EP1259737A1 - Control device for positive displacement pumps - Google Patents

Control device for positive displacement pumps

Info

Publication number
EP1259737A1
EP1259737A1 EP01902363A EP01902363A EP1259737A1 EP 1259737 A1 EP1259737 A1 EP 1259737A1 EP 01902363 A EP01902363 A EP 01902363A EP 01902363 A EP01902363 A EP 01902363A EP 1259737 A1 EP1259737 A1 EP 1259737A1
Authority
EP
European Patent Office
Prior art keywords
flow control
section
control
throttle
control piston
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
EP01902363A
Other languages
German (de)
French (fr)
Other versions
EP1259737B1 (en
Inventor
Günter DRASKOVITS
Gerhard Zimmermann
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 EP1259737A1 publication Critical patent/EP1259737A1/en
Application granted granted Critical
Publication of EP1259737B1 publication Critical patent/EP1259737B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/062—Arrangements for supercharging the working space
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00

Definitions

  • the invention relates to a control device for positive displacement pumps, in particular for vane pumps, according to the preamble of claim 7, in which a pressure chamber is connected via a throttle device to an outlet connected to a consumer. Furthermore, a flow control piston which can be moved in a housing bore is provided, the first end face of which has a connection to the pressure chamber. A second end face of the flow control piston extends into a chamber which is connected to the outlet downstream of the throttle device. The flow control piston releases a connection from the pressure chamber to a pump inlet channel as a function of a differential pressure acting on the two end faces.
  • the throttle device is located in the pressure outlet of the pump and contains a control pin, the control contour of which is designed in such a way that, together with a throttle bore, there is a variable passage cross section.
  • One of the two control pin and throttle bore elements is connected to the flow control piston and the other of the two elements is fixed to the housing.
  • Such a control device interacting with a throttle device according to the preamble of claim 1 is known from DE 22 30 306 B2.
  • the cone of the control pin which is conical at its free end, gives the pump a falling flow characteristic.
  • the proportional range e.g. idling range
  • the delivery rate will increase. This is as a significant drop and subsequent equally significant increase of the steering torque. If an additional pressure relief valve is installed in such a control device, then when the pressure relief valve responds, the maximum pressure is also increased.
  • the invention has for its object to provide a control device with which such overshoot, d. that is, a brief increase in the delivery rate or delivery pressure is prevented when accelerating rapidly from the lowest speeds.
  • control device characterized in claim 1 in that the control pin has a thickened section in an axial displacement area, which is not yet used for volume flow control in the flow control piston, so that there is a minimal aperture cross-section in this displacement area , What is achieved here is that the pressure difference over the thickened area is greater and the flow control piston moves earlier, or faster in dynamic processes.
  • control pin with its thickened section can be produced particularly easily if the control pin is connected to the flow control piston and the throttle bore is fixed to the housing and the thickened section is cylindrical.
  • the control characteristic of the ver ⁇ thickened portion may comprise a frustoconical contour. It is advantageous if the larger diameter of the truncated cone on the first end face of the flow control is arranged. This allows the characteristics of the control process, the control speed, to be fine-tuned.
  • FIG. 1 shows a control device for a vane pump in longitudinal section according to a first embodiment
  • Fig. 2 shows a flow control piston of the control device according to a second embodiment.
  • a drive shaft 3 is mounted in a housing 2 closed by a cover 1.
  • the drive shaft 3 carries a rotor 4 in a conventional manner on a spline.
  • Radially movable blades 5 are guided in radial slots of the rotor 4 and slide along a cam ring 6 in a sealing manner.
  • a pressure plate 7 lies sealingly on the pump package consisting of rotor 4, blades 5 and cam ring 6.
  • Another pressure plate 8 rests on the other side of the pump package due to the force of a spring 10.
  • the vanes 5 enclose conveying chambers (not shown) between them, which stand fertilizer.
  • the pumped pressure oil enters a pressure chamber 12 from the delivery chambers via pressure openings 8 of the pressure plate 8, which are also not shown.
  • the pressure chamber 12 has part-ring-shaped channels 13 and 14 with lower wing spaces 15 and 16 connection. This makes it possible to press the vanes 5 passing through the pressure zone outwards into the cam ring 6.
  • a flow control piston 21 of the flow control valve 18 controls an inlet channel 23 of the pump in a known manner with a control collar 22.
  • the control collar 22 rests against the throttle device 20 under the load of a spring 24.
  • the inlet channel 23 is closed by the control collar 22.
  • a closure element 25 for example a pipe screw connection, which is connected to a consumer, for example an auxiliary power steering system.
  • An inlet channel 26 connects the pressure chamber 12 to the bore section 17A.
  • the throttle device 20 contains a control pin 27 which is fixedly connected to the flow control piston 21 and a throttle bore 28 which is arranged on the closure element 25 and is thus fixedly connected to the housing 2.
  • the two elements control pin 27 and throttle bore 28 can also be connected to the other elements housing 2 and flow control piston 21 with the same effect.
  • the control pin 27 has at its free end a contour which allows the speed-dependent influencing of the conveying flow directed to the consumer.
  • this contour contains an essentially cylindrical end section 30, to which a conical section 31 and a section 32 with the smallest cross section adjoin. Between this section 32 and a first end face 33 of the flow control piston 21 facing the throttle device 20 there is, according to the invention, a thickened section 34 of the control pin 27.
  • the thickened section 34 extends over an axial length such that when the flow control piston 21 is displaced by one of these There is no volume flow control for the corresponding distance. This means that after such a shift there is still no connection between the inlet channel 26 coming from the pressure chamber 12 and the inlet channel 23.
  • the thickened section 34 has a cylindrical contour.
  • the thickened section 35 has a frustoconical contour.
  • the larger diameter of the truncated cone is arranged on the first end face 33 of the flow control piston 21. This is particularly advantageous because the characteristic of the control process, the control speed, can be fine-tuned.
  • a space 36 accommodating the spring 24 of the flow control piston 21 is connected via a control line 37 indicated by dashed lines, an annular groove 38 and a throttle point 40 to an outlet 41 which is arranged on the closure element 25.
  • the annular groove 38 and the throttle point 40 are omitted.
  • the space 36 is delimited on one side by a second end face 42 of the flow control piston 21.
  • the control device works as follows:
  • the entire flow of the pump initially flows via the inlet anal 26 into the bore section 17A. Up to the cut-off point at a pump speed of, for example, 1000 / min, the delivery flow flows past the end face 33 of the control collar 22 to the outlet 41. The delivery flow flows through the passage cross-section drawn between the control pin 27 and the throttle bore 28 resulting pressure drop of the flow control piston 21 slightly to the left, but the control collar 22 does not yet begin to open the inlet channel 23.
  • the very small throttle cross section between the thickened section 34 and the throttle bore 28 creates a large pressure difference across the throttle device 20 and thus above the flow control piston 21. This large pressure difference forces an accelerated movement of the flow control piston 21. This in turn leads to a faster reaction of the control mechanism, so that overshoot and excessive delivery is prevented.

Abstract

The invention relates to a control device for positive displacement pumps, consisting of a throttle device (20) and a flow control valve (18). The flow control valve (18) is provided with a flow control piston (21) and regulates an unrequired excess flow to the pump at an increased speed. The throttle device (20) produces a speed-related pressure differential in a bore section (17A), said pressure differential being responsible for the displacement of the flow control valve (18) and the throttle device (20). The throttle device (20) is placed in the pressure outlet (bore section 17A) of the pump and contains a regulating pin (27) which is connected to the flow control piston (21), having a control contour which is embodied in such a way that a modifiable through cross-section is created in association with a throttle bore (28). The control pin (27) has a wider section (34) in an axial displacement area of the throttle device (20), said area not being involved in control of the volume flow, whereby a minimum obturating section arises in the displacement area. This results in accelerated movement of the flow control piston (21), which in turn results in quicker reaction of the control mechanism, thereby preventing an overshoot and overincrease in the flow capacity.

Description

Regeleinrichtung für Verdrängerpumpen Control device for positive displacement pumps
Die Erfindung betrifft eine Regeleinrichtung für Ver- drängerpumpen, insbesondere für Flügelzellenpumpen, nach dem Oberbegriff des 7Λnspruchs 1. Darin steht ein Druckraum über eine Drosseleinrichtung mit einem an einen Verbraucher angeschlossenen Auslaß in Verbindung. Weiter ist ein in einer Gehäusebohrung verschiebbarer Stromregelkolben vorge- sehen, dessen erste Stirnfläche mit dem Druckraum Verbindung hat. Eine zweite Stirnfläche des Stromregelkolbens ragt in eine Kammer, die mit dem Auslaß stromabwärts der Drosseleinrichtung verbunden ist. Der Stromregelkolben gibt in Abhängigkeit eines auf die beiden Stirnflächen wirkenden Differenzdrucks eine Verbindung von dem Druckraum zu einem Pumpeneinlaßkanal frei. Die Drosseleinrichtung sitzt im Druckausgang der Pumpe und enthält einen Regelstift, dessen Steuerkontur so ausgeführt ist, daß sich zusammen mit einer Drosselbohrung ein veränderbarer Durchtrittsquerschnitt ergibt. Dabei ist eines der beiden Elemente Regelstift und Drosselbohrung mit dem Stromregelkolben verbunden und das andere der beiden Elemente ist gehäusefest.The invention relates to a control device for positive displacement pumps, in particular for vane pumps, according to the preamble of claim 7, in which a pressure chamber is connected via a throttle device to an outlet connected to a consumer. Furthermore, a flow control piston which can be moved in a housing bore is provided, the first end face of which has a connection to the pressure chamber. A second end face of the flow control piston extends into a chamber which is connected to the outlet downstream of the throttle device. The flow control piston releases a connection from the pressure chamber to a pump inlet channel as a function of a differential pressure acting on the two end faces. The throttle device is located in the pressure outlet of the pump and contains a control pin, the control contour of which is designed in such a way that, together with a throttle bore, there is a variable passage cross section. One of the two control pin and throttle bore elements is connected to the flow control piston and the other of the two elements is fixed to the housing.
Eine derartige, mit einer Drosseleinrichtung zusammen- wirkende Regeleinrichtung nach dem Oberbegriff des Anspruchs 1 ist aus der DE 22 30 306 B2 bekannt. Durch einen an seinem freien Ende konischen Zapfen des Regelstiftes erhält die Pumpe eine abfallende Strömungscharakteristik. Bei derartigen Regeleinrichtungen besteht die Gefahr, daß bei einer Drehzahlerhöhung der Pumpe aus dem Proportionalbereich (z. B. Leerlaufbereich) in den Regelbereich eine Überhöhung der Fördermenge eintritt. Dies ist als deutlicher Abfall und anschließender ebenso deutlicher Anstieg des Lenkmomentes zu spüren. Wenn bei einer derartigen Regeleinrichtung ein zusätzliches Druckbegrenzungsventil eingebaut ist, dann kommt es beim Ansprechen dieses Druckbegrenzungsventils außerdem zu einer Überhöhung des maximalen Druckes.Such a control device interacting with a throttle device according to the preamble of claim 1 is known from DE 22 30 306 B2. The cone of the control pin, which is conical at its free end, gives the pump a falling flow characteristic. With such control devices, there is a risk that if the pump increases in speed from the proportional range (e.g. idling range) to the control range, the delivery rate will increase. This is as a significant drop and subsequent equally significant increase of the steering torque. If an additional pressure relief valve is installed in such a control device, then when the pressure relief valve responds, the maximum pressure is also increased.
Der Erfindung liegt die Aufgabe zugrunde, eine Regeleinrichtung zu schaffen, mit der ein solches Überschwingen, d. h., eine kurzzeitige Überhöhung der Fördermenge bzw. des Förderdruckes, bei schnellem Beschleunigen ausgehend von niedrigsten Drehzahlen verhindert wird.The invention has for its object to provide a control device with which such overshoot, d. that is, a brief increase in the delivery rate or delivery pressure is prevented when accelerating rapidly from the lowest speeds.
Diese Aufgabe ist durch die im Anspruch 1 gekennzeichnete Regeleinrichtung dadurch gelöst, daß der Regelstift in einem axialen Verschiebe-Bereich, der bei dem Stromregelkolben noch nicht zur Volumenstromregelung herangezogen wird, einen verdickten Abschnitt aufweist, so daß in diesem Verschiebe-Bereich ein minimaler Blendenquerschnitt besteht. Hierbei wird erreicht, daß die Druckdifferenz über dem verdickten Bereich größer ist und sich damit der Stromregelkolben früher, bzw. bei dynamischen Vorgängen schneller, bewegt.This object is achieved by the control device characterized in claim 1 in that the control pin has a thickened section in an axial displacement area, which is not yet used for volume flow control in the flow control piston, so that there is a minimal aperture cross-section in this displacement area , What is achieved here is that the pressure difference over the thickened area is greater and the flow control piston moves earlier, or faster in dynamic processes.
Vorteilhafte und zweckmäßige Ausgestaltungen der Er- findung sind in den Unteransprüchen angegeben. Besonders einfach läßt sich der Regelstift mit seinem verdickten Abschnitt herstellen, wenn der Regelstift mit dem Stromregelkolben verbunden und die Drosselbohrung gehäusefest ist und der verdickte Abschnitt zylindrisch ausgebildet wird. Zur besseren Feinabstimmung der Regelkennlinie kann der ver¬ dickte Abschnitt eine kegelstumpfförmige Kontur aufweisen. Dabei ist es vorteilhaft, wenn der größere Durchmesser des Kegelstumpfes an der ersten Stirnfläche des Stromregelkol- bens angeordnet ist. Dadurch kann die Charakteristik des Regelvorganges, die Regelgeschwindigkeit, sehr fein abgestimmt werden.Advantageous and expedient refinements of the invention are specified in the subclaims. The control pin with its thickened section can be produced particularly easily if the control pin is connected to the flow control piston and the throttle bore is fixed to the housing and the thickened section is cylindrical. For a better fine-tuning of the control characteristic of the ver ¬ thickened portion may comprise a frustoconical contour. It is advantageous if the larger diameter of the truncated cone on the first end face of the flow control is arranged. This allows the characteristics of the control process, the control speed, to be fine-tuned.
Im folgenden wird die Erfindung anhand zweier in der Zeichnung dargestellter Ausführungsbeispiele der Erfindung näher erläutert. Die dargestellte und beschriebene Flügelzellenpumpe stellt nur ein Anwendungsbeispiel der erfindungsgemäßen Regeleinrichtung dar. Statt dessen kann ebenso eine Rollenzellenpumpe oder eine andere Verdrängerpumpe mit einer erfindungsgemäßen Regeleinrichtung versehen werden. Es zeigen:The invention is explained in more detail below with reference to two exemplary embodiments of the invention shown in the drawing. The vane pump shown and described represents only one application example of the control device according to the invention. Instead, a roller cell pump or another displacement pump can also be provided with a control device according to the invention. Show it:
Fig. 1 eine Regeleinrichtung für eine Flügelzellen- pumpe im Längsschnitt nach einem ersten Aus- führungsbeispiel und1 shows a control device for a vane pump in longitudinal section according to a first embodiment and
Fig. 2 einen Stromregelkolben der Regeleinrichtung nach einem zweiten Ausführungsbeispiel .Fig. 2 shows a flow control piston of the control device according to a second embodiment.
In einem durch einen Deckel 1 verschlossenen Gehäuse 2 ist eine Antriebswelle 3 gelagert. Die Antriebswelle 3 trägt in üblicher Weise auf einer Keilverzahnung einen Rotor 4.A drive shaft 3 is mounted in a housing 2 closed by a cover 1. The drive shaft 3 carries a rotor 4 in a conventional manner on a spline.
In radialen Schlitzen des Rotors 4 sind radial bewegliche Flügel 5 geführt, die an einem Kurvenring 6 dichtend entlanggleiten. Eine Druckplatte 7 liegt dichtend an dem aus Rotor 4, Flügeln 5 und Kurvenring 6 bestehenden Pumpen- paket an. Eine weitere Druckplatte 8 liegt durch die Kraft einer Feder 10 auf der anderen Seite an dem Pumpenpaket an. Die Flügel 5 schließen nicht dargestellte Förderkammern zwischen sich ein, die mit einem Sauganschluß 11 in Verbin- düng stehen. Das geförderte Drucköl tritt aus den Förderkammern über ebenfalls nicht dargestellte Drucköffnungen der Druckplatte 8 in eine Druckkammer 12 ein. Die Druckkammer 12 hat über teilringförmige Kanäle 13 und 14 mit Unter- flügelräumen 15 und 16 Verbindung. Dadurch ist es möglich, die jeweils die Druckzone durchlaufenden Flügel 5 nach außen in den Kurvenring 6 zu drücken.Radially movable blades 5 are guided in radial slots of the rotor 4 and slide along a cam ring 6 in a sealing manner. A pressure plate 7 lies sealingly on the pump package consisting of rotor 4, blades 5 and cam ring 6. Another pressure plate 8 rests on the other side of the pump package due to the force of a spring 10. The vanes 5 enclose conveying chambers (not shown) between them, which stand fertilizer. The pumped pressure oil enters a pressure chamber 12 from the delivery chambers via pressure openings 8 of the pressure plate 8, which are also not shown. The pressure chamber 12 has part-ring-shaped channels 13 and 14 with lower wing spaces 15 and 16 connection. This makes it possible to press the vanes 5 passing through the pressure zone outwards into the cam ring 6.
In einer Gehäusebohrung 17 im - in der Zeichnung - unteren Teil der Pumpe sind gleichachsig zueinander einIn a housing bore 17 in the lower part of the pump in the drawing are coaxial with one another
Stromregelventil 18 und eine Drosseleinrichtung 20 eingebaut. Ein Stromregelkolben 21 des Stromregelventils 18 steuert in bekannter Weise mit einem Steuerbund 22 einen Einlaßkanal 23 der Pumpe. In der gezeichneten Ausgangsstel- lung liegt der Steuerbund 22 unter Belastung einer Feder 24 an der Drosseleinrichtung 20 an. Der Einlaßkanal 23 ist dabei durch den Steuerbund 22 verschlossen. In einem rechts von dem Steuerbund 22 liegenden Bohrungsabschnitt 17A sitzt ein Verschlußelement 25, beispielsweise eine Rohrver- schraubung, das mit einem Verbraucher, zum Beispiel einer Hilfskraftlenkung, verbunden wird. Ein Zulaufkanal 26 schließt die Druckkammer 12 an den Bohrungsabschnitt 17A an.Flow control valve 18 and a throttle device 20 installed. A flow control piston 21 of the flow control valve 18 controls an inlet channel 23 of the pump in a known manner with a control collar 22. In the drawn starting position, the control collar 22 rests against the throttle device 20 under the load of a spring 24. The inlet channel 23 is closed by the control collar 22. In a bore section 17A to the right of the control collar 22 there is a closure element 25, for example a pipe screw connection, which is connected to a consumer, for example an auxiliary power steering system. An inlet channel 26 connects the pressure chamber 12 to the bore section 17A.
Die Drosseleinrichtung 20 enthält einen Regelstift 27, der mit dem Stromregelkolben 21 fest verbunden ist und eine Drosselbohrung 28, die an dem Verschlußelement 25 angeordnet und damit mit dem Gehäuse 2 fest verbunden ist. Mit gleicher Wirkung können die beiden Elemente Regelstift 27 und Drosselbohrung 28 auch jeweils mit den anderen Elementen Gehäuse 2 und Stromregelkolben 21 verbunden sein. Der Regelstift 27 weist an seinem freien Ende eine Kontur auf, die die drehzahlabhängige Beeinflussung des an den Verbraucher geleiteten Förderstromes erlaubt. In dem Ausführungsbeispiel enthält diese Kontur einen im wesentli- chen zylindrischen Endabschnitt 30, an den sich ein konischer Abschnitt 31 und ein Abschnitt 32 mit kleinstem Querschnitt anschließen. Zwischen diesem Abschnitt 32 und einer ersten, der Drosseleinrichtung 20 zugewandten Stirnfläche 33 des Stromregelkolbens 21 befindet sich erfindungsgemäß ein verdickter Abschnitt 34 des Regelstiftes 27. Der verdickte Abschnitt 34 erstreckt sich über eine solche axiale Länge, daß bei einer Verschiebung des Stromregelkolbens 21 um einen dieser Länge entsprechenden Weg noch keine Volumenstromregelung erfolgt. Dies bedeutet, daß nach einer solchen Verschiebung noch keine Verbindung zwischen dem von der Druckkammer 12 kommenden Zulaufkanal 26 zu dem Einlaßkanal 23 besteht.The throttle device 20 contains a control pin 27 which is fixedly connected to the flow control piston 21 and a throttle bore 28 which is arranged on the closure element 25 and is thus fixedly connected to the housing 2. The two elements control pin 27 and throttle bore 28 can also be connected to the other elements housing 2 and flow control piston 21 with the same effect. The control pin 27 has at its free end a contour which allows the speed-dependent influencing of the conveying flow directed to the consumer. In the exemplary embodiment, this contour contains an essentially cylindrical end section 30, to which a conical section 31 and a section 32 with the smallest cross section adjoin. Between this section 32 and a first end face 33 of the flow control piston 21 facing the throttle device 20 there is, according to the invention, a thickened section 34 of the control pin 27. The thickened section 34 extends over an axial length such that when the flow control piston 21 is displaced by one of these There is no volume flow control for the corresponding distance. This means that after such a shift there is still no connection between the inlet channel 26 coming from the pressure chamber 12 and the inlet channel 23.
In dem Ausführungsbeispiel nach Fig. 1 weist der ver- dickte Abschnitt 34 eine zylindrische Kontur auf. In dem Ausführungsbeispiel nach Fig. 2 weist der verdickte Abschnitt 35 eine kegelstumpfförmige Kontur auf. Dabei ist der größere Durchmesser des Kegelstumpfes an der ersten Stirnfläche 33 des Stromregelkolbens 21 angeordnet. Dies ist besonders vorteilhaft, weil so die Charakteristik des Regelvorganges, die Regelgeschwindigkeit, sehr fein abgestimmt werden kann.In the exemplary embodiment according to FIG. 1, the thickened section 34 has a cylindrical contour. In the exemplary embodiment according to FIG. 2, the thickened section 35 has a frustoconical contour. The larger diameter of the truncated cone is arranged on the first end face 33 of the flow control piston 21. This is particularly advantageous because the characteristic of the control process, the control speed, can be fine-tuned.
Ein die Feder 24 des Stromregelkolbens 21 aufnehmender Raum 36 steht über eine gestrichelt angedeutete Steuerleitung 37, eine Ringnut 38 und eine Drosselstelle 40 mit einem Auslaß 41, der an dem Verschlußelement 25 angeordnet ist, in Verbindung. Bei bestimmten Ausführungsformen können die Ringnut 38 und die Drosselstelle 40 entfallen. Der Raum 36 wird an seiner einen Seite durch eine zweite Stirnfläche 42 des Stromregelkolbens 21 begrenzt.A space 36 accommodating the spring 24 of the flow control piston 21 is connected via a control line 37 indicated by dashed lines, an annular groove 38 and a throttle point 40 to an outlet 41 which is arranged on the closure element 25. In certain embodiments the annular groove 38 and the throttle point 40 are omitted. The space 36 is delimited on one side by a second end face 42 of the flow control piston 21.
Die Regeleinrichtung arbeitet wie folgt:The control device works as follows:
Der gesamte Förderstrom der Pumpe fließt zunächst über den Zulauf anal 26 in den Bohrungsabschnitt 17A. Bis zum Abregelpunkt bei einer Pumpendrehzahl von zum Beispiel 1000/min fließt der Förderstrom an der Stirnfläche 33 des Steuerbun- des 22 vorbei zu dem Auslaß 41. Der Förderstrom durchströmt den gezeichneten Durchtrittsquerschnitt zwischen dem Regelstift 27 und der Drosselbohrung 28. Dabei verstellt sich durch den entstehenden Druckabfall der Stromregelkolben 21 geringfügig nach links, wobei der Steuerbund 22 jedoch noch nicht mit dem Öffnen des Einlaßkanals 23 beginnt. Durch den sehr klein gehaltenen Drosselquerschnitt zwischen dem verdickten Abschnitt 34 und der Drosselbohrung 28 entsteht eine große Druckdifferenz über der Drosseleinrichtung 20 und damit über dem Stromregelkolben 21. Diese große Druck- differenz erzwingt eine beschleunigte Bewegung des Stromregelkolbens 21. Dies wiederum führt zu einer schnelleren Reaktion des Regelmechanismus, so daß ein Überschwingen und eine Überhöhung der Fördermenge verhindert wird. The entire flow of the pump initially flows via the inlet anal 26 into the bore section 17A. Up to the cut-off point at a pump speed of, for example, 1000 / min, the delivery flow flows past the end face 33 of the control collar 22 to the outlet 41. The delivery flow flows through the passage cross-section drawn between the control pin 27 and the throttle bore 28 resulting pressure drop of the flow control piston 21 slightly to the left, but the control collar 22 does not yet begin to open the inlet channel 23. The very small throttle cross section between the thickened section 34 and the throttle bore 28 creates a large pressure difference across the throttle device 20 and thus above the flow control piston 21. This large pressure difference forces an accelerated movement of the flow control piston 21. This in turn leads to a faster reaction of the control mechanism, so that overshoot and excessive delivery is prevented.
Bezugszeichenreference numeral
1 Deckel1 lid
2 Gehäuse2 housings
3 Antriebswelle3 drive shaft
4 Rotor4 rotor
5 Flügel5 wings
6 Kurvenring6 curve ring
7 Druckplatte7 pressure plate
8 Druckplatte8 pressure plate
9 -9 -
10 Feder10 spring
11 Sauganschluß11 suction connection
12 Druckkammer12 pressure chamber
13 teilringförmiger Kanal13 partially annular channel
14 teilringförmiger Kanal14 partially annular channel
15 Unterflügelraum15 lower wing room
16 Unterflügelraum16 lower wing room
17 Gehäusebohrung17 Housing bore
17A Bohrungsabschnitt17A bore section
18 Stromregelventil18 flow control valve
19 -19 -
20 Drosseleinrichtung20 throttle device
21 Stromregelkolben21 flow control pistons
22 Steuerbund22 Tax Association
23 Einlaßkanal23 inlet duct
24 Feder24 spring
25 Verschlußelement25 closure element
26 Zulaufkanal26 inlet channel
27 Regelstift27 control pin
28 Drosselbohrung28 throttle bore
29 - Endabschnitt konischer Abschnitt Abschnitt mit kleinstem Querschnitt erste Stirnfläche verdickter Abschnitt verdickter Abschnitt (konisch) Raum Steuerleitung Ringnut29 - End section conical section Section with the smallest cross section first end face thickened section thickened section (conical) space control line ring groove
Drosselstelle Auslaß zweite Stirnfläche Throttling point outlet second face

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Regeleinrichtung für Verdrängerpumpen, insbesondere Flügelzellenpumpen, mit folgenden Merkmalen:1. Control device for positive displacement pumps, in particular vane pumps, with the following features:
Ein Druckraum (12) der Pumpe steht über eine Drosseleinrichtung (20) mit einem an einen Verbraucher angeschlossenen Auslaß (41) in Verbindung; eine erste Stirnfläche (33) eines in einer Gehäuseboh- rung (17) verschiebbaren Stromregelkolbens (21) steht mit dem Druckraum (12) in Verbindung; eine zweite Stirnfläche (42) des Stromregelkolbens (21) begrenzt einen Raum (36) , der an den Auslaß (41) angeschlossen ist; - der Stromregelkolben (21) gibt in Abhängigkeit eines auf die beiden Stirnflächen wirkenden Differenzdruckes eine Verbindung von dem Druckraum (12) zu einem Einlaßkanal (23) der Pumpe frei, die Drosseleinrichtung (20) sitzt im Druckausgang (Bohrungsabschnitt 17A) der Pumpe und enthält einen Regelstift (27), dessen Steuerkontur so ausgeführt ist, daß sich zusammen mit einer Drosselbohrung (28) ein veränderbarer Durchtrittsquerschnitt ergibt, wobei eines der beiden Elemente Regelstift (27) und Drossel- bohrung (28) mit dem Stromregelkolben (21) verbunden und das andere der beiden Elemente gehäusefest ist, dadurch g e k e n n z e i c h n e t , daß der Regelstift (27) in einem axialen Verstell-Bereich der Drosseleinrichtung (20), der bei dem Stromregelkolben (21) noch nicht zur Volumenstromregelung herangezogen wird, einen verdickten Abschnitt aufweist, so daß in diesem Verschiebe- Bereich ein minimaler Blendenquerschnitt besteht. A pressure chamber (12) of the pump is connected via a throttle device (20) to an outlet (41) connected to a consumer; a first end face (33) of a flow control piston (21) displaceable in a housing bore (17) is connected to the pressure chamber (12); a second end face (42) of the flow control piston (21) delimits a space (36) which is connected to the outlet (41); - The flow control piston (21) releases a connection from the pressure chamber (12) to an inlet channel (23) of the pump depending on a differential pressure acting on the two end faces, the throttle device (20) sits in the pressure outlet (bore section 17A) of the pump and contains a control pin (27), the control contour of which is designed such that, together with a throttle bore (28), there is a variable passage cross section, one of the two elements control pin (27) and throttle bore (28) being connected to the flow control piston (21) and the other of the two elements is fixed to the housing, characterized in that the control pin (27) has a thickened section in an axial adjustment region of the throttle device (20), which is not yet used for volume flow control in the flow control piston (21), so that there is a minimal aperture cross-section in this shifting range.
2. Regeleinrichtung nach Anspruch 1, dadurch g e k e n n z e i c h n e t , daß der Regelstift (27) mit dem Stromregelkolben (21) verbunden und die Drosselbohrung (28) gehäusefest ist.2. Control device according to claim 1, characterized in that the control pin (27) is connected to the flow control piston (21) and the throttle bore (28) is fixed to the housing.
3. Regeleinrichtung nach Anspruch 2, dadurch g e k e n n z e i c h n e t , daß der verdickte Abschnitt (34) des Regelstiftes (27) eine zylindrische Kontur aufweist und daß der verdickte Abschnitt (34) an der ersten Stirnfläche (33) des Stromregelkolbens (21) angeordnet ist.3. Control device according to claim 2, characterized in that the thickened section (34) of the control pin (27) has a cylindrical contour and that the thickened section (34) is arranged on the first end face (33) of the flow control piston (21).
4. Regeleinrichtung nach Anspruch 2, dadurch g e k e n n z e i c h n e t , daß der verdickte Abschnitt (35) des Regelstiftes (27) eine kegelstumpfförmige Kontur aufweist, wobei der größere Durchmesser des Kegelstumpfes an der ersten Stirnfläche (33) des Stromregelkolbens (21) angeordnet ist. 4. Control device according to claim 2, characterized in that the thickened section (35) of the control pin (27) has a truncated cone-shaped contour, the larger diameter of the truncated cone being arranged on the first end face (33) of the flow control piston (21).
EP01902363A 2000-02-11 2001-01-30 Control device for positive displacement pumps Expired - Lifetime EP1259737B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10006140A DE10006140A1 (en) 2000-02-11 2000-02-11 Control system for vane and other displacement pumps has a thickened section at the control pin to prevent temporary increase in the pumped volume/pressure on a rapid acceleration
DE10006140 2000-02-11
PCT/EP2001/000955 WO2001059301A1 (en) 2000-02-11 2001-01-30 Control device for positive displacement pumps

Publications (2)

Publication Number Publication Date
EP1259737A1 true EP1259737A1 (en) 2002-11-27
EP1259737B1 EP1259737B1 (en) 2004-01-07

Family

ID=7630612

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01902363A Expired - Lifetime EP1259737B1 (en) 2000-02-11 2001-01-30 Control device for positive displacement pumps

Country Status (6)

Country Link
US (1) US7059838B2 (en)
EP (1) EP1259737B1 (en)
JP (1) JP2003522884A (en)
DE (2) DE10006140A1 (en)
ES (1) ES2213685T3 (en)
WO (1) WO2001059301A1 (en)

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JP3893959B2 (en) * 2001-11-29 2007-03-14 アイシン精機株式会社 Oil pump pressure regulating valve mechanism mounting structure
DE10233579A1 (en) * 2002-07-24 2004-02-05 Zf Lenksysteme Gmbh Impeller pump flow regulation valve has a control spring with lengths having different spring constants so that the pump characteristic curve is linear, even at high flow rates
US20040022654A1 (en) * 2002-08-05 2004-02-05 Takashi Ishida Piston type small discharge pump
US8425204B2 (en) * 2004-06-24 2013-04-23 Luk Automobiltechnik Gmbh & Co. Kg Pump
DE102005043253B4 (en) * 2005-09-09 2014-09-04 Zf Lenksysteme Gmbh Method for producing a positive displacement pump and a positive displacement pump produced thereafter
US8333576B2 (en) * 2008-04-12 2012-12-18 Steering Solutions Ip Holding Corporation Power steering pump having intake channels with enhanced flow characteristics and/or a pressure balancing fluid communication channel
US9127674B2 (en) * 2010-06-22 2015-09-08 Gm Global Technology Operations, Llc High efficiency fixed displacement vane pump including a compression spring
JP2016109029A (en) * 2014-12-05 2016-06-20 株式会社デンソー Vane type pump and fuel vapor leakage detecting device using the same

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Title
See references of WO0159301A1 *

Also Published As

Publication number Publication date
DE10006140A1 (en) 2001-08-16
WO2001059301A1 (en) 2001-08-16
US20030113216A1 (en) 2003-06-19
DE50101292D1 (en) 2004-02-12
ES2213685T3 (en) 2004-09-01
US7059838B2 (en) 2006-06-13
EP1259737B1 (en) 2004-01-07
JP2003522884A (en) 2003-07-29

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