EP1228313B1 - Hydraulic piston pump - Google Patents

Hydraulic piston pump Download PDF

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Publication number
EP1228313B1
EP1228313B1 EP00993113A EP00993113A EP1228313B1 EP 1228313 B1 EP1228313 B1 EP 1228313B1 EP 00993113 A EP00993113 A EP 00993113A EP 00993113 A EP00993113 A EP 00993113A EP 1228313 B1 EP1228313 B1 EP 1228313B1
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EP
European Patent Office
Prior art keywords
pistons
piston pump
piston
hydraulic piston
pump according
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EP00993113A
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German (de)
French (fr)
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EP1228313A1 (en
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Hermann Golle
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    • 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
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate
    • 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
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • 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
    • F04B49/12—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 varying the length of stroke of the working members
    • F04B49/123—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F04B7/06—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports the pistons and cylinders being relatively reciprocated and rotated

Definitions

  • the invention relates to a hydraulic piston pump with a Drive shaft and with this axially arranged or radial cylindrical pistons arranged in a star shape
  • Cylinder spring-loaded axially movable to its longitudinal axis are arranged and between their end face and the cylinder enclose a pump chamber, which with a filling channel, of a control edge of the piston is controlled, connectable, and which is connected to an exhaust valve, with one with the Drive shaft connected and the swash plate driving the piston with axially arranged pistons or eccentric shaft pistons arranged radially in a star shape and with a flow control.
  • a hydraulic piston pump with the features of the preamble of claim 1 e.g. known from US-A-2,775,210.
  • the hydraulic pump mentioned at the outset is for Common rail injection systems are provided.
  • Embodiments of the invention are in subclaims 2 to 9 specified.
  • the pistons 4 have on their, the outlet valve 8 facing Front an oblique control edge 9, which - in the known from in-line injection pumps - with the inlet bore 10 corresponds.
  • Piston 4 is the relevant inlet bore 10 through the oblique control edge 9 is not closed during the piston stroke (the fuel flows back - zero delivery) or it becomes when the control edge 9 of the inlet bore 10th is turned away, already closed from the end face of the piston 4 and all of the fuel through the exhaust valve 8 funded in the hunt group 11 (full funding).
  • Partial delivery rate adjustable The exhaust valves 8 are according to the invention arranged with the smallest distance to the piston 4.
  • To the piston 4 at the high hydraulic pressures from the side Keeping pressure forces free are two sloping control edges 9 arranged opposite to the piston 4.
  • each piston head 6 has external teeth 12, which in the corresponding internal teeth 13 a adjustable ring gear 14 engages.
  • the piston 4 also guide the external toothing 12 Stroke movement in the internal toothing 13. This is because the Adjustment forces are low, with appropriate material selection the gear partner possible.
  • prefabricated tooth segments 15 can be placed on the piston heads 6 .
  • the fuel enters the housing 1 at the inlet opening 16 and flows from here via the cylinder space 17 to the inlet bores 10. Furthermore, fuel flows through the housing channel 18 into the engine case, cools the engine and exits the pump at the outlet opening 19.
  • Fig. 2 shows the adjustment of the ring gear 14, which can be done in a conventional manner via a tangentially arranged adjusting piston 20. Adjustment or restoring forces can be applied by electromagnets or by springs or the fuel pressure in the pump interior.
  • FIG. 4 shows this in a supplementary representation Piston rotation system with the pistons 4, the piston heads 6 and the toothed segments 15, the external teeth 12 in the Engage the internal toothing 13 of the ring gear 14.
  • the twist the ring gear 14 is analogous to FIG. 2 by means of Adjusting piston 20 specified.
  • Fig. 5 shows the principle of a piston rotation system, at which does without a gear-like transmission.
  • collars 23 axially in the housing 1 slidable, but held rotatable.
  • These collars 23 have splines 24 in which the pistons 4 with their external gears 12 (now also splines) can slide.
  • the collars 23 have worked Bolt 25, which is drilled transversely with its outer end Engage pivot 26 in part 14. This now has the corresponding number of instead of an internal toothing Bores for receiving the pivot pins 26.
  • a housing 1 here star-shaped located engine of a radial piston pump, consisting of a drive shaft 3 (here eccentric shaft), intermediate elements like sliding shoes u. a., represented here in simplified form by the race 27 and five pistons 4.
  • a drive shaft 3 here eccentric shaft
  • intermediate elements like sliding shoes u. a., represented here in simplified form by the race 27 and five pistons 4.
  • the bevel edge control works in the manner already described. Is the slant Control edge 9 to the inlet bore 10 so that this up to If the stroke end is not covered, there is no fuel delivery instead of. Is the piston 4 set so that the piston end face closes the inlet bore 10, the full amount of fuel via the outlet valve 8 to the collective outlet 11 funded.
  • the individual exhaust valves 8 are over Intermediate channels not shown here with each other and with connected to the collecting outlet 11.
  • the fuel passes over the Inlet opening 16 into the pump flows on the one hand to the Inlet bores 10, on the other hand, via the housing channel 18 through the engine to the exhaust port 19.
  • the piston rotation system is designed in such a way that everyone Piston 4 two machined, opposite sliding surfaces 28 has, on which the toothed segments 15 engage fork-shaped. These are held axially in the housing slots are with their external teeth 12 with a counter toothing 29 of the ring gear 14 in engagement.
  • the gearing designed as bevel gear teeth. With twisting the In this way, ring gear 14 all pistons 4 in the desired Senses adjusted and the flow rate regulated.
  • the control unit e.g. B. also here as electromagnetic Interlocking 21, is fully integrated into the pump. she is directly connected on the one hand to the ring gear 14 and is based on the other hand in the housing 1.
  • Fig. 7 shows the piston rotation system in a supplementary representation with the radial pump.
  • the pistons 4 with their oblique Control edges 9 are supported on the race 27 on the Eccentric of the drive shaft 3.
  • the tooth segments 15 grip fork-shaped on the sliding surfaces 28 and are on the other hand with their oblique external teeth 12 with the counter teeth 29 of the ring gear 14 in engagement.
  • Adjustment systems for the flow rate are simply designed and suitable for mass production. With appropriate Material selection they will include the gears have it manufactured completely without cutting. According to the The object of the invention can thus be a hydraulic variable displacement pump without additional fine-tuned elements or stroke-adjusting Intermediate links manufactured in a simple manner become.
  • FIG. 1 which characterizes the invention is now another particularly advantageous embodiment described the invention.
  • Each piston 4 moves precisely in a separate cylinder liner.
  • These cylinder liners are used in the housing 1 and are by a closed pressure ring by means of screws the seal pressed and thus sealed on the high pressure side.
  • the housing 1 be kept closed at the end.
  • the big screw fittings, as shown in Fig. 1 on the front side are and each of which is sealed against high pressure can be omitted.

Abstract

All pistons (4) of a hydraulic piston pump having an adjustable delivery rate are provided with beveled control edges (9), which are placed on the faces of the pistons (4) and which interact with the inlet borings (10) according to the principle of beveled edge control. Different means (12; 13; 14; 15; 20; 21; 22; 23; 24; 25; 26; 28; 29) effect a mutual torsion of the pistons (4) thus regulating the delivery rate. The piston pump is especially suited for diesel injection systems but can also be used for many applications in industrial hydraulic engineering.

Description

Die Erfindung betrifft eine hydraulische Kolbenpumpe mit einer Antriebswelle und mit zu dieser axial angeordneten oder radial sternförmig angeordneten zylindrischen Kolben, die in einem Zylinder zu ihrer Längsachse federbelastet axial beweglich angeordnet sind und zwischen ihrer Stirnseite und dem Zylinder einen Pumpraum einschließen, der mit einem Füllkanal, von einer Steuerkante des Kolbens gesteuert, verbindbar ist, und der mit einem Auslassventil verbunden ist, mit einer mit der Antriebswelle verbundenen und die Kolben antreibenden Taumelscheibe bei axial angeordneten Kolben oder Exzenterwelle bei radial sternförmig angeordneten Kolben und mit einer Fördermengenregelung.The invention relates to a hydraulic piston pump with a Drive shaft and with this axially arranged or radial cylindrical pistons arranged in a star shape Cylinder spring-loaded axially movable to its longitudinal axis are arranged and between their end face and the cylinder enclose a pump chamber, which with a filling channel, of a control edge of the piston is controlled, connectable, and which is connected to an exhaust valve, with one with the Drive shaft connected and the swash plate driving the piston with axially arranged pistons or eccentric shaft pistons arranged radially in a star shape and with a flow control.

Eine hydraulische Kolbenpumpe mit den Merkmalen des Oberbegriffs aus Anspruch 1 ist z.B. aus der US-A-2,775,210 bekannt.A hydraulic piston pump with the features of the preamble of claim 1 e.g. known from US-A-2,775,210.

Insbesondere ist die eingangs genannte hydraulische Pumpe für Common-Rail-Einspritzsysteme vorgesehen.In particular, the hydraulic pump mentioned at the outset is for Common rail injection systems are provided.

Für die letztgenannte Anwendung kommen die üblichen Regelsysteme der Ölhydraulik, bei denen die Fördermenge durch Schwenken der Antriebsscheibe oder des Pumpenkörpers regelbar ist, nicht in Frage. Solche Pumpen sind für Common-Rail-Systeme zu groß und zu teuer und außerdem in den Belastungsverhältnissen schwer beherrschbar, da in der Industriehydraulik Drükke über 1000 bar in der Regel nicht angewendet werden. Für Common-Rail-Pumpen mit Drücken von 1500 bar oder höher werden deshalb andere Regelsysteme angewandt. Diese, den Stand der Technik repräsentierenden Systeme sind einschließlich ihrer Nachteile nachfolgend angegeben.

  • 1. Saugseitige Drosselung des einströmenden Kraftstoffes mit dem Nachteil, das Unterdruckbildung und Kavitation entstehen können.
  • 2. Absteuern des Kraftstoffs auf der Hochdruckseite mit dem Nachteil einer bedeutenden Verschlechterung der Energiebilanz und einer hohen Kraftstofferwärmung.
  • 3. Abschalten von Pumpenelementen mit dem Nachteil, dass der Gleichförmigkeitsgrad des Förderstromes verschlechtert wird.
  • 4. Einschalten von Mitteln wie Zwischenhebel u a. zur Hubverstellung der Kolben mit dem Nachteil des höheren Bauaufwandes und des höheren Verschleißes, wie z. B. DE 3803735, DE 4140801.
    • For the latter application, the usual control systems of oil hydraulics, in which the delivery rate can be regulated by swiveling the drive disk or the pump body, are out of the question. Such pumps are too large and too expensive for common rail systems and, moreover, are difficult to control in the load conditions, since Drükke over 1000 bar are generally not used in industrial hydraulics. Other control systems are therefore used for common rail pumps with pressures of 1500 bar or higher. These systems, which represent the prior art, including their disadvantages, are given below.
  • 1. Suction-side throttling of the inflowing fuel with the disadvantage that negative pressure and cavitation can occur.
  • 2. Shutdown of the fuel on the high pressure side with the disadvantage of a significant deterioration in the energy balance and high fuel heating.
  • 3. Switching off pump elements with the disadvantage that the degree of uniformity of the flow rate is deteriorated.
  • 4. Switching on means such as intermediate lever and others. for stroke adjustment of the pistons with the disadvantage of higher construction costs and higher wear, such as. B. DE 3803735, DE 4140801.

    • Es ist Aufgabe der Erfindung, diese genannten Nachteile zu vermeiden. Es soll unter Beibehaltung einer einfachen und raumsparenden Bauweise eine echte Fördermengenregelung erzielt, also nur die jeweils gewünschte Kraftstoffmenge unter Hochdruck gesetzt werden.It is an object of the invention to overcome these disadvantages avoid. It is said to be simple and simple space-saving design achieves a real flow control, So only the desired amount of fuel below High pressure.

    Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass der Kolben an seiner Stirnseite eine zusammen mit der Mantelfläche des Kolbens die Steuerkante bildende Abflachung oder Vertiefung aufweist, derart, dass die Steuerkante eines jeden Kolbens im wesentlichen schräg zur Richtung der Längsachse des Kolbens liegt, und dass alle Kolben zugleich und in gleicher Weise verdrehende Mittel vorgesehen sind.This object is achieved in that the Piston on its face together with the outer surface of the piston the flattening or depression forming the control edge such that the control edge of each piston essentially obliquely to the direction of the longitudinal axis of the Piston lies, and that all pistons at the same time and in the same Means rotating means are provided.

    Ausführungsformen der Erfindung sind in den Unteransprüchen 2 bis 9 angegeben.Embodiments of the invention are in subclaims 2 to 9 specified.

    Die Erfindung wird nachfolgend an zwei Ausführungsbeispielen dargestellt. Die Zeichnungen zeigen:

    Fig. 1
    einen Längsschnitt durch eine 5-zylindrige Pumpe mit axialer Kolbenanordnung (Axialpumpe),
    Fig. 2
    einen Schnitt nach der Linie A-A in Fig. 1,
    Fig. 3
    den gleichen Schnitt wie Fig. 2 mit einem elektromagnetischen Drehstellwerk als Steuereinheit,
    Fig. 4
    eine ergänzende Darstellung des Kolben-Verdrehsystems mit Verzahnungselementen (Axialpumpe),
    Fig. 5
    ein anderes Kolben-Verdrehsystems (Axialpumpe),
    Fig. 6
    einen Längsschnitt durch eine 5-zylindrige Pumpe mit radialer Kolbenanordnung (Radialpumpe),
    Fig. 7
    eine ergänzende Darstellung des Kolben-Verdrehsystems (Radialpumpe) und
    The invention is illustrated below using two exemplary embodiments. The drawings show:
    Fig. 1
    a longitudinal section through a 5-cylinder pump with an axial piston arrangement (axial pump),
    Fig. 2
    2 shows a section along the line AA in FIG. 1,
    Fig. 3
    the same section as Fig. 2 with an electromagnetic rotary interlocking as a control unit,
    Fig. 4
    a supplementary illustration of the piston rotation system with gear elements (axial pump),
    Fig. 5
    another piston rotation system (axial pump),
    Fig. 6
    a longitudinal section through a 5-cylinder pump with a radial piston arrangement (radial pump),
    Fig. 7
    a supplementary representation of the piston rotation system (radial pump) and

    Die Fig. 1 zeigt ein in einem Gehäuse 1 installiertes Taumelscheibentriebwerk 2, welches von einer Antriebswelle 3 in Umdrehung versetzt wird. Dadurch führen die Kolben 4 axiale Hubbewegungen aus, wobei die Druckfedern 5 den ständigen Kontakt zwischen den Kolbenköpfen 6 und der Druckscheibe 7 des Taumelscheibentriebwerks 2 herstellen. Dieser herkömmliche Aufbau einer Axialkolbenpumpe mit nicht verstellbarer Fördermenge wird erfindungsgemäß auf einfache Weise zu einer Verstellpumpe wie folgt gestaltet:1 shows a swash plate engine installed in a housing 1 2, which from a drive shaft 3 in Revolution is offset. As a result, the pistons 4 lead axially Stroke movements, the compression springs 5 the constant Contact between the piston heads 6 and the thrust washer 7 of the swash plate engine 2. This conventional one Construction of an axial piston pump with non-adjustable According to the invention, the delivery rate becomes a in a simple manner Variable pump designed as follows:

    Die Kolben 4 besitzen an ihrer, dem Auslassventil 8 zugewandten Stirnseite eine schräge Steuerkante 9, welche - in der von Reiheneinspritzpumpen her bekannten Weise - mit der Einlassbohrung 10 korrespondiert. Je nach Drehstellung eines Kolbens 4 wird die betreffende Einlassbohrung 10 durch die schräge Steuerkante 9 während des Kolbenhubes nicht verschlossen (der Kraftstoff fließt zurück - Nullförderung) oder sie wird, wenn die Steuerkante 9 von der Einlassbohrung 10 weggedreht ist, schon von der Stirnseite des Kolben 4 verschlossen und der gesamte Kraftstoff durch das Auslassventil 8 in den Sammelanschluss 11 gefördert (Vollförderung). Dazwischen ist entsprechend der Drehstellung des Kolbens 4 jede Teilfördermenge einstellbar. Die Auslassventile 8 sind erfindungsgemäß mit geringstem Abstand zu den Kolben 4 angeordnet. Um die Kolben 4 bei den hohen hydraulischen Drücken von seitlichen Druckkräften frei zu halten, sind zwei schräge Steuerkanten 9 gegenüberliegend an den Kolben 4 angeordnet.The pistons 4 have on their, the outlet valve 8 facing Front an oblique control edge 9, which - in the known from in-line injection pumps - with the inlet bore 10 corresponds. Depending on the rotary position Piston 4 is the relevant inlet bore 10 through the oblique control edge 9 is not closed during the piston stroke (the fuel flows back - zero delivery) or it becomes when the control edge 9 of the inlet bore 10th is turned away, already closed from the end face of the piston 4 and all of the fuel through the exhaust valve 8 funded in the hunt group 11 (full funding). Between is each according to the rotational position of the piston 4 Partial delivery rate adjustable. The exhaust valves 8 are according to the invention arranged with the smallest distance to the piston 4. To the piston 4 at the high hydraulic pressures from the side Keeping pressure forces free are two sloping control edges 9 arranged opposite to the piston 4.

    Die Verdrehung aller Kolben 4 geschieht erfindungsgemäß derart, dass jeder Kolbenkopf 6 eine Aussenverzahnung 12 besitzt, welche in die entsprechende Innenverzahnung 13 eines verstellbaren Zahnkranzes 14 eingreift. Während der Hubbewegung der Kolben 4 führen auch die Aussenverzahnungen 12 diese Hubbewegung in der Innenverzahnung 13 aus. Dies ist, da die Verstellkräfte gering sind, bei entsprechender Werkstoffauswahl der Verzahnungspartner möglich. Es können jedoch auch, wie es in Fig. 2 dargestellt ist, auf den Kolbenköpfen 6 vorgefertigte Zahnsegmente 15 aufgesetzt sein. Der Kraftstoff tritt an der Einlassöffnung 16 in das Gehäuse 1 ein und fließt von hier über den Zylinderraum 17 zu den Einlassbohrungen 10. Ferner strömt Kraftstoff über den Gehäusekanal 18 in das Triebwerksgehäuse, kühlt das Triebwerk und verlässt die Pumpe an der Auslassöffnung 19.According to the invention, all pistons 4 are rotated in such a way that that each piston head 6 has external teeth 12, which in the corresponding internal teeth 13 a adjustable ring gear 14 engages. During the lifting movement the piston 4 also guide the external toothing 12 Stroke movement in the internal toothing 13. This is because the Adjustment forces are low, with appropriate material selection the gear partner possible. However, as shown in FIG. 2, on the piston heads 6 prefabricated tooth segments 15 can be placed. The fuel enters the housing 1 at the inlet opening 16 and flows from here via the cylinder space 17 to the inlet bores 10. Furthermore, fuel flows through the housing channel 18 into the engine case, cools the engine and exits the pump at the outlet opening 19.

    Die Fig. 2 zeigt die Verstellung des Zahnkranzes 14, die in herkömmlicher Weise über einen tangential angeordneten Verstellkolben 20 erfolgen kann.
    Verstell- bzw. Rückstellkräfte können durch Elektromagnete bzw. durch Federn oder den Kraftstoffdruck im Pumpeninnenraum aufgebracht werden.    Fig. 2 shows the adjustment of the ring gear 14, which can be done in a conventional manner via a tangentially arranged adjusting piston 20.
    Adjustment or restoring forces can be applied by electromagnets or by springs or the fuel pressure in the pump interior.

    Für die Verstellung des Zahnkranzes 14 kann jedoch auch, wie es in Fig. 3 dargestellt ist, ein elektromagnetisches Drehstellwerk 21, z. B. ein Schrittmotor, direkt über eine Teilverzahnung 22 in den Zahnkranz 14 eingreifen und diesen verstellen. Damit ergibt sich ein in die Pumpe integriertes Verstellsystem, welches keine Abdichtungen nach außen erfordert.For the adjustment of the ring gear 14 can, however, how it is shown in Fig. 3, an electromagnetic rotary interlocking 21, e.g. B. a stepper motor, directly via a partial toothing 22 engage in the ring gear 14 and adjust it. This results in an integrated in the pump Adjustment system that does not require external seals.

    Die Fig. 4 zeigt in ergänzender Darstellung nochmals das Kolben-Verdrehsystem mit den Kolben 4, den Kolbenköpfen 6 und den Zahnsegmenten 15, deren Aussenverzahnungen 12 in die Innenverzahnung 13 des Zahnkranzes 14 eingreifen. Die Verdrehung des Zahnkranzes 14 ist analog zur Fig. 2 mittels Verstellkolben 20 angegeben.4 shows this in a supplementary representation Piston rotation system with the pistons 4, the piston heads 6 and the toothed segments 15, the external teeth 12 in the Engage the internal toothing 13 of the ring gear 14. The twist the ring gear 14 is analogous to FIG. 2 by means of Adjusting piston 20 specified.

    Die Fig. 5 zeigt das Prinzip eines Kolben-Verdrehsystems, bei welchem auf eine zahnradähnliche Übertragung verzichtet wird. Hierbei sind Stellringe 23 im Gehäuse 1 axial nicht verschiebbar, aber verdrehbar gehalten. Diese Stellringe 23 besitzen Keilverzahnungen 24, in welchen die Kolben 4 mit ihren Aussenverzahnungen 12 (nun ebenfalls Keilverzahnungen) gleiten können. Die Stellringe 23 besitzen angearbeitete Bolzen 25, welche mit ihrem äußeren Ende über quergebohrte Drehzapfen 26 in das Teil 14 eingreifen. Dieses besitzt nun anstelle einer Innenverzahnung die entsprechende Anzahl von Bohrungen zur Aufnahme der Drehzapfen 26.Fig. 5 shows the principle of a piston rotation system, at which does without a gear-like transmission. Here are collars 23 axially in the housing 1 slidable, but held rotatable. These collars 23 have splines 24 in which the pistons 4 with their external gears 12 (now also splines) can slide. The collars 23 have worked Bolt 25, which is drilled transversely with its outer end Engage pivot 26 in part 14. This now has the corresponding number of instead of an internal toothing Bores for receiving the pivot pins 26.

    Die Fig. 6 zeigt das in einem Gehäuse 1 (hier sternförmig) befindliche Triebwerk einer Radialkolbenpumpe, bestehend aus einer Antriebswelle 3 (hier Exzenterwelle), Zwischenelementen wie Gleitschuhen u. a., hier vereinfacht dargestellt durch den Laufring 27 sowie fünf Kolben 4. Diese führen nacheinander Hubbewegungen aus. In der untersten Stellung jedes Kolbens 4 strömt Kraftstoff über die -hier hinter dem Kolben 4 liegende - Einlassbohrung 10 ein. Die Schrägkantensteuerung arbeitet in der schon beschriebenen Weise. Steht die schräge Steuerkante 9 so zur Einlassbohrung 10, dass diese bis zum Hubende nicht verdeckt wird, findet keine Kraftstoffförderung statt. Ist der Kolben 4 so eingestellt, dass schon die Kolbenstirnseite die Einlassbohrung 10 verschließt, wird die volle Kraftstoffmenge über das Auslassventil 8 zum Sammelauslass 11 gefördert. Die einzelnen Auslassventile 8 sind über hier nicht dargestellte Zwischenkanäle untereinander und mit dem Sammelauslass 11 verbunden. Der Kraftstoff tritt über die Einlassöffnung 16 in die Pumpe ein, fließt einerseits zu den Einlassbohrungen 10, andererseits über den Gehäusekanal 18 durch das Triebwerk zur Auslassöffnung 19. Das Kolben-Verdrehsystem ist erfindungsgemäß derart gestaltet, dass jeder Kolben 4 zwei angearbeitete, gegenüberliegende Gleitflächen 28 besitzt, an welchen die Zahnsegmente 15 gabelförmig angreifen. Diese sind in Gehäuseschlitzen axial gehalten und stehen mit ihren Aussenverzahnungen 12 mit einer Gegenverzahnung 29 des Zahnkranzes 14 im Eingriff. Dabei ist die Verzahnung als Kegelradverzahnung ausgeführt. Mit Verdrehung des Zahnkranzes 14 werden auf diese Weise alle Kolben 4 im gewünschten Sinne verstellt und die Fördermenge geregelt.6 shows this in a housing 1 (here star-shaped) located engine of a radial piston pump, consisting of a drive shaft 3 (here eccentric shaft), intermediate elements like sliding shoes u. a., represented here in simplified form by the race 27 and five pistons 4. These guide one after the other Lifting movements. In the lowest position of each Piston 4 flows fuel over the -here behind the piston 4 lying - inlet bore 10. The bevel edge control works in the manner already described. Is the slant Control edge 9 to the inlet bore 10 so that this up to If the stroke end is not covered, there is no fuel delivery instead of. Is the piston 4 set so that the piston end face closes the inlet bore 10, the full amount of fuel via the outlet valve 8 to the collective outlet 11 funded. The individual exhaust valves 8 are over Intermediate channels not shown here with each other and with connected to the collecting outlet 11. The fuel passes over the Inlet opening 16 into the pump flows on the one hand to the Inlet bores 10, on the other hand, via the housing channel 18 through the engine to the exhaust port 19. The piston rotation system is designed in such a way that everyone Piston 4 two machined, opposite sliding surfaces 28 has, on which the toothed segments 15 engage fork-shaped. These are held axially in the housing slots are with their external teeth 12 with a counter toothing 29 of the ring gear 14 in engagement. Here is the gearing designed as bevel gear teeth. With twisting the In this way, ring gear 14 all pistons 4 in the desired Senses adjusted and the flow rate regulated.

    Die Steuereinheit, z. B. auch hier als elektromagnetisches Drehstellwerk 21, ist in die Pumpe vollkommen integriert. Sie ist direkt einerseits mit dem Zahnkranz 14 verbunden und stützt sich andererseits im Gehäuse 1 ab.The control unit, e.g. B. also here as electromagnetic Interlocking 21, is fully integrated into the pump. she is directly connected on the one hand to the ring gear 14 and is based on the other hand in the housing 1.

    Die Fig. 7 zeigt in ergänzender Darstellung das Kolben-Verdrehsystem bei der Radialpumpe. Die Kolben 4 mit ihren schrägen Steuerkanten 9 stützen sich über den Laufring 27 auf dem Exzenter der Antriebswelle 3 ab. Die Zahnsegmente 15 greifen gabelförmig an den Gleitflächen 28 an und stehen andererseits mit ihren schrägen Aussenverzahnungen 12 mit der Gegenverzahnung 29 des Zahnkranzes 14 im Eingriff.Fig. 7 shows the piston rotation system in a supplementary representation with the radial pump. The pistons 4 with their oblique Control edges 9 are supported on the race 27 on the Eccentric of the drive shaft 3. The tooth segments 15 grip fork-shaped on the sliding surfaces 28 and are on the other hand with their oblique external teeth 12 with the counter teeth 29 of the ring gear 14 in engagement.

    Die Elemente für die beschriebenen Ausführungen, insbes. die Verstellsysteme für die Fördermenge, sind einfach gestaltet und für eine Massenfertigung geeignet. Bei entsprechender Werkstoffauswahl werden sie sich einschließlich der Verzahnungen komplett spanlos fertigen lassen. Entsprechend der Aufgabe der Erfindung kann somit eine hydraulische Verstellpumpe ohne zusätzliche feingepasste Elemente oder hubverstellende Zwischenglieder auf einfache Weise hergestellt werden.The elements for the described versions, in particular the Adjustment systems for the flow rate are simply designed and suitable for mass production. With appropriate Material selection they will include the gears have it manufactured completely without cutting. According to the The object of the invention can thus be a hydraulic variable displacement pump without additional fine-tuned elements or stroke-adjusting Intermediate links manufactured in a simple manner become.

    Ergänzend zu der die Erfindung charakterisierenden Fig. 1 wird nun eine weitere besonders vorteilhafte Ausgestaltung der Erfindung beschrieben. Jeder Kolben 4 bewegt sich feingepasst in einer gesonderten Zylinderbüchse. Diese Zylinderbüchsen sind im Gehäuse 1 eingesetzt und werden durch einen geschlossenen Druckring mittels Schrauben gegen die Dichtung gepresst und damit hochdruckseitig abgedichtet. Durch diese erfindungsgemäßen Mittel kann das Gehäuse 1 stirnseitig geschlossen gehalten werden. Die großen Einschraubungen, wie sie in Fig. 1 auf der Stirnseite dargestellt sind und von denen jede für sich gegen Hochdruck abgedichtet sein muss, können entfallen. In addition to FIG. 1, which characterizes the invention is now another particularly advantageous embodiment described the invention. Each piston 4 moves precisely in a separate cylinder liner. These cylinder liners are used in the housing 1 and are by a closed pressure ring by means of screws the seal pressed and thus sealed on the high pressure side. The housing 1 be kept closed at the end. The big screw fittings, as shown in Fig. 1 on the front side are and each of which is sealed against high pressure can be omitted.

    BezugszeichenlisteLIST OF REFERENCE NUMBERS

    11
    Gehäusecasing
    22
    TaumelscheibentriebwerkSwash plate engine
    33
    Antriebswelledrive shaft
    44
    Kolbenpiston
    55
    Druckfedercompression spring
    66
    Kolbenkopfpiston head
    77
    Druckscheibethrust washer
    88th
    Auslassventiloutlet valve
    99
    Steuerkantecontrol edge
    1010
    Einlassbohrunginlet bore
    1111
    Sammelauslasscollection outlet
    1212
    Aussenverzahnungexternal teeth
    1313
    Innenverzahnunginternal gearing
    1414
    Zahnkranzsprocket
    1515
    Zahnsegmenttoothed segment
    1616
    Einlassöffnunginlet port
    1717
    Zylinderraumcylinder space
    1818
    Gehäusekanalhousing channel
    1919
    Auslassöffnungoutlet
    2020
    Verstellkolbenadjusting piston
    2121
    Drehstellwerkrotary positioner
    2222
    Teilverzahnungpart teeth
    2323
    Stellringcollar
    2424
    Keilverzahnungspline
    2525
    Bolzenbolt
    2626
    Drehzapfenpivot
    2727
    Laufringrace
    2828
    Gleitflächensliding surfaces
    2929
    Gegenverzahnungcounter teeth

    Claims (9)

    1. Hydraulic piston pump, with a drive shaft (3) and with cylindrical pistons (4) which are axially arranged or arranged radially in a star-shaped manner in relation to the latter and which, spring-loaded in relation to their longitudinal axis, are arranged axially movably in a cylinder and between their end face and the cylinder enclose a pumping space which, under the control of a control edge (9) of the piston, is connectable to a filling duct (10) and which is connected to an outlet valve (8), with a swashplate (2) connected to the drive shaft (3) and driving the pistons (4), in the case of axially arranged pistons (4), or an eccentric shaft, in the case of pistons (4) arranged radially in a star-shaped manner, and with delivery-quantity regulation, characterized in that each piston (4) has, on its end face, a flattening or depression which, together with the outer surface of the piston, forms the control edge (9), in such a way that the control edge (9) of each piston (4) lies essentially obliquely to the direction of the longitudinal axis of the piston (4), and in that means (12; 13; 14, 15; 20; 21; 22; 23; 24; 25; 26; 28; 29) rotating all the pistons (4) simultaneously and identically are provided.
    2. Hydraulic piston pump according to Claim 1, characterized in that the outlet valves (8) are installed, with the smallest possible distance between them, so as to lie directly opposite the pistons (4) or perpendicularly thereto.
    3. Hydraulic piston pump according to Claim 1 or 2, characterized in that, in the case of pistons (4) arranged axially, external toothings (12) located on the piston heads (6) engage into the internal toothing (13) of an adjustable toothed ring (14).
    4. Hydraulic piston pump according to one of Claims 1 to 3, characterized in that separate toothed quadrants (15), which carry the external toothings (12), are placed on the piston heads (6).
    5. Hydraulic piston pump according to one of Claims 1 to 4, characterized in that, for the adjustment of the toothed ring (14), an electromagnetic rotary actuator (21) with direct engagement into an external part-toothing (22) of the toothed ring (14) is arranged.
    6. Hydraulic piston pump according to one of Claims 1 to 5, characterized in that the piston heads (6) are connected fixedly in terms of rotation, but axially displaceably, to actuating rings (23) via spline toothings (12; 13), and bolts (25) located on the actuating rings (23) engage into pivot pins (26), the pivot pins (26) being mounted in bores of the toothed ring (14).
    7. Hydraulic piston pump according to Claim 1 or 2, characterized in that, in the case of pistons (4) arranged radially in a star-shaped manner, fork-shaped toothed quadrants (15), on the one hand, engage on sliding surfaces (28) of the pistons (4) and, on the other hand, are connected via external toothings (12) to a countertoothing (29) of the toothed ring (14).
    8. Hydraulic piston pump according to Claim 1 or 2 and 7, characterized in that the electromagnetic rotary actuator (21) is arranged inside the casing (1) and is connected, on the one hand, directly to the toothed ring (14) and, on the other hand, to the casing (1).
    9. Hydraulic piston pump according to one of Claims 1 to 8, characterized in that cylinder liners are pressed by means of a thrust ring and screws against seals inserted in the casing (1) and are sealed off on the high-pressure side.
    EP00993113A 1999-11-13 2000-11-13 Hydraulic piston pump Expired - Lifetime EP1228313B1 (en)

    Applications Claiming Priority (3)

    Application Number Priority Date Filing Date Title
    DE19954639A DE19954639C2 (en) 1999-11-13 1999-11-13 Hydraulic piston pump, especially for common rail injection systems
    DE19954639 1999-11-13
    PCT/DE2000/003952 WO2001036820A1 (en) 1999-11-13 2000-11-13 Hydraulic piston pump

    Publications (2)

    Publication Number Publication Date
    EP1228313A1 EP1228313A1 (en) 2002-08-07
    EP1228313B1 true EP1228313B1 (en) 2003-09-03

    Family

    ID=7928918

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP00993113A Expired - Lifetime EP1228313B1 (en) 1999-11-13 2000-11-13 Hydraulic piston pump

    Country Status (7)

    Country Link
    EP (1) EP1228313B1 (en)
    CN (1) CN1390281A (en)
    AT (1) ATE248991T1 (en)
    AU (1) AU2826001A (en)
    CZ (1) CZ20022062A3 (en)
    DE (2) DE19954639C2 (en)
    WO (1) WO2001036820A1 (en)

    Families Citing this family (5)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE10247982A1 (en) * 2002-10-15 2004-04-29 Robert Bosch Gmbh Hydraulic piston machine
    DE102008028547B4 (en) * 2008-06-16 2022-07-07 Danfoss Power Solutions Gmbh & Co. Ohg Mobile working machine
    DE102009038462A1 (en) * 2009-08-21 2011-03-03 Dürr Systems GmbH Tumbling piston pump for metering a coating agent
    JP6905442B2 (en) * 2017-09-29 2021-07-21 株式会社イワキ Plunger pump
    CN110206702B (en) * 2019-06-18 2021-03-30 杭州绿聚科技有限公司 Axial plunger assembly pump

    Family Cites Families (8)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    FR54949E (en) * 1946-10-05 1951-04-30 Nathan Mfg Co Pump
    US2775210A (en) * 1951-04-10 1956-12-25 Scintilla Ltd Piston pump
    DE1222373B (en) * 1963-11-14 1966-08-04 Boelkow Ludwig Piston pump with a small stroke of the working piston
    US3492948A (en) * 1968-04-08 1970-02-03 Haviland H Platt Hydraulic pump/motor
    DE3601462A1 (en) * 1986-01-20 1987-07-23 Mak Maschinenbau Krupp Fuel injection device
    DE3803735A1 (en) * 1988-02-08 1989-08-17 Rexroth Mannesmann Gmbh Eccentric pump, especially a fuel injection pump
    IT1244233B (en) * 1990-05-16 1994-07-08 O M A P Officine Meccaniche Al High pressure pump with an adjustable lead for injectors in endothermic motors
    DE4140801A1 (en) * 1991-12-11 1993-06-17 Bosch Gmbh Robert Externally activated radial piston pump - has several hollow pistons in bores of pump ring body which are in effective connection with eccentric of drive shaft.

    Also Published As

    Publication number Publication date
    WO2001036820A9 (en) 2001-06-21
    EP1228313A1 (en) 2002-08-07
    CZ20022062A3 (en) 2002-10-16
    DE19954639C2 (en) 2002-05-29
    ATE248991T1 (en) 2003-09-15
    DE50003582D1 (en) 2003-10-09
    DE19954639A1 (en) 2001-06-07
    CN1390281A (en) 2003-01-08
    AU2826001A (en) 2001-05-30
    WO2001036820A1 (en) 2001-05-25

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