WO1999039100A1 - Axial piston pump - Google Patents

Axial piston pump Download PDF

Info

Publication number
WO1999039100A1
WO1999039100A1 PCT/EP1999/000448 EP9900448W WO9939100A1 WO 1999039100 A1 WO1999039100 A1 WO 1999039100A1 EP 9900448 W EP9900448 W EP 9900448W WO 9939100 A1 WO9939100 A1 WO 9939100A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial piston
swash plate
shaft
pump housing
piston pump
Prior art date
Application number
PCT/EP1999/000448
Other languages
German (de)
French (fr)
Inventor
Peter Hoffmann
Original Assignee
Continental Teves Ag & Co. Ohg
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 Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Priority to EP99903678A priority Critical patent/EP1049874B1/en
Priority to DE59905314T priority patent/DE59905314D1/en
Priority to JP2000529539A priority patent/JP2002502007A/en
Publication of WO1999039100A1 publication Critical patent/WO1999039100A1/en

Links

Classifications

    • 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
    • F04B1/14—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 having stationary cylinders

Definitions

  • the invention relates to an axial piston pump with a pump housing, a motor-driven shaft, a swash plate rotatably connected to the shaft and a number of pistons which can be moved back and forth by means of the swash plate, as described for example in DE 44 45 522 AI.
  • Such axial piston pumps are used, among other things. used in electronic braking systems for motor vehicles, which can be equipped with controlled devices for preventing the locking of individual wheels when braking, for preventing the driven wheels from spinning and other devices for active vehicle stabilization.
  • electronic braking systems for motor vehicles which can be equipped with controlled devices for preventing the locking of individual wheels when braking, for preventing the driven wheels from spinning and other devices for active vehicle stabilization.
  • the object is therefore to develop an axial piston pump of the type mentioned at the outset in such a way that the disadvantages mentioned can be overcome.
  • the flow of power should be better manageable and, on the other hand, the edge position of the channels in the housing should be avoided as far as possible, so that more favorable design options can be created for the external connections.
  • the available space for example an electronic braking system, should be used optimally.
  • a central bore is provided in the pump housing, through which an extension of the shaft extends, at the end of which the swash plate is arranged outside the pump housing.
  • the swash plate is advantageously arranged in a cover, which can be designed as a valve block or electronics box of an electronic braking system.
  • the pump pistons are advantageously arranged between the swash plate and the pump drive motor. It is also proposed that the piston by means of Return springs are clamped between the swash plate and the inner end of the holes.
  • a shaft bearing is expediently axially supported on the surface of a stepped bore of the pump housing, which is opposite the inner end of the bores.
  • the proposal according to the invention has the great advantage that the frictional connection takes place via the extension of the shaft which is subjected to tension and that only the part between the bearing and the inner end of the bores is subjected to pressure in the main direction of force from the housing.
  • the frictional connection is closed via the bearing which is subjected to pressure and the pistons and return springs which are also subject to pressure and via the swashplate which is subjected to bending.
  • the housing essentially only has to absorb lateral forces, i.e. the components that are not parallel to the axis of the shaft or the bores.
  • the required larger space requirement for the bores in the radial direction does not play a major role, because the pump housing for the attachment of the drive motor usually has to be made larger transversely to the shaft axis than is required for accommodating the bores for the pistons.
  • the larger space requirement in the radial direction is compensated for by a smaller space requirement of the pump housing in the axial direction, because the channels for the supply and discharge of the fluid are no longer arranged on the edge, but at a medium height of the housing and because only in the central part the bearing height, the piston length and the thickness of the swash plate including the bearing-dependent full height of the pump housing must be realized.
  • Figure 1 shows a longitudinal section through the central part of a pump housing (1) for an axial piston pump according to the invention.
  • the motor-driven shaft 2 has an extension 9, on the end of which a swash plate 3 with an axial bearing 13 is rotatably attached.
  • a bearing 6 is arranged between the shaft 2 and the pump housing 1, via which radial and axial forces can be transmitted from the shaft 2 to the pump housing 1.
  • holes 7 for pistons 4 and return springs 5, preferably rounded on the end face, are arranged parallel to the shaft axis, the inner ends 10 of which lie opposite a surface 11 of the stepped bore 12 formed in the housing 1 for the bearing 6.
  • the material region of the pump housing 1 lying between the inner ends 10 of the bores 7 and the surface 11 is the only part of the pump housing that has to absorb forces in the main direction of attack parallel to the shaft axis. Adjacent to the inner ends 10 are the bores 7 with channels 14 and 15 formed in the pump housing 1 for the supply and discharge of the Media connected.
  • the extension 9 of the shaft 2 is carried out according to the invention through a central bore 8 in the pump housing 1, which is closed by a cover 16 which overlaps the swash plate 3 and which does not have to be part of the pump housing.
  • the cover is designed as a valve block and / or electronics box of an electronically controlled braking system.
  • the pistons are therefore preferably arranged between the swash plate 3 and the motor (not shown) driving the pump 1.
  • a receiving area 17 for the arrangement of the drive motor for the shaft 2 is provided in the pump housing 1.
  • the delivery chambers formed between the end face of the pistons 4 and the inner end of the bores 7 are no longer on the edge side in the housing 1, so that for the arrangement of the channels 14, 15 for supplying and removing the delivery medium and their external Connections there are better design options.
  • the pump housing 1 can be kept flatter overall, because only the central area must have the full height due to the dimensions of the bearing 6, the return springs 5, the piston 4 and the swash plate 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

The invention relates to an axial piston pump comprising a pump housing (1), a motor-driven shaft (2), a swash plate (3) connected to the shaft (2) in a rotationally fixed manner, and a number of pistons (4). The swash plate (3) permits the pistons to move in a back and forward manner. According to the invention, the axial piston pump is configured in such a way that the shaft (2) extends through the pump housing (1), and the swash plate (3) is arranged outside said pump housing (1).

Description

AxialkolbenpumpeAxial piston pump
Die Erfindung betrifft eine Axialkolbenpumpe mit einem Pumpengehause, einer motorisch antreibbaren Welle, einer mit der Welle drehfest verbundenen Taumelscheibe und einer Anzahl von Kolben, die mittels der Taumelscheibe hin- und herbewegbar sind, wie sie beispielsweise in der DE 44 45 522 AI beschrieben ist.The invention relates to an axial piston pump with a pump housing, a motor-driven shaft, a swash plate rotatably connected to the shaft and a number of pistons which can be moved back and forth by means of the swash plate, as described for example in DE 44 45 522 AI.
Derartige Axialkolbenpumpen werden u.a. in elektronischen Bremssystemen für Kraftfahrzeuge verwendet, die mit geregelten Einrichtungen zur Verhinderung des Blockierens einzelner Rader beim Bremsen, zur Verhinderung des Durchdrehens der angetriebenen Rader sowie weiteren Einrichtungen zur aktiven Fahrzeugstabilisierung ausgestattet sein können. Für das dauerhaft zuverlässige Funktionieren solcher Bremssysteme kommt es darauf an, daß sämtliche Komponenten des Systems im Hinblick auf die zu erwartenden statischen und dynamischen Beanspruchungen einerseits robust und möglichst verschleißarm ausgelegt werden, andererseits aber auch den Forderungen nach Platz- und Gewichtsersparnis sowie nach wirtschaftlicher Herstellung gerecht werden.Such axial piston pumps are used, among other things. used in electronic braking systems for motor vehicles, which can be equipped with controlled devices for preventing the locking of individual wheels when braking, for preventing the driven wheels from spinning and other devices for active vehicle stabilization. For the long-term reliable functioning of such brake systems, it is important that all components of the system are designed robustly and with as little wear as possible with regard to the static and dynamic loads to be expected, but also meet the demands for space and weight savings as well as economical production become.
Bei Axialkolbenpumpen kann man eine kompakte Bauweise erreichen, indem die Bohrungen für die Kolben im Pumpengehause auf einem Kreis mit möglichst kleinem Durchmesser angeordnet werden, wobei dann auch der Durchmesser der Taumelscheibe klein gehalten werden kann. Diese Anordnung hat jedoch den Nachteil, daß die Kanäle für die Zu- und Abfuhr des Fordermediums am äußeren Rand desIn the case of axial piston pumps, a compact design can be achieved by arranging the bores for the pistons in the pump housing on a circle with the smallest possible diameter, in which case the diameter of the swash plate can also be kept small. However, this arrangement has the disadvantage that the channels for the supply and discharge of the medium on the outer edge of the
ee teuNGSKDPff Pumpengehauses angeordnet werden müssen, und daß sich die statischen und dynamischen Reaktionskrafte im wesentlichen als Zugkräfte im Gehäuse auswirken, das aufgrund der Vielzahl von Bohrungen kein homogener Baukorper mehr ist, in dem die Kraftlinien sehr unübersichtlich verlaufen und in dem Spannungsspitzen auftreten können, was in Verbindung mit kleinsten Material- oder Fertigungsfehlern eine Versagensgefahr bedeuten konnte.ee teuNGSKDPff Pump housing must be arranged, and that the static and dynamic reaction forces essentially act as tensile forces in the housing, which due to the large number of holes is no longer a homogeneous structure, in which the lines of force run very confusing and in which voltage peaks can occur, which in connection with the smallest material or manufacturing defects could mean a risk of failure.
Es besteht somit die Aufgabe, eine Axialkolbenpumpe der eingangs genannten Art so weiterzubilden, daß die genannten Nachteile überwunden werden können. Dabei soll einerseits der Kraftfluß besser überschaubar und andererseits die Randlage der Kanäle im Gehäuse möglichst vermieden werden, damit gunstigere Gestaltungsmoglichkeiten für die äußeren Anschlüsse geschaffen werden können. Außerdem soll der zur Verfugung stehende Bauraum, beispielsweise eines elektronischen Bremssystems, optimal genutzt werden.The object is therefore to develop an axial piston pump of the type mentioned at the outset in such a way that the disadvantages mentioned can be overcome. On the one hand, the flow of power should be better manageable and, on the other hand, the edge position of the channels in the housing should be avoided as far as possible, so that more favorable design options can be created for the external connections. In addition, the available space, for example an electronic braking system, should be used optimally.
Zur Losung dieser Aufgabe wird erfmdungsgemaß vorgeschlagen, daß bei einer gattungsgemaßen Axialkolbenpumpe im Pumpengehause eine zentrale Bohrung vorgesehen ist, durch die sich eine Verlängerung der Welle hindurch erstreckt, an deren Ende die Taumelscheibe außerhalb des Pumpengehauses angeordnet ist. Mit Vorteil ist dabei die Taumelscheibe in einer Abdeckung angeordnet, die als Ventilblock bzw. Elektronikbox eines elektronischen Bremssystems ausgebildet sein kann.To solve this problem, it is proposed according to the invention that, in the case of a generic axial piston pump, a central bore is provided in the pump housing, through which an extension of the shaft extends, at the end of which the swash plate is arranged outside the pump housing. The swash plate is advantageously arranged in a cover, which can be designed as a valve block or electronics box of an electronic braking system.
In vorteilhafter Weise sind die Pumpenkolben zwischen Taumelscheibe und dem Pumpenantriebsmotor angeordnet. Ferner wird vorgeschlagen, daß die Kolben mittels der Ruckstellfedern zwischen der Taumelscheibe und dem inneren Ende der Bohrungen eingespannt sind. Ein Wellenlager ist zweckmaßigerweise axial auf derjenigen Flache einer Stufenbohrung des Pumpengehauses abgestutzt, die dem inneren Ende der Bohrungen gegenüberliegt.The pump pistons are advantageously arranged between the swash plate and the pump drive motor. It is also proposed that the piston by means of Return springs are clamped between the swash plate and the inner end of the holes. A shaft bearing is expediently axially supported on the surface of a stepped bore of the pump housing, which is opposite the inner end of the bores.
Der erfmdungsgemaße Vorschlag hat den großen Vorteil, daß der Kraftschluß über die auf Zug beanspruchte Verlängerung der Welle erfolgt und vom Gehäuse nur der Teil zwischen Lager und innerem Ende der Bohrungen in der Hauptkraftrichtung auf Druck beansprucht wird. Im übrigen wird der Kraftschluß über das auf Druck beanspruchte Lager und die ebenfalls auf Druck beanspruchten Kolben und Ruckstellfedern sowie über die auf Biegung beanspruchte Taumelscheibe geschlossen. Das Gehäuse hat im wesentlichen nur noch Querkrafte aufzunehmen, d.h. die Komponenten, die nicht parallel zur Achse der Welle bzw. der Bohrungen gerichtet sind.The proposal according to the invention has the great advantage that the frictional connection takes place via the extension of the shaft which is subjected to tension and that only the part between the bearing and the inner end of the bores is subjected to pressure in the main direction of force from the housing. For the rest, the frictional connection is closed via the bearing which is subjected to pressure and the pistons and return springs which are also subject to pressure and via the swashplate which is subjected to bending. The housing essentially only has to absorb lateral forces, i.e. the components that are not parallel to the axis of the shaft or the bores.
Der erforderliche größere Platzbedarf für die Bohrungen m radialer Richtung spielt keine große Rolle, weil das Pumpengehause für die Anbringung des Antriebsmotors üblicherweise quer zur Wellenachse ohnehin großer ausgeführt werden muß, als es für die Unterbringung der Bohrungen für die Kolben erforderlich ist. Außerdem wird der größere Platzbedarf in radialer Richtung durch einen geringeren Platzbedarf des Pumpengehauses m axialer Richtung kompensiert, weil die Kanäle für die Zu- und Abfuhr des Fordermediums nicht mehr randseitig angeordnet sind, sondern in mittlerer Hohe des Gehäuses und weil nur im zentralen Teil die von der Lagerhohe, der Kolbenlange und der Dicke der Taumelscheibe einschließlich Lager abhangige volle Hohe des Pumpengehauses realisiert werden muß .The required larger space requirement for the bores in the radial direction does not play a major role, because the pump housing for the attachment of the drive motor usually has to be made larger transversely to the shaft axis than is required for accommodating the bores for the pistons. In addition, the larger space requirement in the radial direction is compensated for by a smaller space requirement of the pump housing in the axial direction, because the channels for the supply and discharge of the fluid are no longer arranged on the edge, but at a medium height of the housing and because only in the central part the bearing height, the piston length and the thickness of the swash plate including the bearing-dependent full height of the pump housing must be realized.
Vorteilhafte Weiterbildungen des Erfindungsgedankens sind in den Unteranspruchen beschrieben. Weitere Einzelheiten werden anhand des in Figur 1 dargestellten Ausfuhrungsbeispiels naher erläutert.Advantageous further developments of the inventive concept are described in the subclaims. Further details are explained in more detail with reference to the exemplary embodiment shown in FIG. 1.
Figur 1 zeigt einen Längsschnitt durch den zentralen Teil eines Pumpengehauses (1) für eine Axialkolbenpumpe gemäß der Erfindung.Figure 1 shows a longitudinal section through the central part of a pump housing (1) for an axial piston pump according to the invention.
Die motorisch antreibbare Welle 2 besitzt eine Verlängerung 9, an der endseitig eine Taumelscheibe 3 mit einem Axiallager 13 drehfest angebracht ist. Zwischen der Welle 2 und dem Pumpengehause 1 ist ein Lager 6 angeordnet, über das radiale und axiale Kräfte von der Welle 2 auf das Pumpengehause 1 übertragen werden können. Auf einem zur Verlängerung 9 der Welle 2 konzentrisch angeordnetem Kreis sind parallel zur Wellenachse Bohrungen 7 für vorzugsweise stirnseitig abgerundete Kolben 4 und Ruckstellfedern 5 angeordnet, deren innere Enden 10 einer Flache 11 der im Gehäuse 1 ausgebildeten Stufenbohrung 12 für das Lager 6 gegenüberliegen. Der zwischen den inneren Enden 10 der Bohrungen 7 und der Flache 11 liegende Materialbereich des Pumpengehauses 1, ist der einzige Teil des Pumpengehauses, der Kräfte in der Hauptangriffsrichtung parallel zur Wellenachse aufnehmen muß. Benachbart zu den inneren Enden 10 sind die Bohrungen 7 mit im Pumpengehause 1 ausgebildeten Kanälen 14 und 15 für die Zu- bzw. Abfuhr des Fordermediums verbunden.The motor-driven shaft 2 has an extension 9, on the end of which a swash plate 3 with an axial bearing 13 is rotatably attached. A bearing 6 is arranged between the shaft 2 and the pump housing 1, via which radial and axial forces can be transmitted from the shaft 2 to the pump housing 1. On a circle concentrically arranged for the extension 9 of the shaft 2, holes 7 for pistons 4 and return springs 5, preferably rounded on the end face, are arranged parallel to the shaft axis, the inner ends 10 of which lie opposite a surface 11 of the stepped bore 12 formed in the housing 1 for the bearing 6. The material region of the pump housing 1 lying between the inner ends 10 of the bores 7 and the surface 11 is the only part of the pump housing that has to absorb forces in the main direction of attack parallel to the shaft axis. Adjacent to the inner ends 10 are the bores 7 with channels 14 and 15 formed in the pump housing 1 for the supply and discharge of the Media connected.
Die Verlängerung 9 der Welle 2 ist erfmdungsgemaß durch eine zentrale Bohrung 8 im Pumpengehause 1 hmdurchgefuhrt , die von einer die Taumelscheibe 3 übergreifenden Abdeckung 16, die nicht Teil des Pumpengehauses sein muß, abgeschlossen ist. In besonders vorteilha ter Weise ist die Abdeckung als Ventilblock und/oder Elektronikbox eines elektronisch geregelten Bremssystems ausgebildet. Erfmdungsgemaß sind die Kolben also bevorzugt zwischen der Taumelscheibe 3 und dem die Pumpe 1 antreibenden Motor (nicht dargestellt) angeordnet. Der Abdeckung 16 gegenüberliegend ist im Pumpengehause 1 ein Aufnahmebereich 17 für die Anordnung des Antriebsmotors für die Welle 2 vorgesehen .The extension 9 of the shaft 2 is carried out according to the invention through a central bore 8 in the pump housing 1, which is closed by a cover 16 which overlaps the swash plate 3 and which does not have to be part of the pump housing. In a particularly advantageous manner, the cover is designed as a valve block and / or electronics box of an electronically controlled braking system. According to the invention, the pistons are therefore preferably arranged between the swash plate 3 and the motor (not shown) driving the pump 1. Opposite the cover 16, a receiving area 17 for the arrangement of the drive motor for the shaft 2 is provided in the pump housing 1.
Aus Figur 1 ist ohne weiteres ersichtlich, daß die statischen und dynamischen Kräfte beim Betrieb der Axialkolbenpumpe in einem kurzen und übersichtlichen Kraftschluß verlaufen. Die parallel zur Wellenachse wirkenden statischen Kräfte der Federn 5 und die in gleicher Richtung verlaufenden Hauptkomponenten der durch die Bewegung der Taumelscheibe 3 erzeugten dynamischen Kräfte, wirken sich in der Verlängerung der Welle 2 als Zugkräfte aus, die über Biegekrafte in der Taumelscheibe 3 sowie Druckkräfte in den Kolben 4, den Federn 5, einem kurzen Wandteil des Pumpengehauses 1 sowie im Wellenlager 6 aufgenommen werden. Damit ist das Pumpengehause 1 praktisch frei von Beanspruchungen der Hauptkraftrichtung und muß nur noch im Hinblick auf die unvermeidbaren Querkrafte ausgelegt werden. Dies ermöglicht eine platz- und gewichtssparende Ausfuhrung des Pumpengehauses 1, das festigkeitsmaßig weniger beansprucht ist und für das aus diesem Grunde auch weniger hochfeste Werkstoffe verwendet werden können.From Figure 1 it is readily apparent that the static and dynamic forces during operation of the axial piston pump run in a short and clear force fit. The static forces of the springs 5 acting parallel to the shaft axis and the main components of the dynamic forces generated by the movement of the swash plate 3, which act in the same direction, have an effect in the extension of the shaft 2 as tensile forces, which are caused by bending forces in the swash plate 3 and compressive forces in the piston 4, the springs 5, a short wall part of the pump housing 1 and in the shaft bearing 6 are accommodated. The pump housing 1 is thus practically free from stresses in the main direction of force and only has to be designed with regard to the unavoidable transverse forces. This enables space and weight-saving execution of the pump housing 1, the strength is less stressed and for this reason less high-strength materials can be used.
Als besonders vorteilhaft wird angesehen, daß die zwischen Stirnflache der Kolben 4 und innerem Ende der Bohrungen 7 ausgebildeten Forderkammern nicht mehr randseitig im Gehäuse 1 liegen, so daß für die Anordnung der Kanäle 14, 15 zur Zu- bzw. Abfuhr des Fordermediums sowie deren äußere Anschlüsse bessere Gestaltungsmoglichkeiten bestehen. Außerdem kann das Pumpengehause 1 insgesamt flacher gehalten werden, weil nur der zentrale Bereich die volle, durch die Abmessungen des Lagers 6, der Ruckstellfedern 5, der Kolben 4 und der Taumelscheibe 3 konstruktiv bedingte volle Hohe aufweisen muß. It is considered to be particularly advantageous that the delivery chambers formed between the end face of the pistons 4 and the inner end of the bores 7 are no longer on the edge side in the housing 1, so that for the arrangement of the channels 14, 15 for supplying and removing the delivery medium and their external Connections there are better design options. In addition, the pump housing 1 can be kept flatter overall, because only the central area must have the full height due to the dimensions of the bearing 6, the return springs 5, the piston 4 and the swash plate 3.

Claims

Patentansprüche claims
1. Axialkolbenpumpe mit einem Pumpengehause (1), einer motorisch antreibbaren Welle (2), einer mit der Welle1. Axial piston pump with a pump housing (1), a motor-driven shaft (2), one with the shaft
(2) drehfest verbundenen Taumelscheibe (3) und einer Anzahl von Kolben (4), die mittels der Taumelscheibe(2) non-rotatably connected swash plate (3) and a number of pistons (4) by means of the swash plate
(3) hm- und herbewegbar sind, dadurch gekennzeichnet, daß sich die Welle (2) durch das Pumpengehause (1) hindurch erstreckt und die Taumelscheibe (3) außerhalb des Pumpengehauses (1) angeordnet ist.(3) can be moved and moved, characterized in that the shaft (2) extends through the pump housing (1) and the swash plate (3) is arranged outside the pump housing (1).
2. Axialkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die die Taumelscheibe (3) in einer Abdeckung (16) angeordnet ist.2. Axial piston pump according to claim 1, characterized in that the swash plate (3) is arranged in a cover (16).
3. Axialkolbenpumpe nach Anspruch 2, dadurch gekennzeichnet, daß die Abdeckung (16) als Ventilblock und/oder als Elektronikbox eines elektronischen Bremssystems ausgebildet ist.3. Axial piston pump according to claim 2, characterized in that the cover (16) is designed as a valve block and / or as an electronics box of an electronic braking system.
4. Axialkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Kolben (4) zwischen der Taumelscheibe (3) und dem die Welle (2) antreibenden Motor angeordnet sind. 4. Axial piston pump according to claim 1, characterized in that the pistons (4) between the swash plate (3) and the shaft (2) driving motor are arranged.
. Axialkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, daß die Kolben (4) mittels Ruckstellfedern (5) zwischen der Taumelscheibe (3) und dem inneren Ende (10) von den die Kolben (4) aufnehmenden Bohrungen (7) eingespannt sind.. Axial piston pump according to claim 1, characterized in that the pistons (4) are clamped by means of return springs (5) between the swash plate (3) and the inner end (10) of the bores (7) receiving the pistons (4).
6. Axial kolbenpumpe nach Anspruch 5, dadurch gekennzeichnet, daß em Lager (6) der Welle (2) axial auf einer Flache (11) einer Stufenbohrung (12) des Pumpengehauses (1) abgestutzt ist, die dem inneren Ende (10) der Bohrungen (7) gegenüber liegt.6. Axial piston pump according to claim 5, characterized in that the bearing (6) of the shaft (2) is axially supported on a surface (11) of a stepped bore (12) of the pump housing (1), the inner end (10) of the Bores (7) is opposite.
7. Axialkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwischen Taumelscheibe (3) und Kolben (4) em Axiallager (13) angeordnet ist.7. Axial piston pump according to one of the preceding claims, characterized in that between the swash plate (3) and piston (4) em axial bearing (13) is arranged.
8. Axialkolbenpumpe nach Anspruch 7, dadurch gekennzeichnet, daß die dem Axiallager (13) zugewandten Enden der Kolben (4) abgerundet sind.8. Axial piston pump according to claim 7, characterized in that the ends of the pistons (4) facing the axial bearing (13) are rounded.
9. Axialkolbenteil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Bohrungen9. Axial piston part according to one of the preceding claims, characterized in that the bores
(7) mit im Pumpengehause (1) ausgebildeten Kanälen (14, 15) für die Zu- bzw. Abfuhr des Fordermediums verbunden sind. (7) are connected to channels (14, 15) formed in the pump housing (1) for the supply and discharge of the delivery medium.
PCT/EP1999/000448 1998-01-30 1999-01-26 Axial piston pump WO1999039100A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP99903678A EP1049874B1 (en) 1998-01-30 1999-01-26 Axial piston pump
DE59905314T DE59905314D1 (en) 1998-01-30 1999-01-26 axial piston pump
JP2000529539A JP2002502007A (en) 1998-01-30 1999-01-26 Axial piston pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803533.0 1998-01-30
DE19803533A DE19803533A1 (en) 1998-01-30 1998-01-30 Axial piston pump

Publications (1)

Publication Number Publication Date
WO1999039100A1 true WO1999039100A1 (en) 1999-08-05

Family

ID=7856093

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1999/000448 WO1999039100A1 (en) 1998-01-30 1999-01-26 Axial piston pump

Country Status (4)

Country Link
EP (1) EP1049874B1 (en)
JP (1) JP2002502007A (en)
DE (2) DE19803533A1 (en)
WO (1) WO1999039100A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102966504A (en) * 2012-12-10 2013-03-13 西安航空动力控制科技有限公司 Axial plunger pump with baffle type one-way valve and without sliding shoe or oil distributing disc

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008014974B4 (en) * 2008-03-19 2016-06-23 Schaeffler Technologies AG & Co. KG Swash bearing and method for its production
JP4740983B2 (en) * 2008-06-18 2011-08-03 三菱電機株式会社 Fuel supply device

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2998827A (en) * 1958-04-14 1961-09-05 Ernest E Cook Valve construction for fluid pressure pump and the like
FR1407267A (en) * 1964-06-20 1965-07-30 Sarl Rech S Etudes Production Advanced hydraulic pump, barrel and fluid bearings
DE1234529B (en) * 1963-11-13 1967-02-16 Teves Kg Alfred Axial roller bearings of the head swash plate of an axial piston pump
DE1453532A1 (en) * 1964-04-07 1969-09-25 Walter Hunger Hydraulic support devices for motor vehicles that can be operated by hand or by electric motor
DE4303205A1 (en) * 1993-02-04 1994-08-11 Teves Gmbh Alfred Pump, made of material produced in a continuous process, with a valve block, especially for a controlled braking system
DE4445522A1 (en) 1994-12-20 1996-06-27 Kaercher Gmbh & Co Alfred Piston pump for high pressure cleaning device

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1877285A (en) * 1931-10-01 1932-09-13 Eckels Engineering Corp Swash plate
JPS5011086B1 (en) * 1967-06-14 1975-04-26
DE3347307A1 (en) * 1983-12-28 1985-07-11 Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried PLUNGER PUMP
DE4203619C2 (en) * 1992-02-07 1996-07-25 Rexroth Mannesmann Gmbh Hydraulic system

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2998827A (en) * 1958-04-14 1961-09-05 Ernest E Cook Valve construction for fluid pressure pump and the like
DE1234529B (en) * 1963-11-13 1967-02-16 Teves Kg Alfred Axial roller bearings of the head swash plate of an axial piston pump
DE1453532A1 (en) * 1964-04-07 1969-09-25 Walter Hunger Hydraulic support devices for motor vehicles that can be operated by hand or by electric motor
FR1407267A (en) * 1964-06-20 1965-07-30 Sarl Rech S Etudes Production Advanced hydraulic pump, barrel and fluid bearings
DE4303205A1 (en) * 1993-02-04 1994-08-11 Teves Gmbh Alfred Pump, made of material produced in a continuous process, with a valve block, especially for a controlled braking system
DE4445522A1 (en) 1994-12-20 1996-06-27 Kaercher Gmbh & Co Alfred Piston pump for high pressure cleaning device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102966504A (en) * 2012-12-10 2013-03-13 西安航空动力控制科技有限公司 Axial plunger pump with baffle type one-way valve and without sliding shoe or oil distributing disc

Also Published As

Publication number Publication date
EP1049874A1 (en) 2000-11-08
DE59905314D1 (en) 2003-06-05
EP1049874B1 (en) 2003-05-02
JP2002502007A (en) 2002-01-22
DE19803533A1 (en) 1999-08-05

Similar Documents

Publication Publication Date Title
DE4138313C2 (en) Radial piston pump
DE4225380B4 (en) Hydrostatic unit with a main pump and a secondary pump
DE10161715A1 (en) Electrical power steering for motor vehicle has hydraulic pressure biasing device, coupling for connecting drive shaft to worm and pivotable bearing in coupling region
EP1831546B1 (en) Drive device
DE102005034571A1 (en) Electrohydraulic unit
WO1999060271A1 (en) Motor-driven pump assembly
DE19831838B4 (en) braking device
EP1049874B1 (en) Axial piston pump
WO2001056850A1 (en) Brake unit
EP0638144B1 (en) Gear machine
EP1986901A1 (en) Drive unit for hydraulic piston pumps, with eccentrics, of a vehicle brake system
WO2005065978A1 (en) Hydrostatic drive system with pump-sided division of the amount of hydraulic fluid for two hydraulic circuits
WO2012010262A1 (en) Piston unit
DE69100392T2 (en) Hydrostatically driven axle of a forklift.
WO2007028687A1 (en) Piston pump with swash plate drive
DE19855899B4 (en) axial piston
DE102012210199A1 (en) Plunger assembly for high-pressure fuel pump to support liftable pump piston of pump element, has supporting element forming lateral faces that are spaced apart from peripheral wall of plunger body to form cavities
DE8802023U1 (en) Tandem pump
EP0302190B1 (en) Internal-gear machine
DE19704248A1 (en) Pump unit for vehicle brake system
DE19910659C2 (en) Hydraulic piston machine unit
DE102020001586B4 (en) Swivel drive for a swiveling ramp, in particular for the entry and exit aid for wheelchair users
DE102006041480B4 (en) Motor-pump unit with a pump drive shaft high elasticity and an eccentric at the drive shaft end
WO2022228606A1 (en) Electric-motor-driven hydraulic pump actuator
DE2332621A1 (en) Hydrostatic torque converter for small vehicles - uses axial piston variable output pump driving constant inward flow motor

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE

121 Ep: the epo has been informed by wipo that ep was designated in this application
DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
WWE Wipo information: entry into national phase

Ref document number: 1999903678

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 09601045

Country of ref document: US

WWP Wipo information: published in national office

Ref document number: 1999903678

Country of ref document: EP

WWG Wipo information: grant in national office

Ref document number: 1999903678

Country of ref document: EP