WO2008128880A1 - Pump unit for producing high pressures - Google Patents
Pump unit for producing high pressures Download PDFInfo
- Publication number
- WO2008128880A1 WO2008128880A1 PCT/EP2008/054162 EP2008054162W WO2008128880A1 WO 2008128880 A1 WO2008128880 A1 WO 2008128880A1 EP 2008054162 W EP2008054162 W EP 2008054162W WO 2008128880 A1 WO2008128880 A1 WO 2008128880A1
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- WO
- WIPO (PCT)
- Prior art keywords
- pump
- piston
- outlet
- pump device
- valve
- Prior art date
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Classifications
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
- F04B53/125—Reciprocating valves
- F04B53/126—Ball valves
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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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
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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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0421—Cylinders
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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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0452—Distribution members, e.g. valves
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
- F04B53/166—Cylinder liners
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
- F04B53/166—Cylinder liners
- F04B53/168—Mounting of cylinder liners in cylinders
Definitions
- the invention relates to a pump device, in particular for generating pressures of up to 3000 bar and more, according to the preamble of claim 1.
- Fig. 2 shows a known high-pressure feed pump device 101 for common rail diesel injection systems for generating a maximum of about 2200 bar discharge pressure.
- This pumping device 101 comprises a pump piston 103 guided in a pump housing 102, a cylindrical pump chamber 104, which is formed by an axial bore and bounded by the pump piston 103, an intake valve 105, via which the pump chamber 104 is connected to an inlet line 106, and an outlet valve 107, via which the pump chamber 104 is connected to an outlet line 108.
- the inlet line 106 opens on the opposite side of the pump piston 103 coaxially to the piston axis 109 in the pump chamber 104.
- the outlet 108 goes radially to the piston axis 109 from the pump chamber 104 and is formed as a radial bore, which leads to 117 at an intersection.
- the pump piston 103 is driven to oscillate via the cam 112 of a cam drive.
- the pressure increase is achieved by targeted avoidance or by compensation of weak points, so that higher quality and therefore extremely expensive materials can be dispensed with.
- the pump device according to the invention is constructed consistently axially symmetrical. Critical intersections that lead to stress peaks are avoided.
- the intake valve is practically under hydrostatic pressure and is therefore low in tension.
- the pump housing is clamped with a respect to the piston axis conical outer surface in a corresponding conical sleeve opening of a clamping sleeve and thereby biased during assembly radially inwardly, whereby the tensile stresses acting during operation on the outer circumferential surface can be significantly reduced.
- pressures greater than 3000 bar can be reached permanently with materials that allow only about 2200 bar in the conventional design.
- FIG. 1 shows a longitudinal section through the pump device according to the invention.
- Fig. 2 is a longitudinal section through a pump device according to the prior
- the pump device 1 shown in Fig. 1 is used to generate pressures of up to 3000 bar or more and comprises a guided in a cylindrical pump housing 2 pump piston 3, a pump chamber 4, which is bounded by the pump piston 3, an intake valve 5, via the the pump space 4 is connected to an inlet line 6, and an outlet valve 7, via which the pump space 4 is connected to an outlet line 8.
- the inlet line 6 extends in the pump piston 3 coaxially to the piston axis 9 to the pump chamber 4, wherein the intake valve 5 is arranged in the pump piston 3 in the coaxial inlet line 6.
- the outlet line 8 extends on the pump piston 3 opposite side of the pump chamber 4 coaxially to the piston axis 9 from the pump chamber 4 into the pump housing 2, wherein the outlet valve 7 is arranged in the pump housing 2 in the coaxial outlet 8.
- the intake and exhaust valves 5, 7 are spring-loaded check valves, each with a ball 10 which opens in the suction or discharge direction against the action of a spring 11 and closes in the opposite direction.
- the pump piston 3 is driven in an oscillating manner via the cam 12 of a cam drive.
- the inlet and outlet lines 6, 8, the intake and exhaust valves 5, 7 and the conical outer surface 13 of the pump housing 2 are rotationally symmetrical with respect to the piston axis 9, so that the entire pump device 1 is rotationally or axially symmetrical with respect to the piston axis 9.
- the pump housing 2 with its conical outer surface 13 is axially clamped in a correspondingly conical bore of a clamping sleeve 14, as indicated by the arrows 15, and thereby biased radially inwardly.
- the pump housing 2, in particular in the highly loaded region of the pump chamber 4 and the outlet valve 7, can be pretensioned defined over the conical surfaces of the clamping sleeve 14 and the pump housing 2 in the housing assembly (self-locking conical surfaces, sleeve suit over thread, etc.). So there are pressure stresses in the unpressurized state, and only when pumping arise along the outer circumferential surface 13 of the pump housing 2 tensile stresses, the amount of which is substantially lower than in conventional pumps without bias. A load point displaced in the direction of pressure is much better tolerated by the material than a load point which lies purely in the tensile area.
- the suction valve 5 is also practically under hydrostatic pressure: From the pump chamber 4 and from the side (leakage gap, pressure drop from high pressure to low pressure), the pressure prevailing in the pump chamber 4 acts, and the pump chamber 4 facing away from the end face of the pump piston 3, the cam force acts 16 that corresponds to the pressure in the pump chamber 4; So the three main voltages are about the same.
- the outlet valve 7 is connected directly above the pump chamber 4. This results in a Verschneidungsoker transition of the small diameter of the axial bore of the outlet 8 to the large diameter of the pump chamber 4, which causes no voltage peaks (notch effect).
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a pump unit (1) comprising a pump piston (3) guided inside a pump case (2), a pump chamber (4) which is delimited by the pump piston (3), an inlet valve (5) via which the pump chamber (4) is connected to an inlet line (6), and an outlet valve (7) via which the pump chamber (4) is connected to an outlet line (8). The pump unit is characterized in that the inlet line (6) extends in the pump piston (3) coaxially to the piston axis (9) up to the pump chamber (4) and the inlet valve (5) is arranged in the pump piston (3) in the coaxial inlet line (6). The invention is also characterized in that the outlet line (8) branches off into the pump case (2) coaxially to the piston axis (9) on the side of the pump chamber (4) opposite the pump piston (3) and that the outlet valve (7) is arranged in the pump case (2) in the coaxial outlet line (8).
Description
Pumpenvorrichtung zur Erzeugung hoher Drücke Pump device for generating high pressures
Stand der TechnikState of the art
Die Erfindung betrifft eine Pumpenvorrichtung, insbesondere zur Erzeugung von Drücken von bis zu 3000 bar und mehr, nach dem Oberbegriff des Anspruchs 1.The invention relates to a pump device, in particular for generating pressures of up to 3000 bar and more, according to the preamble of claim 1.
Für Common Rail Dieseleinspritzsysteme werden Hochdruck-Förderpumpen benötigt. Diese Pumpen erreichen derzeit bei ungefähr 2200 bar Förderdruck ihre Festigkeitsgrenze, die einerseits durch den verwendeten Werkstoff und andererseits durch die Bauart der Pumpe definiert ist. Die Schwachstellen dabei sind Hochdruckverschneidungen im Pumpengehäuse und die Ein- und Auslassventile.Common rail diesel injection systems require high-pressure pumps. These pumps currently reach their strength limit at approximately 2200 bar discharge pressure, which is defined on the one hand by the material used and on the other by the design of the pump. The weak points are high-pressure intersections in the pump housing and the inlet and outlet valves.
Fig. 2 zeigt eine bekannte Hochdruck-Förderpumpenvorrichtung 101 für Common Rail Dieseleinspritzsysteme zum Erzeugen von maximal ca. 2200 bar Förderdruck.
Diese Pumpvorrichtung 101 umfasst einen in einem Pumpengehäuse 102 geführten Pumpenkolben 103, einen zylindrischen Pumpenraum 104, der durch eine Axialbohrung gebildet und durch den Pumpenkolben 103 begrenzt ist, ein Ansaugventil 105, über das der Pumpenraum 104 mit einer Einlassleitung 106 verbunden ist, und ein Auslassventil 107, über das der Pumpenraum 104 mit einer Auslassleitung 108 verbunden ist. Die Einlassleitung 106 mündet auf der dem Pumpenkolben 103 gegenüberliegenden Seite koaxial zur Kolbenachse 109 in den Pumpenraum 104. Die Auslassleitung 108 geht radial zur Kolbenachse 109 aus dem Pumpenraum 104 ab und ist als Radialbohrung ausgebildet, was bei 117 zu einer Verschneidung führt. Der Pumpenkolben 103 wird über die Nocke 112 eines Nockenantriebs oszillierend angetrieben.Fig. 2 shows a known high-pressure feed pump device 101 for common rail diesel injection systems for generating a maximum of about 2200 bar discharge pressure. This pumping device 101 comprises a pump piston 103 guided in a pump housing 102, a cylindrical pump chamber 104, which is formed by an axial bore and bounded by the pump piston 103, an intake valve 105, via which the pump chamber 104 is connected to an inlet line 106, and an outlet valve 107, via which the pump chamber 104 is connected to an outlet line 108. The inlet line 106 opens on the opposite side of the pump piston 103 coaxially to the piston axis 109 in the pump chamber 104. The outlet 108 goes radially to the piston axis 109 from the pump chamber 104 and is formed as a radial bore, which leads to 117 at an intersection. The pump piston 103 is driven to oscillate via the cam 112 of a cam drive.
Um die Emissionen von Dieselmotoren weiter zu senken, soll mit immer höheren Drücken eingespritzt werden. Möchte man einfache Lösungen ohne hydraulische Druckverstärker realisieren, benötigt man zukünftig einstufige Hochdruck- Förderpumpen, die möglichst bis 3000 bar und mehr aushalten und liefern.In order to further reduce the emissions of diesel engines should be injected with ever higher pressures. If you want to realize simple solutions without hydraulic pressure booster, you will need in the future single-stage high-pressure feed pumps, the possible up to 3000 bar and more endure and deliver.
Offenbarung der ErfindungDisclosure of the invention
Erfindungsgemäß wird die Drucksteigerung durch gezielte Vermeidung oder durch Ausgleich von Schwachstellen erreicht, so dass auf hochwertigere und damit extrem teuere Werkstoffe verzichtet werden kann. Die erfindungsgemäße Pumpenvorrichtung ist konsequent axialsymmetrisch aufgebaut. Kritische Verschneidungen, die zu Spannungsüberhöhungen führen, werden vermieden. Das Ansaugventil steht praktisch unter hydrostatischem Druck und ist damit spannungsarm. Vorzugsweise ist das Pumpengehäuse mit einer bezüglich der Kolbenachse konischen Außenmantelfläche in einer entsprechend konischen Hülsenöffnung einer Spannhülse eingespannt und dadurch bei der Montage radial nach innen vorgespannt, wodurch die im Betrieb an der Außenmantelfläche wirkenden Zugspannungen deutlich verringert werden können. So sind Drücke größer 3000 bar dauerfest mit Werkstoffen erreichbar, die bei herkömmlicher Bauart nur ca. 2200 bar erlauben.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.According to the invention, the pressure increase is achieved by targeted avoidance or by compensation of weak points, so that higher quality and therefore extremely expensive materials can be dispensed with. The pump device according to the invention is constructed consistently axially symmetrical. Critical intersections that lead to stress peaks are avoided. The intake valve is practically under hydrostatic pressure and is therefore low in tension. Preferably, the pump housing is clamped with a respect to the piston axis conical outer surface in a corresponding conical sleeve opening of a clamping sleeve and thereby biased during assembly radially inwardly, whereby the tensile stresses acting during operation on the outer circumferential surface can be significantly reduced. Thus, pressures greater than 3000 bar can be reached permanently with materials that allow only about 2200 bar in the conventional design. Further advantages and advantageous embodiments of the subject invention are the description, the drawings and claims removed.
Kurze Beschreibung der ZeichnungShort description of the drawing
Nachfolgend wird eine besonders bevorzugte Ausführungsform der vorliegenden Erfindung unter Bezugnahme auf die beiliegende Zeichnung näher erläutert. In der Zeichnung zeigen:Hereinafter, a particularly preferred embodiment of the present invention will be explained in more detail with reference to the accompanying drawings. In the drawing show:
Fig. 1 einen Längsschnitt durch die erfindungsgemäße Pumpenvorrichtung; und Fig. 2 einen Längsschnitt durch eine Pumpenvorrichtung nach dem Stand der1 shows a longitudinal section through the pump device according to the invention. and Fig. 2 is a longitudinal section through a pump device according to the prior
Technik.Technology.
Ausführungsform der ErfindungEmbodiment of the invention
Die in Fig. 1 gezeigte Pumpvorrichtung 1 dient zum Erzeugen von Drücken von bis zu 3000 bar oder mehr und umfasst einen in einem zylinderförmigen Pumpengehäuse 2 geführten Pumpenkolben 3, einen Pumpenraum 4, der durch den Pumpenkolben 3 begrenzt ist, ein Ansaugventil 5, über das der Pumpenraum 4 mit einer Einlassleitung 6 verbunden ist, und ein Auslassventil 7, über das der Pumpenraum 4 mit einer Auslassleitung 8 verbunden ist. Die Einlassleitung 6 erstreckt sich im Pumpenkolben 3 koaxial zur Kolbenachse 9 bis zum Pumpenraum 4, wobei das Ansaugventil 5 im Pumpenkolben 3 in der koaxialen Einlassleitung 6 angeordnet ist. Die Auslassleitung 8 geht auf der dem Pumpenkolben 3 gegenüberliegenden Seite des Pumpenraums 4 koaxial zur Kolbenachse 9 aus dem Pumpenraum 4 in das Pumpengehäuse 2 ab, wobei das Auslassventil 7 im Pumpengehäuse 2 in der koaxialen Auslassleitung 8 angeordnet ist. Die Ansaug- und Auslassventile 5, 7 sind federbelastete Rückschlagventile mit jeweils einer Kugel 10, die in Saug- bzw. Auslassrichtung gegen die Wirkung einer Feder 11 öffnet und in der Gegenrichtung schließt. Der Pumpenkolben 3 wird über die Nocke 12 eines Nockenantriebs oszillierend angetrieben.
Die Ein- und Auslassleitungen 6, 8, die Ansaug- und Auslassventile 5, 7 und die konische Außenmantelfläche 13 des Pumpengehäuses 2 sind bezüglich der Kolbenachse 9 rotationssymmethsch, so dass die gesamte Pumpenvorrichtung 1 bezüglich der Kolbenachse 9 rotations- bzw. axialsymmethsch ist.The pump device 1 shown in Fig. 1 is used to generate pressures of up to 3000 bar or more and comprises a guided in a cylindrical pump housing 2 pump piston 3, a pump chamber 4, which is bounded by the pump piston 3, an intake valve 5, via the the pump space 4 is connected to an inlet line 6, and an outlet valve 7, via which the pump space 4 is connected to an outlet line 8. The inlet line 6 extends in the pump piston 3 coaxially to the piston axis 9 to the pump chamber 4, wherein the intake valve 5 is arranged in the pump piston 3 in the coaxial inlet line 6. The outlet line 8 extends on the pump piston 3 opposite side of the pump chamber 4 coaxially to the piston axis 9 from the pump chamber 4 into the pump housing 2, wherein the outlet valve 7 is arranged in the pump housing 2 in the coaxial outlet 8. The intake and exhaust valves 5, 7 are spring-loaded check valves, each with a ball 10 which opens in the suction or discharge direction against the action of a spring 11 and closes in the opposite direction. The pump piston 3 is driven in an oscillating manner via the cam 12 of a cam drive. The inlet and outlet lines 6, 8, the intake and exhaust valves 5, 7 and the conical outer surface 13 of the pump housing 2 are rotationally symmetrical with respect to the piston axis 9, so that the entire pump device 1 is rotationally or axially symmetrical with respect to the piston axis 9.
Das Pumpengehäuse 2 mit seiner konischen Außenmantelfläche 13 ist in einer entsprechend konischen Bohrung einer Spannhülse 14 axial eingespannt, wie durch die Pfeile 15 angedeutet ist, und dadurch radial nach innen vorgespannt. Das Pumpengehäuse 2, insbesondere im hoch belasteten Bereich des Pumpenraums 4 und des Auslassventils 7, kann über die Kegelflächen der Spannhülse 14 und des Pumpengehäuses 2 bei der Gehäusemontage definiert vorgespannt werden (selbst hemmende Kegelflächen, Hülsenanzug über Gewinde, etc.). So liegen dort im drucklosen Zustand Druckspannungen vor, und erst beim Pumpen entstehen entlang der Außenmantelfläche 13 des Pumpengehäuses 2 Zugspannungen, deren Betrag wesentlich geringer ist als bei konventionellen Pumpen ohne Vorspannung. Ein in Richtung Druck verlagerter Lastpunkt wird vom Werkstoff wesentlich besser ertragen, als ein Lastpunkt der rein im Zugbereich liegt.The pump housing 2 with its conical outer surface 13 is axially clamped in a correspondingly conical bore of a clamping sleeve 14, as indicated by the arrows 15, and thereby biased radially inwardly. The pump housing 2, in particular in the highly loaded region of the pump chamber 4 and the outlet valve 7, can be pretensioned defined over the conical surfaces of the clamping sleeve 14 and the pump housing 2 in the housing assembly (self-locking conical surfaces, sleeve suit over thread, etc.). So there are pressure stresses in the unpressurized state, and only when pumping arise along the outer circumferential surface 13 of the pump housing 2 tensile stresses, the amount of which is substantially lower than in conventional pumps without bias. A load point displaced in the direction of pressure is much better tolerated by the material than a load point which lies purely in the tensile area.
Da das Ansaugventil 5 im Pumpenkolben 3 untergebracht ist, entsteht hier keine Verschneidung. Das Ansaugventil 5 steht so auch praktisch unter hydrostatischem Druck: Vom Pumpenraum 4 und von der Seite (Leckagespalt, Druckabfall von Hochdruck nach Niederdruck) wirkt der im Pumpenraum 4 herrschende Druck, und auf die dem Pumpenraum 4 abgewandte Stirnseite des Pumpenkolbens 3 wirkt die Nockenkraft 16, die dem Druck im Pumpenraum 4 entspricht; die drei Hauptspannungen sind also ungefähr gleich. So ergeben sich in dem in Fig. 1 oberen Bereich des Pumpenkolbens 3 sehr niedrige Vergleichsspannungen um Null und damit ein unkritischer Ventilbereich. Das Auslassventil 7 ist oben direkt am Pumpenraum 4 angeschlossen. Es entsteht so ein verschneidungsfreier Übergang des kleinen Durchmessers der Axialbohrung der Auslassleitung 8 zum großen Durchmesser des Pumpenraumes 4, der keine Spannungsüberhöhungen (Kerbwirkung) verursacht.
Since the intake valve 5 is housed in the pump piston 3, there is no intersection. The suction valve 5 is also practically under hydrostatic pressure: From the pump chamber 4 and from the side (leakage gap, pressure drop from high pressure to low pressure), the pressure prevailing in the pump chamber 4 acts, and the pump chamber 4 facing away from the end face of the pump piston 3, the cam force acts 16 that corresponds to the pressure in the pump chamber 4; So the three main voltages are about the same. Thus, in the upper region of the pump piston 3 in FIG. 1, very low reference stresses occur around zero and thus an uncritical valve region. The outlet valve 7 is connected directly above the pump chamber 4. This results in a Verschneidungsfreier transition of the small diameter of the axial bore of the outlet 8 to the large diameter of the pump chamber 4, which causes no voltage peaks (notch effect).
Claims
1. Pumpenvorrichtung (1 ) mit einem in einem Pumpengehäuse (2) geführten Pumpenkolben (3), mit einem Pumpenraum (4), der durch den Pumpenkolben (3) begrenzt ist, mit einem Ansaugventil (5), über das der Pumpenraum (4) mit einer Einlassleitung (6) verbunden ist, und mit einem Auslassventil (7), über das der Pumpenraum (4) mit einer Auslassleitung (8) verbunden ist, dadurch gekennzeichnet, dass sich die Einlassleitung (6) im Pumpenkolben (3) koaxial zur Kolbenachse (9) bis zum Pumpenraum (4) erstreckt und das Ansaugventil (5) im Pumpenkolben (3) in der koaxialen Einlassleitung (6) angeordnet ist, und dass die Auslassleitung (8) auf der dem Pumpenkolben (3) gegenüberliegenden Seite des Pumpenraums (4) koaxial zur Kolbenachse (9) in das Pumpengehäuse (2) abgeht und das Auslassventil (7) im Pumpengehäuse (2) in der koaxialen Auslassleitung (8) angeordnet ist.A pump device (1) with a pump piston (3) guided in a pump housing (2), with a pump chamber (4) bounded by the pump piston (3), with a suction valve (5) via which the pump chamber (4 ) is connected to an inlet line (6) and to an outlet valve (7) via which the pump space (4) is connected to an outlet line (8), characterized in that the inlet line (6) in the pump piston (3) is coaxial extends to the piston axis (9) to the pump chamber (4) and the suction valve (5) in the pump piston (3) in the coaxial inlet line (6) is arranged, and that the outlet line (8) on the pump piston (3) opposite side of Pump chamber (4) coaxial with the piston axis (9) in the pump housing (2) goes off and the outlet valve (7) in the pump housing (2) in the coaxial outlet line (8) is arranged.
2. Pumpenvorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das Pumpengehäuse (2) eine bezüglich der Kolbenachse (9) rotationssymmetrische Außenmantelfläche (13) aufweist.2. Pump device according to claim 1, characterized in that the pump housing (2) has a relative to the piston axis (9) rotationally symmetrical outer circumferential surface (13).
3. Pumpenvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Außenmantelfläche (13) des Pumpengehäuses (2) von einem Spannelement (14) formschlüssig umgeben ist.3. Pump device according to claim 1 or 2, characterized in that the outer circumferential surface (13) of the pump housing (2) by a clamping element (14) is positively surrounded.
4. Pumpenvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass das Pumpengehäuse (2) durch das Spannelement (14) radial nach innen vorgespannt ist. 4. Pump device according to claim 3, characterized in that the pump housing (2) is biased by the clamping element (14) radially inwardly.
5. Pumpenvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Spannelement (14) eine Spannhülse ist.5. Pump device according to one of the preceding claims, characterized in that the clamping element (14) is a clamping sleeve.
6. Pumpenvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Pumpengehäuse (2) mit seiner bezüglich der Kolbenachse (9) konischen Außenmantelfläche (13) in einer entsprechend konischen Bohrung eines Spannelements (14) eingespannt ist.6. Pump device according to one of the preceding claims, characterized in that the pump housing (2) with its relative to the piston axis (9) conical outer lateral surface (13) in a correspondingly conical bore of a clamping element (14) is clamped.
7. Pumpenvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ansaugventil (5) und/oder das Auslassventil (7) federbelastete Rückschlagventile sind, die in Saug- bzw. Auslassrichtung gegen die Wirkung einer Feder (11 ) öffnen und in der Gegenrichtung schließen.7. Pump device according to one of the preceding claims, characterized in that the intake valve (5) and / or the outlet valve (7) are spring-loaded check valves which open in the suction or outlet direction against the action of a spring (11) and in the opposite direction shut down.
8. Pumpenvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Pumpenvorrichtung (1 ) bezüglich der Kolbenachse (9) rotationssymmetrisch ist. 8. Pump device according to one of the preceding claims, characterized in that the pump device (1) with respect to the piston axis (9) is rotationally symmetrical.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102007018235.1 | 2007-04-18 | ||
| DE200710018235 DE102007018235A1 (en) | 2007-04-18 | 2007-04-18 | Pump device for generating high pressures |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2008128880A1 true WO2008128880A1 (en) | 2008-10-30 |
Family
ID=39638769
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/EP2008/054162 WO2008128880A1 (en) | 2007-04-18 | 2008-04-07 | Pump unit for producing high pressures |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE102007018235A1 (en) |
| WO (1) | WO2008128880A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012223119A1 (en) * | 2012-12-13 | 2014-06-18 | Robert Bosch Gmbh | Cylinder of a piston pump of a vehicle brake system |
| GB2549745A (en) * | 2016-04-27 | 2017-11-01 | Delphi Int Operations Luxembourg Sarl | High pressure fuel pump |
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|---|---|---|---|---|
| US3128718A (en) * | 1961-05-08 | 1964-04-14 | Stanley J Rhodes | High pressure pump |
| DE19854716A1 (en) * | 1998-11-26 | 2000-05-31 | Continental Teves Ag & Co Ohg | Piston pump |
| US20010048884A1 (en) * | 1997-07-30 | 2001-12-06 | Heinz Siegel | Piston pump for a brake system for a vehicle |
| WO2002068844A1 (en) * | 2001-02-21 | 2002-09-06 | Utex Industries, Inc. | Pump liner |
| US20050249615A1 (en) * | 2002-06-14 | 2005-11-10 | Jetstream Of Houston, Llp | High pressure reciprocating pump |
-
2007
- 2007-04-18 DE DE200710018235 patent/DE102007018235A1/en not_active Withdrawn
-
2008
- 2008-04-07 WO PCT/EP2008/054162 patent/WO2008128880A1/en active Application Filing
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3128718A (en) * | 1961-05-08 | 1964-04-14 | Stanley J Rhodes | High pressure pump |
| US20010048884A1 (en) * | 1997-07-30 | 2001-12-06 | Heinz Siegel | Piston pump for a brake system for a vehicle |
| DE19854716A1 (en) * | 1998-11-26 | 2000-05-31 | Continental Teves Ag & Co Ohg | Piston pump |
| WO2002068844A1 (en) * | 2001-02-21 | 2002-09-06 | Utex Industries, Inc. | Pump liner |
| US20050249615A1 (en) * | 2002-06-14 | 2005-11-10 | Jetstream Of Houston, Llp | High pressure reciprocating pump |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102007018235A1 (en) | 2008-10-23 |
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