peuvent être utilisés.
  4. Pompe à palettes selon la revendication 1, 2 ou 3,
    caractérisée en ce que
    le courant de fluide sous pression peut être acheminé depuis la première chambre de sortie (12) dans une position de fermeture de l'électrovanne (16) par le biais d'une soupape anti-retour (19) à l'espace de pression ou à la conduite de pression principale (14).
  5. Pompe à palettes selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    le courant de fluide sous pression peut être acheminé de la première chambre de sortie (12) dans une position d'ouverture de l'électrovanne (16) directement au côté aspiration de la pompe (1) ou au raccord d'aspiration (2).
  6. Pompe à palettes selon la revendication 4 ou 5,
    caractérisée en ce que
    la soupape anti-retour (19) empêche un échappement du courant de fluide sous pression hors de la deuxième chambre de sortie (13) et de l'espace de pression ou de la conduite de pression principale (14).
  7. Pompe à palettes selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    le courant de fluide sous pression recyclé ou court-circuité provenant de la première chambre de sortie (12) peut être injecté au moyen d'une intersection (20) dans le courant de fluide sous pression du raccord d'aspiration (2).
  8. Pompe à palettes selon la revendication 7,
    caractérisée en ce que
    l'intersection est réalisée sous forme d'injecteur (20).
  9. Pompe à palettes selon la revendication 1,
    caractérisée en ce que
    le piston de régulation du courant (29) ou la chicane de régulation (27) régulent un courant de fluide sous pression de dérivation de telle sorte qu'un courant de fluide sous pression régulé, constant, parvienne au consommateur.
  10. Pompe à palettes selon la revendication 1 ou 9,
    caractérisée en ce que
    grâce au piston de régulation du courant (29) et/ou à l'électrovanne (16), on peut réaliser pour une vitesse de pompe croissante, une évolution constante ou diminuant du courant de fluide sous pression allant au consommateur.
  11. Pompe à palettes selon la revendication 9 ou 10,
    caractérisée en ce que
    le courant de fluide sous pression de dérivation peut être acheminé au courant de fluide sous pression allant aux chambres d'entrée (10, 11) par une deuxième intersection réalisée sous forme d'injecteur de dérivation (33).
  12. Pompe à palettes selon l'une quelconque des revendications 1 à 11,
    caractérisée en ce que
    l'électrovanne (16) est intégrée dans un couvercle de la pompe.
  13. Pompe à palettes selon l'une quelconque des revendications 4 à 12,
    caractérisée en ce que
    la soupape anti-retour (19) est disposée dans une plaque frontale et est réalisée de préférence sous forme de soupape à membrane.
  14. Pompe à palettes selon l'une quelconque des revendications 4 à 13,
    caractérisée en ce que
    les chambres de travail (9) sont réalisées sous forme asymétrique et la plus grande chambre de travail (9) ou la plus grande chambre de sortie (12) peut être commandée au moyen de l'électrovanne (16).
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 EP1378665A1 (fr) 2004-01-07
EP1378665B1 true EP1378665B1 (fr) 2005-10-05

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EP20030013008 Expired - Fee Related EP1378665B1 (fr) 2002-07-03 2003-06-10 Pompe à palettes

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

Families Citing this family (7)

* 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
DE102012100702A1 (de) * 2012-01-30 2013-08-01 Zf Lenksysteme Gmbh Pumpe, insbesondere Flügelzellenpumpe für eine Hilfskraftlenkung
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
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

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Publication number Priority date Publication date Assignee Title
DE1528973A1 (de) * 1951-01-28 1969-09-25 Bosch Gmbh Robert Verdraengerpumpe
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
EP0522505A3 (en) * 1991-07-09 1993-07-14 Toyoda Koki Kabushiki Kaisha Variable-displacement vane pump
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
EP1327077A1 (fr) * 2000-01-21 2003-07-16 Delphi Technologies, Inc. Pompe a palettes pour fluide hydraulique
DE10160286A1 (de) * 2001-12-07 2003-06-18 Zf Lenksysteme Gmbh Flügelzellenpumpen

Also Published As

Publication number Publication date
EP1378665A1 (fr) 2004-01-07
DE10229809A1 (de) 2004-01-15
ES2250787T3 (es) 2006-04-16
DE50301288D1 (de) 2006-02-16

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