EP0840851A1 - Pump - Google Patents

Pump

Info

Publication number
EP0840851A1
EP0840851A1 EP96925712A EP96925712A EP0840851A1 EP 0840851 A1 EP0840851 A1 EP 0840851A1 EP 96925712 A EP96925712 A EP 96925712A EP 96925712 A EP96925712 A EP 96925712A EP 0840851 A1 EP0840851 A1 EP 0840851A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
suction valve
line
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.)
Withdrawn
Application number
EP96925712A
Other languages
German (de)
French (fr)
Inventor
Hans-Jörg Feigel
Lothar Schiel
Ulrich Neumann
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.)
Continental Teves AG and Co OHG
Original Assignee
ITT Automotive Europe GmbH
Alfred Teves 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 ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Publication of EP0840851A1 publication Critical patent/EP0840851A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/12—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid
    • B60T13/16—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being liquid using pumps directly, i.e. without interposition of accumulators or reservoirs
    • B60T13/168—Arrangements for pressure supply
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/08—Control regulated by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/3205—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration acceleration
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/321—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration deceleration

Definitions

  • the present invention relates to a pump with the features of the preamble of claim 1.
  • Such a pump is known for example from DE 35 10 633 AI.
  • a piston pump is known which is provided with a plurality of cylinder-piston units, one of which is intended to supply the suction lines of the other cylinder-piston units with pressure medium under pressure.
  • the suction valve devices of the individual cylinder-piston units have non-return valves which are under prestress and which only open from a minimum pressure in the suction line. If this minimum pressure is not present, the piston cannot draw in any pressure medium and remains in its rest position, i.e. it is not in contact with the eccentric that drives it.
  • a disadvantage of this known piston pump is that an upstream pressure is required, for which at least one additional cylinder-piston unit is required.
  • the maximum volume flow of the pump is limited by the delivery rate of this cylinder-piston unit.
  • the object of the present invention is to propose a pump which is both capable of delivering a high volume flow and, as required, temporarily deactivating one or more of its cylinder-piston units. This problem is solved by the measures specified in the characterizing part of claim 1 and in the subclaims.
  • At least one of the suction valve devices opens depending on the pressure in the pressure line. Therefore, no pre-pressure is required on the suction line, i.e. none of the pistons has to be used as a backing pump, the volume flow is not limited by the delivery rate of such a backing pump.
  • the opening of the suction valve device corresponds to an idling of the assigned piston, i.e. a lower volume flow and a lower power consumption of the pump. As long as there is a high volume requirement by the consumer, the pressure in the pressure line is low, the suction valve device remains closed during the pressure stroke.
  • the suction valve device If the pressure in the pressure line exceeds a certain switching pressure, the suction valve device also opens during the pressure stroke, and the pressure medium can be conveyed back from the work space into the suction line almost without pressure. Only friction losses occur, the power consumption of the pump is low.
  • the measure according to the invention can be used particularly advantageously in radial piston pumps, the pistons of which are coupled to the eccentric and therefore cannot remain immobile in a rest position, as is possible with the pump known from the prior art.
  • the opening of the suction valve device advantageously takes place in a positively controlled manner.
  • This can be done, for example, via an electromagnetically actuated valve which is controlled by suitable pressure detection and control devices. It is also advantageously possible to carry out the aforementioned positive control hydraulically.
  • an actuating member can be provided which can be acted upon by the pressure in the pressure line on the one hand and on the other hand can act on a closing member of the suction valve device in the opening direction.
  • the suction line acts as a damping chamber for smoothing pressure pulses occurring in the pressure line.
  • the assigned pump pistons can be switched off one after the other.
  • the switching pressures are staggered, e.g. aquidistant or in another staggering, adjusted to the volume flow requirement or the pressure requirement of the consumer. This enables a reduction in the power consumption of the pump with simultaneous optimization to the needs of the connected consumer, since only the required number of pump pistons is in operation, which is necessary to maintain the required volume flow or the required pressure.
  • a simple possibility to set the different switching pressures is that the spring elements of the suction valve devices have different spring rates or are prestressed to different extents.
  • the pump according to the invention is advantageously used as a pressure medium source in auxiliary vehicle pressure systems, in particular for hydraulic steering boosters, brake boosters or electronically controlled power brake systems, such as anti-lock braking systems, traction control, driving stability control or systems for driver-independent actuation of the braking system.
  • auxiliary vehicle pressure systems in particular for hydraulic steering boosters, brake boosters or electronically controlled power brake systems, such as anti-lock braking systems, traction control, driving stability control or systems for driver-independent actuation of the braking system.
  • a volume flow-pressure characteristic curve is often desired, which can be set using the pump according to the invention.
  • this does not exclude that corresponding pumps are also suitable for other applications.
  • Fig. 1 is a schematic representation of a pump according to the invention with four pump pistons and
  • Fig. 2 shows a pump characteristic of a pump according to the invention.
  • Fig. 1 shows a schematic representation of a section through the housing 1 of a pump according to the invention.
  • a suction port 2 and a pressure port 3 are arranged in the housing 1.
  • Suction lines 4 lead via prechambers 6 to suction valve devices 8 of the pump pistons 10.
  • the pump pistons 10 are guided in holes 11 and driven by an eccentric.
  • the end of the pump piston 10 facing away from the eccentric 12 delimits a working chamber 13 which is connected to the prechamber 6 via the suction valve device 8, consisting of spring 14, closing member 15 and valve seat 16.
  • the working chamber 13 is connected to the pressure line 5 via a pressure valve device 9.
  • the pump pistons 10 are sealed off from the bore 11 by sealing elements 17.
  • Damping chambers 7 are arranged in the pressure line 5 in the vicinity of the pressure valve devices 9.
  • the damping chambers 7 are delimited by a movable control piston 18, which is displaceable in the antechamber 6 and is arranged in a sealed manner by means of a sealing element 19.
  • a spring element 20 which prestresses the control piston 18 into its rest position close to the damping chamber.
  • a stop 21 limits the possible stroke of the control piston 18 in the position facing away from its rest position.
  • the control piston 18 is provided with an actuating member 22 which, in the actuated position of the control piston 18, see page A of FIG. 1, removes the closing member 15 of the suction valve device 8 from its valve seat 16 and thus the working chamber 13 with the suction line 4 connects. This forced opening of the suction valve device 8 takes place after the control piston 18 has covered an empty travel a.
  • the eccentric 12 executes an eccentric movement and thereby displaces the pump pistons 10 in a radial direction with respect to the eccentric 12.
  • the suction valve device 8 is open and pressure medium reaches the working chamber 13 from the suction line 4 (see, for example, page D of FIG. 1).
  • the working chamber 13 has reached its largest volume.
  • the pressure stroke begins, at the beginning of which the suction valve device 8 closes and the pressure valve device 9 opens (see page B of FIG. 1).
  • the pressure medium is now ter pressure from the working chamber 13 pressed into the pressure line 5.
  • the pressure in the damping chamber 7 also rises, whereby the control piston 18 is displaced from its rest position as soon as the force exerted on the damping chamber side exceeds the restoring force of the spring element 20.
  • the control piston 18 yields, as a result of which pressure pulsations in the pressure line 5 are smoothed.
  • the actuating member 22 opens the associated suction valve device 8, whereby the corresponding piston in each of its working positions, i.e. also connected to the suction line 4 during the pressure stroke, i.e. is short-circuited. That is, it is idling (side A of Fig. 1).
  • This piston now neither contributes to increasing the volume flow nor to the power consumption of the pump.
  • the spring rates of the spring elements 20 are of different sizes, so that the switching pressures required for the forced opening of the corresponding suction valve devices 8 are of different sizes.
  • the control piston 18 on side A of FIG. 1 already reaches its end position at a pressure p which is lower than the pressure p 2 at which the control piston 18 on side C of FIG. 1 reaches its end position.
  • the control pressure p 2 is in turn lower than the control pressure p 3 at which the control valve unit 8 is opened on the side B of FIG. 1.
  • At least one of the pump pistons 10, in FIG. 1 on side D, has no actuating member 22 and thus contributes to the volume flow and the pressure build-up in the pressure line 5 at all times.
  • the free travel a of the control piston 18 is such that a Pressure pulsation compensation is possible without a simultaneous forced opening of the control valve unit 8.
  • FIG. 2 shows a pump characteristic of a pump according to the invention.
  • the volume flow Q is plotted against the hydraulic pressure p.
  • the upper line b shows the characteristic of a conventional pump, which should be able to generate both a maximum volume flow Q max and a maximum pressure p max .
  • Line c shows the characteristics of the pump according to the invention when all four pistons are in operation. At a switching pressure pj, a pump piston 10 (on
  • the pump according to the invention is preferably electrically driven and can be used without a pressure accumulator, for example for a brake booster or a steering booster. Due to the special training of a typical pressure-volume characteristic curve g, in particular in a motor vehicle brake system, and the driver's ability to actuate a motor vehicle is a very high volume flow from the auxiliary pressure generator in a first phase of braking at low load pressure (pump characteristic c) and in a second phase a high pump pressure with a low volume flow (pump characteristic g) is required. These extreme requirements mean that the electric motor driving the pump has to be designed with high corner power and at the same time high mass moments of inertia. This problem can be solved by changing the delivery volume Q depending on the pressure.
  • the pump according to the invention offers a possible solution that is much cheaper to implement for use in a motor vehicle.
  • the pressure-side damping chamber 7 receives the control piston 18 designed as a damping piston, which in turn interacts with a spring element 20 which dampens pressure peaks on the one hand and after reaching a structurally determined pressure level
  • the suction valve device 8 open enables.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

The present invention relates to a pump, especially a radial piston pump, having at least two pistons (10) with their working chambers (13), in which the working chambers (13) are connected via intake valve systems (8) to intake pipes (4) and via pressure valve systems (9) to a common pressure pipe (5), where at least one of the intake valve systems (8) opens during the pressure stroke depending on the pressure in one of the relevant pipes (4, 5) and at least one of the intake valve systems (8) opens during the pressure stroke depending on the pressure in the pressure pipe (5).

Description

Pumpepump
Die vorliegende Erfindung befaßt sich mit einer Pumpe mit den Merkmalen des Oberbegriffs des Anspruchs 1.The present invention relates to a pump with the features of the preamble of claim 1.
Eine derartige Pumpe ist beispielweise aus der DE 35 10 633 AI bekannt. Aus dieser Schrift ist eine Kolbenpumpe bekannt, die mit mehreren Zylinder-Kolben-Einheiten versehen ist, von denen eine dazu bestimmt ist, die Saugleitungen der anderen Zylinder-Kolben-Einheiten mit unter Druck stehendem Druck¬ mittel zu versorgen. Die Saugventileinrichtungen der einzel¬ nen Zylinder-Kolben-Einheiten weisen unter Vorspannung ste¬ hende Rückschlagventile auf, die erst ab einem Mindestdruck in der Saugleitung öffnen. Liegt dieser Mindestdruck nicht an, so kann der Kolben kein Druckmittel ansaugen und ver¬ bleibt in seiner Ruhestellung, d.h., er liegt nicht an dem ihn antreibenden Exzenter an.Such a pump is known for example from DE 35 10 633 AI. From this document a piston pump is known which is provided with a plurality of cylinder-piston units, one of which is intended to supply the suction lines of the other cylinder-piston units with pressure medium under pressure. The suction valve devices of the individual cylinder-piston units have non-return valves which are under prestress and which only open from a minimum pressure in the suction line. If this minimum pressure is not present, the piston cannot draw in any pressure medium and remains in its rest position, i.e. it is not in contact with the eccentric that drives it.
Als nachteilig an dieser bekannten Kolbenpumpe ist anzusehen, daß ein Vordruck auf der Saugseite erforderlich ist, wofür mindestens eine weitere Zylinder-Kolben-Einheit benötigt wird. Der maximale Volumenstrom der Pumpe wird durch die För¬ derleistung dieser Zylinder-Kolben-Einheit begrenzt.A disadvantage of this known piston pump is that an upstream pressure is required, for which at least one additional cylinder-piston unit is required. The maximum volume flow of the pump is limited by the delivery rate of this cylinder-piston unit.
Aufgabe der vorliegenden Erfindung ist es, eine Pumpe vor¬ zuschlagen, die sowohl in der Lage ist einen hohen Volumen¬ strom zu liefern als auch bedarfsabhängig eine oder mehrere ihrer Zylinder-Kolben-Einheiten vorübergehend außer Betrieb zu setzen. Gelöst wird diese Aufgabe durch die im kennzeichnenden Teil des Anspruchs 1 sowie die in den Unteransprüchen angegebenen Maßnahmen.The object of the present invention is to propose a pump which is both capable of delivering a high volume flow and, as required, temporarily deactivating one or more of its cylinder-piston units. This problem is solved by the measures specified in the characterizing part of claim 1 and in the subclaims.
Erfindungsgemäß ist vorgesehen, daß zumindest eine der Saug¬ ventileinrichtungen in Abhängigkeit vom Druck in der Druck¬ leitung öffnet. Es ist daher kein Vordruck auf der Sauglei¬ tung erforderlich, d.h. keiner der Kolben muß als Vorpumpe eingesetzt werden, der Volumenstrom ist nicht durch die För¬ derleistung einer derartigen Vorpumpe begrenzt. Das Öffnen der Saugventileinrichtung entspricht einem Leerlauf des zu¬ geordneten Kolbens, d.h. einem geringeren Volumenstrom und einer geringeren Leistungsaufnahme der Pumpe. Solange ein hoher Volumenbedarf beim Verbraucher besteht, ist der Druck in der Druckleitung niedrig, die Saugventileinrichtung bleibt während des Druckhubs geschlossen. Übersteigt der Druck in der Druckleitung einen bestimmten Schaltdruck, so öffnet die Saugventileinrichtung auch während des Druckhubs, das Druck¬ mittel kann aus dem Arbeitsraum nahezu drucklos in die Saug¬ leitung zurückgefördert werden. Dabei treten lediglich Rei¬ bungsverluste auf, die Leistungsaufnahme der Pumpe ist ge¬ ring. Die erfindungsgemäße Maßnahme ist besonders vorteilhaft bei Radialkolbenpumpen einsetzbar, deren Kolben an den Exzen¬ ter gekoppelt sind und daher nicht unbeweglich in einer Ruhe¬ stellung verharren können, wie das bei der aus dem Stand der Technik bekannten Pumpe der möglich ist.According to the invention it is provided that at least one of the suction valve devices opens depending on the pressure in the pressure line. Therefore, no pre-pressure is required on the suction line, i.e. none of the pistons has to be used as a backing pump, the volume flow is not limited by the delivery rate of such a backing pump. The opening of the suction valve device corresponds to an idling of the assigned piston, i.e. a lower volume flow and a lower power consumption of the pump. As long as there is a high volume requirement by the consumer, the pressure in the pressure line is low, the suction valve device remains closed during the pressure stroke. If the pressure in the pressure line exceeds a certain switching pressure, the suction valve device also opens during the pressure stroke, and the pressure medium can be conveyed back from the work space into the suction line almost without pressure. Only friction losses occur, the power consumption of the pump is low. The measure according to the invention can be used particularly advantageously in radial piston pumps, the pistons of which are coupled to the eccentric and therefore cannot remain immobile in a rest position, as is possible with the pump known from the prior art.
Vorteilhafterweise erfolgt das Öffnen der Saugventileinrich¬ tung zwangsgesteuert. Dies kann beispielsweise über ein elek¬ tromagnetisch betätigbares Ventil erfolgen, welches über ge¬ eignete Druckerfassungs- und Steuerungseinrichtungen ange¬ steuert wird. Es ist ebenfalls vorteilhaft möglich, die ge¬ nannte Zwangssteuerung hydraulisch auszuführen. Dazu kann beispielsweise ein Betätigungsglied vorgesehen sein, welches einerseits von dem Druck in der Druckleitung beaufschlagbar ist und andererseits auf ein Schließglied der Saugventilein¬ richtung in Öffnungsrichtung einwirken kann.The opening of the suction valve device advantageously takes place in a positively controlled manner. This can be done, for example, via an electromagnetically actuated valve which is controlled by suitable pressure detection and control devices. It is also advantageously possible to carry out the aforementioned positive control hydraulically. This can for example, an actuating member can be provided which can be acted upon by the pressure in the pressure line on the one hand and on the other hand can act on a closing member of the suction valve device in the opening direction.
Erfindungsgemäß ist vorgesehen, ein derartiges Schließglied mit einem Steuerkolben zu verbinden, der einerseits mit der Druckleitung und andererseits mit der Saugleitung verbunden ist. Die Saugleitung wirkt in diesem Fall als Dämpfungskammer zum Glätten von in der Druckleitung auftretenden Druckpulsa¬ tionen.According to the invention, it is provided to connect such a closing member to a control piston which is connected on the one hand to the pressure line and on the other hand to the suction line. In this case, the suction line acts as a damping chamber for smoothing pressure pulses occurring in the pressure line.
Werden mehrere Saugventileinrichtungen in Abhängigkeit vom Druck in der Druckleitung geöffnet, wobei die Schaltdruck¬ werte unterschiedlich groß sind, so können die zugeordneten Pumpenkolben nacheinander abgeschaltet werden. Die Schalt¬ drücke sind dazu gestaffelt, z.B. aquidistant oder in einer anderen, auf den Volumenstrombedarf bzw. den Druckbedarf des Verbrauchers abgestimmten Staffelung. Dies ermöglicht eine Reduzierung der Leistungsaufnahme der Pumpe bei gleichzeiti¬ ger Optimierung an den Bedarf des angeschlossenen Verbrau¬ chers, da jeweils nur die erforderliche Anzahl Pumpenkolben in Betrieb ist, die erforderlich ist, um den erforderlichen Volumenstrom bzw. den erforderlichen Druck aufrechtzuerhal¬ ten.If several suction valve devices are opened depending on the pressure in the pressure line, the switching pressure values being different, the assigned pump pistons can be switched off one after the other. The switching pressures are staggered, e.g. aquidistant or in another staggering, adjusted to the volume flow requirement or the pressure requirement of the consumer. This enables a reduction in the power consumption of the pump with simultaneous optimization to the needs of the connected consumer, since only the required number of pump pistons is in operation, which is necessary to maintain the required volume flow or the required pressure.
Eine einfache Möglichkeit die verschiedenen Schaltdrücke ein¬ zustellen, besteht darin, daß die Federelemente der Saugven¬ tileinrichtungen unterschiedliche Federraten aufweisen bzw. verschieden stark vorgespannt sind.A simple possibility to set the different switching pressures is that the spring elements of the suction valve devices have different spring rates or are prestressed to different extents.
Die erfindungsgemäße Pumpe wird vorteilhafterweise als Druck¬ mittelquelle in Kraftfahrzeughilfsdruckanlagen eingesetzt, insbesondere für hydraulische Lenkkraftverstärker, Brems¬ kraftverstärker oder elektronisch angesteuerte Fremdkraft- bremsanlagen, wie Antiblockiersystem, Antriebsschlupfrege- lung, Fahrstabilitätsregelung oder Anlage zum fahrerunabhän¬ gigen Betätigen der Bremsanlage. Bei derartigen Anlagen ist oftmals eine Volumenstrom-Druck-Kennlinie erwünscht, die sich mit der erfindungsgemäßen Pumpe einstellen läßt. Dies schließt natürlich nicht aus, daß entsprechende Pumpen auch für andere Anwendungsfälle geeignet sind.The pump according to the invention is advantageously used as a pressure medium source in auxiliary vehicle pressure systems, in particular for hydraulic steering boosters, brake boosters or electronically controlled power brake systems, such as anti-lock braking systems, traction control, driving stability control or systems for driver-independent actuation of the braking system. In systems of this type, a volume flow-pressure characteristic curve is often desired, which can be set using the pump according to the invention. Of course, this does not exclude that corresponding pumps are also suitable for other applications.
Weitere Vorteile der Erfindung ergeben sich aus der nachfol¬ genden Beschreibung anhand von Abbildungen.Further advantages of the invention result from the following description with the aid of illustrations.
Dabei zeigen:Show:
Fig. 1 eine schematische Darstellung einer erfindungsgemä¬ ßen Pumpe mit vier Pumpenkolben undFig. 1 is a schematic representation of a pump according to the invention with four pump pistons and
Fig. 2 eine Pumpencharakteristik einer erfindungsgemäßen Pumpe.Fig. 2 shows a pump characteristic of a pump according to the invention.
Fig. 1 zeigt in schematischer Darstellung einen Schnitt durch das Gehäuse 1 einer erfindungsgemäßen Pumpe. Im Gehäuse 1 ist ein Sauganschluß 2 und ein Druckanschluß 3 angeordnet. Saug¬ leitungen 4 führen über Vorkammern 6 zu Saugventileinrichtun¬ gen 8 der Pumpenkolben 10. Die Pumpenkolben 10 sind in Boh¬ rungen 11 geführt und von einem Exzenter angetrieben. Das dem Exzenter 12 abgewandte Ende der Pumpenkolben 10 begrenzt eine Arbeitskammer 13, die über die Saugventileinrichtung 8, be¬ stehend aus Feder 14, Schließglied 15 und Ventilsitz 16 mit der Vorkammer 6 verbunden ist. Die Arbeitskammer 13 ist über eine Druckventileinrichtung 9 mit der Druckleitung 5 verbun¬ den. Die Pumpenkolben 10 sind durch Dichtelemente 17 gegenüber der Bohrung 11 abgedichtet. In der Druckleitung 5 sind in der Nähe der Druckventileinrichtungen 9 Dämpfungskammem 7 an¬ geordnet. Die Dämpfungskammern 7 werden von einem beweglichen Steuerkolben 18 begrenzt, der in der Vorkammer 6 verschiebbar und mittels eines Dichtelements 19 abgedichtet angeordnet ist. In der Vorkammer 6 ist weiterhin ein Federelement 20 angeordnet, welches den Steuerkolben 18 in seine dämpfungs- kammernahe Ruhestellung vorspannt. Ein Anschlag 21 begrenzt den möglichen Hubweg des Steuerkolbens 18, in der seiner Ru¬ hestellung abgewandten Position. Weiterhin der ist der Steu¬ erkolben 18 mit einem Betätigungsglied 22 versehen, welches in der betätigten Stellung des Steuerkolbens 18, siehe Seite A der Fig. 1, das Schließglied 15 der Saugventileinrichtung 8 von seinem Ventilsitz 16 entfernt und somit die Arbeitskammer 13 mit der Saugleitung 4 verbindet. Dieses zwangsweise Öffnen der Saugventileinrichtung 8 erfolgt, nachdem der Steuerkolben 18 einen Leerweg a zurückgelegt hat.Fig. 1 shows a schematic representation of a section through the housing 1 of a pump according to the invention. A suction port 2 and a pressure port 3 are arranged in the housing 1. Suction lines 4 lead via prechambers 6 to suction valve devices 8 of the pump pistons 10. The pump pistons 10 are guided in holes 11 and driven by an eccentric. The end of the pump piston 10 facing away from the eccentric 12 delimits a working chamber 13 which is connected to the prechamber 6 via the suction valve device 8, consisting of spring 14, closing member 15 and valve seat 16. The working chamber 13 is connected to the pressure line 5 via a pressure valve device 9. The pump pistons 10 are sealed off from the bore 11 by sealing elements 17. Damping chambers 7 are arranged in the pressure line 5 in the vicinity of the pressure valve devices 9. The damping chambers 7 are delimited by a movable control piston 18, which is displaceable in the antechamber 6 and is arranged in a sealed manner by means of a sealing element 19. In the prechamber 6 there is also a spring element 20 which prestresses the control piston 18 into its rest position close to the damping chamber. A stop 21 limits the possible stroke of the control piston 18 in the position facing away from its rest position. Furthermore, the control piston 18 is provided with an actuating member 22 which, in the actuated position of the control piston 18, see page A of FIG. 1, removes the closing member 15 of the suction valve device 8 from its valve seat 16 and thus the working chamber 13 with the suction line 4 connects. This forced opening of the suction valve device 8 takes place after the control piston 18 has covered an empty travel a.
Funktionsweise der Pumpe:How the pump works:
Der Exzenter 12 führt eine exzentrische Bewegung aus, und verschiebt dabei die Pumpenkolben 10 in bezüglich des Exzen¬ ters 12 radialer Richtung. Solange sich der Pumpenkolben 10 radial nach innen bewegt, vergrößert sich das Volumen der Arbeitskammer 13, die Saugventileinrichtung 8 ist geöffnet und Druckmittel gelangt aus der Saugleitung 4 in die Arbeits¬ kammer 13 (s. beispielsweise Seite D der Fig. 1). Ist der Pumpenkolben 10 am unteren Totpunkt angelangt (s.Seite C der Fig. 1), so hat die Arbeitskammer 13 ihr größtes Volumen er¬ reicht. Nun beginnt der Druckhub, zu dessen Beginn die Saug¬ ventileinrichtung 8 schließt und die Druckventileinrichtung 9 öffnet (s. Seite B der Fig. 1). Das Druckmittel wird nun un- ter Druck aus der Arbeitskammer 13 in die Druckleitung 5 ge¬ preßt. Damit steigt auch der Druck in der Dämpfungskammer 7 an, wodurch der Steuerkolben 18 aus seiner Ruhestellung ver¬ schoben wird, sobald die auf ihn dämpfungskammerseitig ausge¬ übte Kraft die Rückstellkraft des Federelements 20 über¬ schreitet. Der Steuerkolben 18 gibt nach, wodurch Druckpulsa¬ tionen in der Druckleitung 5 geglättet werden.The eccentric 12 executes an eccentric movement and thereby displaces the pump pistons 10 in a radial direction with respect to the eccentric 12. As long as the pump piston 10 moves radially inward, the volume of the working chamber 13 increases, the suction valve device 8 is open and pressure medium reaches the working chamber 13 from the suction line 4 (see, for example, page D of FIG. 1). When the pump piston 10 has reached bottom dead center (see page C of FIG. 1), the working chamber 13 has reached its largest volume. Now the pressure stroke begins, at the beginning of which the suction valve device 8 closes and the pressure valve device 9 opens (see page B of FIG. 1). The pressure medium is now ter pressure from the working chamber 13 pressed into the pressure line 5. The pressure in the damping chamber 7 also rises, whereby the control piston 18 is displaced from its rest position as soon as the force exerted on the damping chamber side exceeds the restoring force of the spring element 20. The control piston 18 yields, as a result of which pressure pulsations in the pressure line 5 are smoothed.
Ist der Druck in der Druckleitung 5 so hoch, daß der Steuer¬ kolben 18 bis an seinen der Dämpfungskammer 7 abgewandten Endanschlag gelangt, so öffnet das Betätigungsglied 22 die zugeordnet Saugventileinrichtung 8, wodurch der entsprechende Kolben in jeder seiner Arbeitsstellungen, d.h. auch während des Druckhubs mit der Saugleitung 4 verbunden, d.h. kurzge¬ schlossen ist. Das heißt, er läuft somit im Leerlauf (Seite A der Fig. 1). Dieser Kolben trägt nun weder zur Erhöhung des Volumenstroms noch zur Leistungsaufnahme der Pumpe bei.If the pressure in the pressure line 5 is so high that the control piston 18 reaches its end stop facing away from the damping chamber 7, the actuating member 22 opens the associated suction valve device 8, whereby the corresponding piston in each of its working positions, i.e. also connected to the suction line 4 during the pressure stroke, i.e. is short-circuited. That is, it is idling (side A of Fig. 1). This piston now neither contributes to increasing the volume flow nor to the power consumption of the pump.
Die Federraten der Federelemente 20 sind unterschiedlich groß ausgelegt, so daß die zur zwangsweisen Öffnung der entspre¬ chenden Saugventileinrichtungen 8 erforderlichen Schaltdrücke unterschiedlich groß sind. Beispielsweise erreicht der Steu¬ erkolben 18 auf Seite A der Fig. 1 seine Endstellung bereits bei einem Druck p, der niederiger ist als der Druck p2, bei dem der Steuerkolben 18 auf Seite C der Fig, 1 seine Endstel¬ lung erreicht. Der Steuerdruck p2 ist wiederum niedriger als der Steuerdruck p3, bei dem die Steuerventileinheit 8 auf der Seite B der Fig. 1 geöffnet wird. Zumindest einer der Pumpen¬ kolben 10, in Fig. 1 auf Seite D, weist kein Betätigungsglied 22 auf, und trägt somit jederzeit zum Volumenstrom und zum Druckaufbau in der Druckleitung 5 bei.The spring rates of the spring elements 20 are of different sizes, so that the switching pressures required for the forced opening of the corresponding suction valve devices 8 are of different sizes. For example, the control piston 18 on side A of FIG. 1 already reaches its end position at a pressure p which is lower than the pressure p 2 at which the control piston 18 on side C of FIG. 1 reaches its end position. The control pressure p 2 is in turn lower than the control pressure p 3 at which the control valve unit 8 is opened on the side B of FIG. 1. At least one of the pump pistons 10, in FIG. 1 on side D, has no actuating member 22 and thus contributes to the volume flow and the pressure build-up in the pressure line 5 at all times.
Der Leerweg a der Steuerkolben 18 ist so bemessen, daß ein Druckpulsationsausgleich möglich ist, ohne eine gleichzeitige zwangsweise Öffnung der Steuerventileinheit 8.The free travel a of the control piston 18 is such that a Pressure pulsation compensation is possible without a simultaneous forced opening of the control valve unit 8.
Fig. 2 zeigt eine Pumpencharakteristik einer erfindungsgemä¬ ßen Pumpe. Dabei ist der Volumenstrom Q über den hydrauli¬ schen Druck p aufgetragen. Die obere Linie b zeigt die Cha¬ rakteristik einer herkömmlichen Pumpe, die sowohl einen maxi¬ malen Volumenstrom Qmax als auch einen maximalen Druck pmax erzeugen können soll. Die Linie c zeigt die Chrakteristik der erfindungsgemäßen Pumpe, wenn alle vier Kolben in Betrieb sind. Bei einem Schaltdruck pj wird ein Pumpenkolben 10 (auf2 shows a pump characteristic of a pump according to the invention. The volume flow Q is plotted against the hydraulic pressure p. The upper line b shows the characteristic of a conventional pump, which should be able to generate both a maximum volume flow Q max and a maximum pressure p max . Line c shows the characteristics of the pump according to the invention when all four pistons are in operation. At a switching pressure pj, a pump piston 10 (on
Seite A in Fig. 1) ausgeschaltet, was der Pumpencharakteri¬ stik d in Fig. 2 entspricht. In diesem Fall liegt der maximal mögliche Volumenstrom Qj wesentlich niedriger als Qmax, der maximal mögliche Druck p liegt unterhalb des erforderlichen Maximaldrucks pmaχ. Hier wird bei Erreichen des Schaltdrucks p2 eine weiterer Pumpenkolben 10 auf Leerlauf geschaltet (Sei¬ te C der Fig. 1), wodurch die Pumpencharkteristik e erreicht wird. Übersteigt der Druck p in der Druckleitung 5 den Schaltdruck p3, so wird auch der dritte Pumpenkolben 10 (Sei¬ te B der Fig. 1) auf Leerlauf geschaltet, wodurch die Pumpen¬ charkteristik f in Fig. 2 eingenommen wird. Da hier nur noch ein Pumpenkolben 10 fördert, liegt der theroetische Volumen¬ strom Q3 sehr viel niedriger als Qmax der maximal erreichbare hydraulische Druck pmax entspricht dem Geforderten. Durch die einzelnen Schaltvorgänge ergibt sich für die erfindungsgemäße Pumpe die fett eingezeichnete Pumpencharkteristik g.Side A in FIG. 1) is switched off, which corresponds to the pump characteristic d in FIG. 2. In this case, the maximum possible volume flow Qj is significantly lower than Q ma x, the maximum possible pressure p is below the required maximum pressure p ma χ. Here, when the switching pressure p 2 is reached, a further pump piston 10 is switched to idling (page C of FIG. 1), as a result of which the pump characteristic e is achieved. If the pressure p in the pressure line 5 exceeds the switching pressure p 3 , the third pump piston 10 (page B of FIG. 1) is also switched to idling, as a result of which the pump characteristic f is assumed in FIG. 2. Since only one pump piston 10 is delivering here, the theroetic volume flow Q 3 is much lower than Q max, the maximum achievable hydraulic pressure p max corresponds to the required. The individual switching processes result in the pump characteristic g indicated in bold for the pump according to the invention.
Die erfindungsgemäße Pumpe ist vorzugsweise elektrisch an¬ getrieben und kann ohne einen Druckspeicher beispielsweise für einen Bremskraft- oder einen Lenkkraftverstärker einge¬ setzt werden. Bedingt durch die besondere Ausbildung einer typischen Druck-Volumen-Kennlinie g, insbesondere bei einer Kraftfahrzeug-Bremsanlage, und das Betätigungsvermögen des Fahrers eines Kraftfahrzeugs wird von dem Hilfsdruckerzeuger in einer ersten Phase der Bremsung ein sehr hoher Volumen¬ strom bei geringem Lastdruck (Pumpencharkteristik c) und in einer zweiten Phase ein hoher Pumpendruck bei geringem Volu¬ menstrom (Pumpencharkteristik g) verlangt. Diese extremen Anforderungen führen dazu, daß der die Pumpe antreibende Elektromotor mit hohen Eckleistungen und zugleich hohen Mas¬ senträgheitsmomenten ausgelegt werden muß. Dieses Problem kann dadurch gelöst werden, daß das Fördervolumen Q druck¬ abhängig verändert wird. Im Gegensatz zu üblichen Verstell¬ pumpen, wie sie aus dem Stand der Technik bekannt sind, bie¬ tet die erfindungsgemäße Pumpe eine für die Anwendung im Kraftfahrzeug wesentlich kostengünstiger zu realisierende Lösungsmöglichkeit. In Fig. 1 ist gezeigt, daß die drucksei¬ tige Dämpfungskammer 7 den als Dämpfungskolben ausgebildeten Steuerkolben 18 aufnimmt, welcher seinerseits mit einem Fe¬ derelement 20 zusammenwirkt, welches die Dämpfung von Druck¬ spitzen einerseits und nach Erreichen eines konstruktiv fest¬ gelegten Druckniveaus das Offenhalten der Suagventileinrich- tung 8 andererseits ermöglicht. The pump according to the invention is preferably electrically driven and can be used without a pressure accumulator, for example for a brake booster or a steering booster. Due to the special training of a typical pressure-volume characteristic curve g, in particular in a motor vehicle brake system, and the driver's ability to actuate a motor vehicle is a very high volume flow from the auxiliary pressure generator in a first phase of braking at low load pressure (pump characteristic c) and in a second phase a high pump pressure with a low volume flow (pump characteristic g) is required. These extreme requirements mean that the electric motor driving the pump has to be designed with high corner power and at the same time high mass moments of inertia. This problem can be solved by changing the delivery volume Q depending on the pressure. In contrast to conventional variable displacement pumps, such as are known from the prior art, the pump according to the invention offers a possible solution that is much cheaper to implement for use in a motor vehicle. 1 shows that the pressure-side damping chamber 7 receives the control piston 18 designed as a damping piston, which in turn interacts with a spring element 20 which dampens pressure peaks on the one hand and after reaching a structurally determined pressure level On the other hand, keeping the suction valve device 8 open enables.

Claims

Patentansprüche claims
1. Pumpe, insbesondere Radialkolbenpumpe, mit mindestens zwei Pumpenkolben (10), mit jeweils zugeordneter Ar¬ beitskammer (13), wobei die Arbeitskammern (13) über Saugventileinrichtungen (8) an Saugleitungen (4) und über Druckventileinrichtungen (9) an eine gemeinsame Druckleitung (5) angeschlossen sind, wobei zumindest eine der Saugventileinrichtungen (8) während des Druck¬ hubs in Abhängigkeit vom Druck in einer der zugeordneten Leitungen (4,5) öffnet, dadurch gekennzeichnet, daß zu¬ mindest eine der Saugventileinrichtungen (8) während des Druckhubs in Abhängigkeit vom Druck in der Druck-leitung (5) öffnet.1. Pump, in particular radial piston pump, with at least two pump pistons (10), each with an associated working chamber (13), the working chambers (13) via suction valve devices (8) on suction lines (4) and via pressure valve devices (9) to a common one Pressure line (5) are connected, at least one of the suction valve devices (8) opening during the pressure stroke depending on the pressure in one of the assigned lines (4,5), characterized in that at least one of the suction valve devices (8) during of the pressure stroke depending on the pressure in the pressure line (5) opens.
2. Pumpe nach Anspruch 1, dadurch gekennzeichnet, daß die zumindest eine Saugventileinrichtung (8) zwangsgesteuert öffnet.2. Pump according to claim 1, characterized in that the at least one suction valve device (8) opens under positive control.
3. Pumpe nach Anspruch 2, dadurch gekennzeichnet, daß die Saugventileinrichtung (8) ein Schließglied (15) auf¬ weist, welches gegen einen Ventilsitz (16) vorgespannt ist, und daß dem Schließglied (15) ein Betätigungsglied (22) zugeordnet ist, welches einerseits auf das Schlie߬ glied (15) einwirken kann und andererseits vom Druck in der Druckleitung (5) beaufschlagbar ist.3. Pump according to claim 2, characterized in that the suction valve device (8) has a closing member (15) which is biased against a valve seat (16) and that the closing member (15) is associated with an actuating member (22), which on the one hand can act on the closing member (15) and on the other hand can be acted upon by the pressure in the pressure line (5).
4. Pumpe nach Anspruch 3, dadurch gekennzeichnet, daß das Betätigungsglied (22) mit einem Steuerkolben (18) ver¬ bunden ist, der einerseits vom Druck in der Druckleitung (5) beaufschlagbar ist und andererseits vom Druck in der Saugleitung (4) beaufschlagbar ist sowie mittels eines Federelements (20) vorgespannt ist. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß mehrere Saugventileinrichtungen (8) in Abhängigkeit vom Druck in der Druckleitung (5) öffnen, wobei die den einzelnen Saugventileinrichtungen (8) zu¬ geordneten Schaltdruckwerte unterschiedlich groß sind.4. Pump according to claim 3, characterized in that the actuating member (22) with a control piston (18) is connected, which can be acted upon by the pressure in the pressure line (5) and the pressure in the suction line (4) is biased and by means of a spring element (20). Pump according to one of the preceding claims, characterized in that several suction valve devices (8) open depending on the pressure in the pressure line (5), the switching pressure values assigned to the individual suction valve devices (8) being of different sizes.
Pumpe nach Anspruch 4 und 5, dadurch gekennzeichnet, daß die Federelemente (20) unterschiedliche Federraten auf¬ weisen, bzw. verschieden stark vorgespannt sind.Pump according to Claims 4 and 5, characterized in that the spring elements (20) have different spring rates or are biased to different extents.
Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Pumpe Teil einer Kraftfahrzeug¬ hilfsdruckanlage ist. Pump according to one of the preceding claims, characterized in that the pump is part of a motor vehicle auxiliary pressure system.
EP96925712A 1995-07-27 1996-07-11 Pump Withdrawn EP0840851A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19527402 1995-07-27
DE1995127402 DE19527402A1 (en) 1995-07-27 1995-07-27 pump
PCT/EP1996/003028 WO1997005381A1 (en) 1995-07-27 1996-07-11 Pump

Publications (1)

Publication Number Publication Date
EP0840851A1 true EP0840851A1 (en) 1998-05-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
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EP (1) EP0840851A1 (en)
JP (1) JPH11509905A (en)
DE (1) DE19527402A1 (en)
WO (1) WO1997005381A1 (en)

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WO1997005381A1 (en) 1997-02-13
JPH11509905A (en) 1999-08-31

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