WO2007057285A1 - Multi-piston pump - Google Patents
Multi-piston pump Download PDFInfo
- Publication number
- WO2007057285A1 WO2007057285A1 PCT/EP2006/067824 EP2006067824W WO2007057285A1 WO 2007057285 A1 WO2007057285 A1 WO 2007057285A1 EP 2006067824 W EP2006067824 W EP 2006067824W WO 2007057285 A1 WO2007057285 A1 WO 2007057285A1
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- WO
- WIPO (PCT)
- Prior art keywords
- piston
- pump
- eccentric
- piston pumps
- piston pump
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
- B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
- B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
- B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
- B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
- B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
- B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master 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
- F04B1/0421—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
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
- F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
- F04B1/0538—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units located side-by-side
Definitions
- the present invention relates to a multi-piston pump according to the preamble of claim 1.
- Such a multi-piston pump is known for example from DE 103 53 834 Al. Such multi-piston pumps are used for example in motor vehicles for the pressure build-up in brake systems.
- the known multi-piston pump has two eccentrics, which are arranged in series and each drive three piston pumps.
- the piston pumps are arranged in two parallel planes at the height of the eccentric.
- the piston pumps associated with each eccentric are arranged at different angles to one another around the eccentric.
- two piston pumps of the first eccentric are connected to a piston pump of the second excenter and two piston pumps of the second eccentric are connected to a piston pump of the first eccentric.
- the eccentrics are arranged rotated by an angle of about 150 ° to each other.
- the multi-piston pump according to the invention with the features of claim 1 has the advantage that it ensures a uniform circumferential load of a drive shaft and the bearing of the drive shaft bearing. This also noise can be reduced and in particular a pulsation-free promotion can be achieved.
- the multi-piston pump according to the invention can be provided easier and cheaper. This is inventively achieved in that each piston pump of a first pump unit is arranged parallel to a piston pump of a second pump unit. This ensures that the piston pumps of the first and second pump units are arranged the same. This avoids that non-uniform mechanical forces are exerted on the drive shaft and the bearing by different arrangement of the piston pumps.
- the parallel arrangement of the piston pumps of the first and second pump units results in a reduced number of directions, from which it is necessary to manufacture and assemble. Moreover, the parallel arrangement can still ensure that line lengths of the lines to and from the first pump unit and line lengths of the lines from and to the second pump unit can be made the same length. This has the great advantage that this same response times can be achieved by different brake circuits, which are each supplied by the first and second pump unit. As a result, the brake circuits can be connected, for example directly without detours with a high-pressure switching valve in each brake circuit.
- the first and second pump units each comprise three piston pumps.
- the piston pumps are preferably each arranged at an angle of 120 ° at the first and second eccentric.
- Another advantage is that the two brake circuits can now be performed hydraulically symmetrical, which further simplifies the production. Since the multi-piston pumps according to the invention are preferably used in vehicles and therefore are mass products, the parallel arrangements of the piston pumps according to the invention result in great savings potentials.
- first eccentric and the second eccentric are arranged at an angle to each other twisted.
- the angle is particularly preferably about 150 °.
- the piston pumps of the first pump unit are arranged in a first half of the multi-piston pump and the piston pumps of the second pump unit are arranged in a second half of the multi-piston pump.
- the piston pumps of a pump unit are particularly preferably arranged in one half in an angular range of about 120 °. This provides a very compact structure.
- FIG. 1 shows a schematic, perspective view of a multi-piston pump according to an exemplary embodiment of the invention
- Figure 2 is a schematic plan view illustrating the arrangement of the piston pumps of the first and second pump unit, and - A -
- Figure 3 is a schematic representation of a brake system with the multi-piston pump according to the invention.
- the multi-piston pump 1 comprises a housing 2, a first pump unit 3 and a second pump unit 4.
- the first pump unit 3 comprises three piston pumps 3a, 3b, 3c and the second pump unit 4 comprises three piston pumps 4a, 4b, 4c.
- three piston pumps are arranged around a first eccentric 5 and a second eccentric 6.
- two piston pumps 3a, 3b of the first pump unit 3 and a piston pump 4c of the second pump unit 4 are assigned to the first eccentric 5.
- the second eccentric 6 is associated with a piston pump 3 c of the first pump unit 3 and two piston pumps 4 a, 4 b of the second pump unit 4.
- the piston pumps 3a, 3b, 3c of the first pump unit 3 thereby provide the pressure in a first brake circuit I and the piston pumps 4a, 4b, 4c of the second pump unit 4 provide the pressure for a second brake circuit II ready.
- a pedal P and a pressure medium container D and four wheel brakes VR, HL, VL and HR is shown schematically.
- the brake circuit distribution of this embodiment is an X-brake circuit division, wherein the brake circuits I and II in a known manner still inlet, exhaust, changeover and high-pressure switching valves, which will not be described in detail.
- the piston pumps 3a, 3b; 4c arranged in a first plane El in the housing 2 and the piston pumps 4a, 4b; 3c arranged in a second plane E2 in the housing 2.
- the first eccentric 5 is also arranged in the first plane E1
- the second eccentric 6 is arranged in the second plane E2.
- a recess 7 is arranged, which serves for receiving the first eccentric 5 and the second eccentric 6.
- a first low-pressure accumulator 8a and a second low-pressure accumulator 8a accumulator 8b arranged in the housing 2.
- Low pressure lines go from the first low pressure accumulator 8a to the first pump unit 3 and low pressure accumulators 8b go to the second pump unit 4.
- the low pressure lines from the first low pressure accumulator 8a to the piston pumps 3c and 3b are very short.
- the low pressure line to the piston pump 3 a can also be relatively easily realized by two holes which are arranged at 90 ° to each other.
- the high-pressure lines of the first and second pump units 3, 4 can be designed in a simple manner. As shown in Figure 1, between the piston pump 3b and the piston pump 3c of the first pump unit 3, which are arranged parallel to each other, only a short connection bore to a switching valve or a master cylinder connection 9 of the brake circuit I necessary. From the piston pump 3a and 3b then goes a horizontal / vertical high pressure line directly to the connection of the intake valves in the brake circuit I. In the second pump unit 4, the high pressure lines to a master cylinder connection of the brake circuit Il are also simple.
- the piston pump 4a is about two at 90 ° - to each other arranged holes also with the Inlet valves connected in the brake circuit Il.
- the connections 9, 10 are arranged on a shoulder formed in the housing 2.
- the same line lengths for the first and second pump units 3, 4 also ensure that no braking occurs at the wheel brakes VR, HL or VL, HR during braking between the two brake circuits I and II.
- the eccentric unit comprising the first and second eccentrics 5, 6 is arranged in the recess 7 and is driven by an electric motor, not shown.
- the electric motor can be placed directly on the housing 2.
- the first eccentric 5 and the second eccentric 6 are arranged rotated by an angle of approximately 150 ° with respect to one another (cf., FIG. 3), wherein the eccentricity of the two eccentrics 5, 6 is chosen to be the same.
- the parallel arrangement of the piston pumps on the first and second eccentric 5, 6 ensures that that during operation of the multi-piston pump uniform load changes in a sequence of 0 o ... 30 ° ... 120 °, 150 ° ... 240 ° ...
- the piston pumps 3 a, 3 b, 3 c of the first pump unit are arranged in an angular range ⁇ of 120 °.
- the piston pumps 4a, 4b, 4c of the second pump unit 4 are arranged in an angular range ⁇ of 120 °.
- the arrangement of the piston pumps is such that the piston pumps 3 a, 3 b, 3 c of the first pump unit 3 in a first half 11 and the piston pumps 4 a, 4 b, 4 c of the second pump unit 4 are arranged in a second half 12.
- the piston pumps are shown schematically in Figure 2 by lines.
- FIG. 2 makes it clear again that a particularly compact design can be realized by the inventive, in pairs parallel arrangement of piston pumps on the first and second eccentric 5, 6.
- the multi-piston pump 1 can thereby be constructed symmetrically, so that in particular a hydraulic symmetry with respect to the cable lengths in the housing can be easily realized. This makes it possible that the Saug effetsaniere the multi-piston pumps can be connected directly to a high-pressure switching valve.
- Figure 2 also makes it clear that the production and assembly of the multi-piston pump can also be simplified significantly, since, for example, the piston pumps are mounted only in three directions or holes must be introduced into the housing. As a result, manufacturing and assembly aids can be significantly simplified.
- the connecting lines between the individual piston pumps of each pump unit 3, 4 can be made particularly short, since the piston pumps are provided in pairs in parallel. This also significantly reduces a drilling effort in the housing 2.
- the idea according to the invention of the parallel arrangement of piston pumps of different eccentrics in combination with the distribution of the piston pumps of a pump unit on two eccentrics 5, 6 can furthermore avoid pressure pulsation during operation, wherein the symmetrical arrangement of the piston Pumps on the Excentern also caused by mechanical load changes noise emissions also prevented.
- the multi-piston pump according to the invention is additionally particularly cost-effective and easy to produce.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- Electromagnetism (AREA)
- Fluid Mechanics (AREA)
- Transportation (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The present invention relates to a multi-piston pump comprising a housing (2), a first pump unit (3) having a plurality of piston pumps (3a, 3b, 3c) for the pressure supply of a first pressure circuit (I), a second pump unit (4) having a plurality of piston pumps (4a, 4b, 4c) for the pressure supply of a second pressure circuit (II), a drive and an eccentric unit having a first eccentric (5) and a second eccentric (6), wherein the first and the second eccentrics (5, 6) drive the plurality of piston pumps (3a, 3b, 3c; 4a, 4b, 4c), and wherein the first and second pump units (3, 4) comprise in each case at least one piston pump (3a, 3b; 4c) which can be driven by the first eccentric (5) and one piston pump (3c; 4a, 4b) which can be driven by the second eccentric (6), characterized in that in each case one piston pump (3a, 3b; 4c) which is driven by the first eccentric (6) is arranged parallel to a piston pump (4a, 4b; 3c) which is driven by the second eccentric (6).
Description
Beschreibungdescription
Titel MehrkolbenpumpeTitle multi-piston pump
Stand der TechnikState of the art
Offenbarung der ErfindungDisclosure of the invention
Die vorliegende Erfindung betrifft eine Mehrkolbenpumpe nach dem Oberbegriff des Anspruchs 1.The present invention relates to a multi-piston pump according to the preamble of claim 1.
Eine derartige Mehrkolbenpumpe ist beispielsweise aus der DE 103 53 834 Al bekannt. Derartige Mehrkolbenpumpen werden beispielsweise in Kraftfahrzeugen für den Druckaufbau in Bremssystemen verwendet. Die bekannte Mehrkolbenpumpe weist zwei Excenter auf, welche in Reihe angeordnet sind und jeweils drei Kolbenpumpen antreiben. Die Kolbenpumpen sind dabei in zwei parallelen Ebenen auf Höhe der Excenter angeordnet. Die jedem Excenter zugeordneten Kolbenpumpen sind dabei in unterschiedlichen Winkeln zueinander um den Excenter herum angeordnet. Um Druckpulsation zu verhindern, sind dabei zwei Kolbenpumpen des ersten Excenters mit einer Kolbenpumpe des zweiten Excen- ters verbunden und zwei Kolbenpumpen des zweiten Excenters mit einer Kolbenpumpe des ersten Excenters verbunden. Die Excenter sind dabei um einen Winkel von ca. 150° zueinander verdreht angeordnet. Hierbei hat sich jedoch herausgestellt, dass einerseits der Herstellungsaufwand einer derartigen Mehrkolbenpumpe sehr groß ist, da in ein gemeinsames Gehäuse eine Vielzahl von Niederdruckleitungen und Hochdruckleitungen eingebracht werden muss. Ferner ergeben sich durch die Anordnung der Kolbenpumpen ungleichförmige mechanische Kräfte auf eine Lagerung des Motors und der Excenterwelle. Ferner hat die dort vorgeschlagene Lösung den Nachteil, dass die hydraulischen Längen bei den Bohrungen des ersten und zweiten Bremskreises unterschiedlich sind, so
dass unterschiedliche Druckaufbauzeiten in der Mehrkolbenpumpe vorhanden sind.Such a multi-piston pump is known for example from DE 103 53 834 Al. Such multi-piston pumps are used for example in motor vehicles for the pressure build-up in brake systems. The known multi-piston pump has two eccentrics, which are arranged in series and each drive three piston pumps. The piston pumps are arranged in two parallel planes at the height of the eccentric. The piston pumps associated with each eccentric are arranged at different angles to one another around the eccentric. In order to prevent pressure pulsation, two piston pumps of the first eccentric are connected to a piston pump of the second excenter and two piston pumps of the second eccentric are connected to a piston pump of the first eccentric. The eccentrics are arranged rotated by an angle of about 150 ° to each other. It has been found, however, that on the one hand, the production cost of such a multi-piston pump is very large, as in a common housing a plurality of low pressure lines and high pressure lines must be introduced. Furthermore, due to the arrangement of the piston pumps non-uniform mechanical forces on a bearing of the engine and the eccentric shaft. Furthermore, the solution proposed there has the disadvantage that the hydraulic lengths in the holes of the first and second brake circuit are different, so that different pressure build-up times are present in the multi-piston pump.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Mehrkolbenpumpe mit den Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass sie eine gleichmäßige umlaufende Belastung einer Antriebswelle und der die Antriebswelle lagernden Lager sicherstellt. Hierdurch können ferner Geräusche reduziert werden und insbesondere eine pulsationsfreie Förderung erreicht werden. Darüber hinaus kann die erfindungsgemäße Mehrkolbenpumpe einfacher und kostengünstiger bereitgestellt werden. Dies wird erfindungsgemäß dadurch erreicht, dass jede Kolbenpumpe einer ersten Pumpeneinheit parallel zu einer Kolbenpumpe einer zweiten Pumpeneinheit angeordnet ist. Somit wird sichergestellt, dass die Kolbenpumpen der ersten und zweiten Pumpeneinheit gleich angeordnet sind. Dadurch wird vermieden, dass durch unterschiedliche Anordnung der Kolbenpumpen ungleichförmige mechanische Kräfte auf die Antriebswelle und die Lager ausgeübt werden. Ferner ergeben sich durch die parallele Anordnung der Kolbenpumpen der ersten und zweiten Pumpeneinheit eine reduzierte Anzahl von Richtungen, von welchen gefertigt und montiert werden muss. Darüber hinaus kann die parallele Anordnung noch sicherstellen, dass Leitungslängen der Leitungen von und zur ersten Pumpeneinheit und Leitungslängen der Leitungen von und zur zweiten Pumpeneinheit gleich lang ausgebildet werden können. Dies hat den großen Vorteil, dass dadurch gleiche Ansprechzeiten von unterschiedlichen Bremskreisen erreicht werden können, die jeweils von der ersten und zweiten Pumpeneinheit versorgt werden. Dadurch können die Bremskreise beispielsweise direkt ohne Umwege mit einem Hochdruckschaltventil in jedem Bremskreis verbunden werden.The multi-piston pump according to the invention with the features of claim 1 has the advantage that it ensures a uniform circumferential load of a drive shaft and the bearing of the drive shaft bearing. This also noise can be reduced and in particular a pulsation-free promotion can be achieved. In addition, the multi-piston pump according to the invention can be provided easier and cheaper. This is inventively achieved in that each piston pump of a first pump unit is arranged parallel to a piston pump of a second pump unit. This ensures that the piston pumps of the first and second pump units are arranged the same. This avoids that non-uniform mechanical forces are exerted on the drive shaft and the bearing by different arrangement of the piston pumps. Furthermore, the parallel arrangement of the piston pumps of the first and second pump units results in a reduced number of directions, from which it is necessary to manufacture and assemble. Moreover, the parallel arrangement can still ensure that line lengths of the lines to and from the first pump unit and line lengths of the lines from and to the second pump unit can be made the same length. This has the great advantage that this same response times can be achieved by different brake circuits, which are each supplied by the first and second pump unit. As a result, the brake circuits can be connected, for example directly without detours with a high-pressure switching valve in each brake circuit.
Die Unteransprüche zeigen weitere vorteilhafte Ausgestaltungen der erfindungsgemäßen Lösung.The subclaims show further advantageous embodiments of the solution according to the invention.
Vorzugsweise umfassen die erste und die zweite Pumpeneinheit jeweils drei Kolbenpumpen. Die Kolbenpumpen sind vorzugsweise jeweils in einem Winkel von 120° am ersten und zweiten Excenter angeordnet.
Ein weiterer Vorteil liegt darin, dass die beiden Bremskreise nun auch hydraulisch symmetrisch ausgeführt werden können, was die Herstellung weiter vereinfacht. Da die erfindungsgemäßen Mehrkolbenpumpen vorzugsweise in Fahrzeugen eingesetzt werden und daher Massenprodukte sind, ergeben sich durch die erfindungsgemäßen Parallelanordnungen der Kolbenpumpen große Einsparungspotentiale.Preferably, the first and second pump units each comprise three piston pumps. The piston pumps are preferably each arranged at an angle of 120 ° at the first and second eccentric. Another advantage is that the two brake circuits can now be performed hydraulically symmetrical, which further simplifies the production. Since the multi-piston pumps according to the invention are preferably used in vehicles and therefore are mass products, the parallel arrangements of the piston pumps according to the invention result in great savings potentials.
Weiter bevorzugt sind der erste Excenter und der zweite Excenter in einem Winkel zueinander verdreht angeordnet. Der Winkel beträgt dabei besonders bevorzugt ca. 150°.More preferably, the first eccentric and the second eccentric are arranged at an angle to each other twisted. The angle is particularly preferably about 150 °.
Um eine besonders kompakte Anordnung zu erhalten und möglichst kurze Leitungswege im Gehäuse der Mehrkolbenpumpe zu realisieren, sind die Kolbenpumpen der ersten Pumpeneinheit in einer ersten Hälfte der Mehrkolbenpumpe angeordnet und die Kolbenpumpen der zweiten Pumpeneinheit in einer zweiten Hälfte der Mehrkolbenpumpe angeordnet.In order to obtain a particularly compact arrangement and to realize the shortest possible conduit paths in the housing of the multi-piston pump, the piston pumps of the first pump unit are arranged in a first half of the multi-piston pump and the piston pumps of the second pump unit are arranged in a second half of the multi-piston pump.
Die Kolbenpumpen einer Pumpeneinheit sind besonders bevorzugt in einer Hälfte in einem Winkelbereich von ca. 120° angeordnet. Dies stellt einen sehr kompakten Aufbau bereit.The piston pumps of a pump unit are particularly preferably arranged in one half in an angular range of about 120 °. This provides a very compact structure.
Zeichnungdrawing
Nachfolgend wird die Erfindung unter Bezugnahme auf die begleitende Zeichnung im Detail beschrieben. In der Zeichnung ist:Hereinafter, the invention will be described in detail with reference to the accompanying drawings. In the drawing is:
Figur 1 eine schematische, perspektivische Ansicht einer Mehrkolbenpumpe gemäß einem Ausführungsbeispiel der Erfindung,FIG. 1 shows a schematic, perspective view of a multi-piston pump according to an exemplary embodiment of the invention,
Figur 2 eine schematische Draufsicht, welche die Anordnung der Kolbenpumpen der ersten und zweiten Pumpeneinheit verdeutlicht, und
- A -Figure 2 is a schematic plan view illustrating the arrangement of the piston pumps of the first and second pump unit, and - A -
Figur 3 eine schematische Darstellung einer Bremsanlage mit der erfindungsgemäßen Mehrkolbenpumpe.Figure 3 is a schematic representation of a brake system with the multi-piston pump according to the invention.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Nachfolgend wird unter Bezugnahme auf die Figuren 1 bis 3 eine Mehrkolbenpumpe 1 gemäß einem Ausführungsbeispiel der Erfindung beschrieben.Hereinafter, a multi-piston pump 1 according to an embodiment of the invention will be described with reference to Figures 1 to 3.
Die Mehrkolbenpumpe 1 umfasst ein Gehäuse 2, eine erste Pumpeneinheit 3 und eine zweite Pumpeneinheit 4. Die erste Pumpeneinheit 3 umfasst drei Kolbenpumpen 3a, 3b, 3c und die zweite Pumpeneinheit 4 umfasst drei Kolbenpumpen 4a, 4b, 4c. Wie insbesondere aus Figur 3 ersichtlich ist, sind jeweils drei Kolbenpumpen um einen ersten Excenter 5 und einen zweiten Excenter 6 herum angeordnet. Dabei sind dem ersten Excenter 5 zwei Kolbenpumpen 3a, 3b der ersten Pumpeneinheit 3 und eine Kolbenpumpe 4c der zweiten Pumpeneinheit 4 zugeordnet. Dem zweiten Excenter 6 ist eine Kolbenpumpe 3c der ersten Pumpeneinheit 3 und zwei Kolbenpumpen 4a, 4b der zweiten Pumpeneinheit 4 zugeordnet. Die Kolbenpumpen 3a, 3b, 3c der ersten Pumpeneinheit 3 stellen dabei den Druck in einem ersten Bremskreis I bereit und die Kolbenpumpen 4a, 4b, 4c der zweiten Pumpeneinheit 4 stellen den Druck für einen zweiten Bremskreis Il bereit. In Figur 3 ist schematisch noch ein Pedal P und ein Druckmittelbehälter D sowie vier Radbremsen VR, HL, VL und HR dargestellt. Die Bremskreisaufteilung dieses Ausführungsbeispiels ist eine X- Bremskreisaufteilung, wobei die Bremskreise I und Il in bekannter Weise noch Einlass-, Auslass-, Umschalt- und Hochdruckschaltventile aufweisen, welche nicht im Detail beschrieben werden.The multi-piston pump 1 comprises a housing 2, a first pump unit 3 and a second pump unit 4. The first pump unit 3 comprises three piston pumps 3a, 3b, 3c and the second pump unit 4 comprises three piston pumps 4a, 4b, 4c. As can be seen in particular from FIG. 3, in each case three piston pumps are arranged around a first eccentric 5 and a second eccentric 6. In this case, two piston pumps 3a, 3b of the first pump unit 3 and a piston pump 4c of the second pump unit 4 are assigned to the first eccentric 5. The second eccentric 6 is associated with a piston pump 3 c of the first pump unit 3 and two piston pumps 4 a, 4 b of the second pump unit 4. The piston pumps 3a, 3b, 3c of the first pump unit 3 thereby provide the pressure in a first brake circuit I and the piston pumps 4a, 4b, 4c of the second pump unit 4 provide the pressure for a second brake circuit II ready. In Figure 3, a pedal P and a pressure medium container D and four wheel brakes VR, HL, VL and HR is shown schematically. The brake circuit distribution of this embodiment is an X-brake circuit division, wherein the brake circuits I and II in a known manner still inlet, exhaust, changeover and high-pressure switching valves, which will not be described in detail.
Wie aus Figur 1 ersichtlich ist, sind die Kolbenpumpen 3a, 3b; 4c in einer ersten Ebene El im Gehäuse 2 angeordnet und die Kolbenpumpen 4a, 4b; 3c in einer zweiten Ebene E2 im Gehäuse 2 angeordnet. In der ersten Ebene El ist auch der erste Excenter 5 angeordnet und in der zweiten Ebene E2 der zweite Excenter 6.As can be seen from Figure 1, the piston pumps 3a, 3b; 4c arranged in a first plane El in the housing 2 and the piston pumps 4a, 4b; 3c arranged in a second plane E2 in the housing 2. The first eccentric 5 is also arranged in the first plane E1, and the second eccentric 6 is arranged in the second plane E2.
Zentral in der Mitte des Gehäuses 2 ist eine Ausnehmung 7 angeordnet, welche zur Aufnahme des ersten Excenters 5 und des zweiten Excenters 6 dient. Im Gehäuse 2 ist ferner ein erster Niederdruckspeicher 8a und ein zweiter Nieder-
druckspeicher 8b angeordnet. Von dem ersten Niederdruckspeicher 8a gehen Niederdruckleitungen zur ersten Pumpeneinheit 3 und vom zweiten Niederdruckspeicher 8b gehen Niederdruckleitungen zur zweiten Pumpeneinheit 4. Wie aus Figur 1 ersichtlich ist, sind die Niederdruckleitungen vom ersten Niederdruckspeicher 8a zu den Kolbenpumpen 3c und 3b sehr kurz. Die Niederdruckleitung zur Kolbenpumpe 3a kann ebenfalls relativ einfach durch zwei Bohrungen, die zueinander im 90°-Winkel angeordnet werden, realisiert werden. Ebenfalls können auf einfache Weise die Hochdruckleitungen der ersten und zweiten Pumpeneinheit 3, 4 ausgeführt sein. Wie in Figur 1 gezeigt, ist zwischen der Kolbenpumpe 3b und der Kolbenpumpe 3c der ersten Pumpeneinheit 3, welche parallel zueinander angeordnet sind, nur eine kurze Verbindungsbohrung zu einem Umschaltventil bzw. einem Hauptbremszylinderanschluss 9 des Bremskreises I notwendig. Von der Kolbenpumpe 3a bzw. 3b geht dann eine waagerechte/senkrechte Hochdruckleitung direkt zur Anbindung der Einlassventile im Bremskreis I. Bei der zweiten Pumpeneinheit 4 sind die Hochdruckleitungen zu einem Hauptbremszylinderanschluss des Bremskreises Il ebenfalls einfach ausgeführt. Zwischen den beiden Kolbenpumpen 4b und 4c ist ebenfalls nur eine kurze Verbindungsleitung zum Umschaltventil notwendig und von der Kolbenpumpe 4c geht eine Bohrung unmittelbar zur Anbindung der Einlassventile im Bremskreis II. Die Kolbenpumpe 4a ist über zwei im 90°- Winkel zueinander angeordnete Bohrungen ebenfalls mit den Einlassventilen im Bremskreis Il verbunden. Wie aus Figur 1 ersichtlich ist, sind die Anschlüsse 9, 10 an einem im Gehäuse 2 gebildeten Absatz angeordnet.Centrally in the middle of the housing 2, a recess 7 is arranged, which serves for receiving the first eccentric 5 and the second eccentric 6. In the housing 2, a first low-pressure accumulator 8a and a second low-pressure accumulator 8a accumulator 8b arranged. Low pressure lines go from the first low pressure accumulator 8a to the first pump unit 3 and low pressure accumulators 8b go to the second pump unit 4. As can be seen from FIG. 1, the low pressure lines from the first low pressure accumulator 8a to the piston pumps 3c and 3b are very short. The low pressure line to the piston pump 3 a can also be relatively easily realized by two holes which are arranged at 90 ° to each other. Likewise, the high-pressure lines of the first and second pump units 3, 4 can be designed in a simple manner. As shown in Figure 1, between the piston pump 3b and the piston pump 3c of the first pump unit 3, which are arranged parallel to each other, only a short connection bore to a switching valve or a master cylinder connection 9 of the brake circuit I necessary. From the piston pump 3a and 3b then goes a horizontal / vertical high pressure line directly to the connection of the intake valves in the brake circuit I. In the second pump unit 4, the high pressure lines to a master cylinder connection of the brake circuit Il are also simple. Between the two piston pumps 4b and 4c also only a short connection line to the changeover valve is necessary and from the piston pump 4c is a hole directly to the connection of the intake valves in the brake circuit II. The piston pump 4a is about two at 90 ° - to each other arranged holes also with the Inlet valves connected in the brake circuit Il. As can be seen from FIG. 1, the connections 9, 10 are arranged on a shoulder formed in the housing 2.
Die gleichen Leitungslängen für die erste und zweite Pumpeneinheit 3, 4 stellen ferner sicher, dass beim Bremsen zwischen den beiden Bremskreisen I und Il keine Verzögerung an den Radbremsen VR, HL bzw. VL, HR auftritt.The same line lengths for the first and second pump units 3, 4 also ensure that no braking occurs at the wheel brakes VR, HL or VL, HR during braking between the two brake circuits I and II.
Die den ersten und zweiten Excenter 5, 6 umfassende Excentereinheit ist in der Ausnehmung 7 angeordnet und wird von einem nicht dargestellten Elektromotor angetrieben. Der Elektromotor kann unmittelbar an das Gehäuse 2 gesetzt werden. Der erste Excenter 5 und der zweite Excenter 6 sind dabei um einen Winkel von ca. 150° verdreht zueinander angeordnet (vgl. Figur 3), wobei die Exzentrizität der beiden Excenter 5, 6 gleich gewählt ist. Durch die parallele Anordnung der Kolbenpumpen am ersten und zweiten Excenter 5, 6 wird dabei sichergestellt,
dass während des Betriebs der Mehrkolbenpumpe gleichmäßige Lastwechsel in einer Abfolge von 0o...30°...120°, 150°...240°...270° während einer Motorumdrehung (360°) erhalten werden, so dass verhindert wird, dass unregelmäßige mechanische Kräfte, insbesondere auf die Lager der Excenterwelle wirken. Hierdurch kann ein besonders vibrationsarmer und gleichmäßiger Betrieb der Mehrkolbenpumpe erreicht werden und eine Geräuschentwicklung durch schlagende Lager o. ä. ausgeschlossen werden.The eccentric unit comprising the first and second eccentrics 5, 6 is arranged in the recess 7 and is driven by an electric motor, not shown. The electric motor can be placed directly on the housing 2. The first eccentric 5 and the second eccentric 6 are arranged rotated by an angle of approximately 150 ° with respect to one another (cf., FIG. 3), wherein the eccentricity of the two eccentrics 5, 6 is chosen to be the same. The parallel arrangement of the piston pumps on the first and second eccentric 5, 6 ensures that that during operation of the multi-piston pump uniform load changes in a sequence of 0 o ... 30 ° ... 120 °, 150 ° ... 240 ° ... 270 ° during a motor revolution (360 °) are obtained, so that prevents is that irregular mechanical forces, in particular act on the bearings of the eccentric shaft. In this way, a particularly low-vibration and uniform operation of the multi-piston pump can be achieved and a noise by beating bearings o. Ä. Be excluded.
Wie aus Figur 2 ersichtlich ist, sind dabei die Kolbenpumpen 3a, 3b, 3c der ersten Pumpeneinheit in einem Winkelbereich α von 120° angeordnet. In gleicher Weise sind die Kolbenpumpen 4a, 4b, 4c der zweiten Pumpeneinheit 4 in einem Winkelbereich ß von 120° angeordnet. Die Anordnung der Kolbenpumpen ist dabei derart, dass die Kolbenpumpen 3a, 3b, 3c der ersten Pumpeneinheit 3 in einer ersten Hälfte 11 und die Kolbenpumpen 4a, 4b, 4c der zweiten Pumpeneinheit 4 in einer zweiten Hälfte 12 angeordnet sind. Die Kolbenpumpen sind in Figur 2 schematisch durch Linien dargestellt. Die Darstellung von Figur 2 macht nochmals deutlich, dass durch die erfindungsgemäße, paarweise parallele Anordnung von Kolbenpumpen am ersten und zweiten Excenter 5, 6 ein besonders kompakter Aufbau realisiert werden kann. Die Mehrkolbenpumpe 1 kann dadurch symmetrisch aufgebaut werden, so dass insbesondere auch eine hydraulische Symmetrie hinsichtlich der Leitungslängen im Gehäuse einfach verwirklicht werden kann. Dadurch ist es möglich, dass die Saugleitungsanschlüsse der Mehrkolbenpumpen direkt mit einem Hochdruckschaltventil verbunden werden können. Figur 2 macht ferner deutlich, dass die Fertigung und Montage der Mehrkolbenpumpe ebenfalls deutlicht vereinfacht werden kann, da beispielsweise die Kolbenpumpen nur in drei Richtungen montiert werden bzw. Bohrungen in das Gehäuse eingebracht werden müssen. Dadurch können auch Fertigungs- und Montagehilfen deutlicht vereinfacht werden. Ferner können die Verbindungsleitungen zwischen den einzelnen Kolbenpumpen jeder Pumpeneinheit 3, 4 besonders kurz ausgeführt werden, da die Kolbenpumpen paarweise parallel vorgesehen sind. Hierdurch reduziert sich auch ein Bohrungsaufwand im Gehäuse 2 signifikant. Die erfindungsgemäße Idee der Parallelanordnung von Kolbenpumpen verschiedener Excenter in Kombination mit der Verteilung der Kolbenpumpen einer Pumpeneinheit auf zwei Excenter 5, 6 kann ferner eine Druckpulsation während des Betriebes vermeiden, wobei die symmetrische Anordnung der Kolben-
pumpen auf den Excentern eine durch mechanische Lastwechsel verursachte Geräuschemissionen ebenfalls verhindert. Die erfindungsgemäße Mehrkolbenpumpe ist dabei zusätzlich noch besonders kostengünstig und einfach herstellbar.
As can be seen from FIG. 2, the piston pumps 3 a, 3 b, 3 c of the first pump unit are arranged in an angular range α of 120 °. In the same way, the piston pumps 4a, 4b, 4c of the second pump unit 4 are arranged in an angular range β of 120 °. The arrangement of the piston pumps is such that the piston pumps 3 a, 3 b, 3 c of the first pump unit 3 in a first half 11 and the piston pumps 4 a, 4 b, 4 c of the second pump unit 4 are arranged in a second half 12. The piston pumps are shown schematically in Figure 2 by lines. The representation of Figure 2 makes it clear again that a particularly compact design can be realized by the inventive, in pairs parallel arrangement of piston pumps on the first and second eccentric 5, 6. The multi-piston pump 1 can thereby be constructed symmetrically, so that in particular a hydraulic symmetry with respect to the cable lengths in the housing can be easily realized. This makes it possible that the Saugleitungsanschlüsse the multi-piston pumps can be connected directly to a high-pressure switching valve. Figure 2 also makes it clear that the production and assembly of the multi-piston pump can also be simplified significantly, since, for example, the piston pumps are mounted only in three directions or holes must be introduced into the housing. As a result, manufacturing and assembly aids can be significantly simplified. Furthermore, the connecting lines between the individual piston pumps of each pump unit 3, 4 can be made particularly short, since the piston pumps are provided in pairs in parallel. This also significantly reduces a drilling effort in the housing 2. The idea according to the invention of the parallel arrangement of piston pumps of different eccentrics in combination with the distribution of the piston pumps of a pump unit on two eccentrics 5, 6 can furthermore avoid pressure pulsation during operation, wherein the symmetrical arrangement of the piston Pumps on the Excentern also caused by mechanical load changes noise emissions also prevented. The multi-piston pump according to the invention is additionally particularly cost-effective and easy to produce.
Claims
1. Mehrkolbenpumpe umfassend ein Gehäuse (2), eine erste Pumpeneinheit (3) mit einer Vielzahl von Kolbenpumpen (3a, 3b, 3c) zur Druckversorgung eines ersten Druckkreises (I), eine zweite Pumpeneinheit (4) mit einer Vielzahl von Kolbenpumpen (4a, 4b, 4c) zur Druckversorgung eines zweiten Druckkreises (II), einen Antrieb und eine Excentereinheit mit einem ersten Excenter (5) und einem zweiten Excenter (6), wobei der erste und der zweite Excenter (5, 6) die Vielzahl von Kolbenpumpen (3a, 3b, 3c; 4a, 4b, 4c) antreiben, und wobei die erste und zweite Pumpeneinheit (3, 4) jeweils wenigstens eine Kolbenpumpe (3a, 3b; 4c), die vom ersten Excenter (5) antreibbar ist und eine Kolbenpumpe (3c; 4a, 4b), die vom zweiten Excenter (6) antreibbar ist, umfasst, dadurch gekennzeichnet, dass jeweils eine vom ersten Excenter (5) angetriebene Kolbenpumpe (3a, 3b; 4c) zu jeweils einer vom zweiten Excenter (6) angetriebenen Kolbenpumpe (4a, 4b; 3c) parallel angeordnet ist.1. A multi-piston pump comprising a housing (2), a first pump unit (3) with a plurality of piston pumps (3a, 3b, 3c) for pressure supply of a first pressure circuit (I), a second pump unit (4) with a plurality of piston pumps (4a , 4b, 4c) for supplying pressure to a second pressure circuit (II), a drive and an eccentric unit having a first eccentric (5) and a second eccentric (6), wherein the first and second eccentric (5, 6) the plurality of piston pumps (3a, 3b, 3c; 4a, 4b, 4c), and wherein the first and second pump units (3, 4) each have at least one piston pump (3a, 3b; 4c) drivable by the first eccentric (5) and one Piston pump (3c, 4a, 4b) which is drivable by the second eccentric (6), characterized in that in each case one of the first eccentric (5) driven piston pump (3a, 3b, 4c) to one of the second eccentric (6 ) driven piston pump (4a, 4b, 3c) is arranged in parallel.
2. Mehrkolbenpumpe nach Anspruch 1, dadurch gekennzeichnet, dass die erste und zweite Pumpeneinheit (3, 4) jeweils drei Kolbenpumpen aufweisen.2. Multi-piston pump according to claim 1, characterized in that the first and second pump unit (3, 4) each have three piston pumps.
3. Mehrkolbenpumpe nach Anspruch 2, dadurch gekennzeichnet, dass die drei dem ersten Excenter (5) zugeordnete Kolbenpumpen (3a, 3b; 4c) und die drei dem zweiten Excenter (6) zugeordneten Kolbenpumpen (4a, 4b; 3c) jeweils in einem Winkel von 120° benachbart zueinander angeordnet sind.3. A multi-piston pump according to claim 2, characterized in that the three eccentric (5) associated with the piston pumps (3a, 3b, 4c) and the three eccentric (6) associated piston pumps (4a, 4b, 3c) each at an angle of 120 ° adjacent to each other.
4. Mehrkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Excenter (5, 6) in einem Winkel zueinander verdreht angeordnet sind.4. Multi-piston pump according to one of the preceding claims, characterized in that the eccentric (5, 6) are arranged rotated at an angle to each other.
5. Mehrkolbenpumpe nach Anspruch 4, dadurch gekennzeichnet, dass der Winkel, in welchen die Excenter (5, 6) zueinander verdreht angeordnet sind, ca. 150° beträgt. 5. A multi-piston pump according to claim 4, characterized in that the angle in which the eccentric (5, 6) are arranged rotated to each other, is about 150 °.
6. Mehrkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kolbenpumpen (3a, 3b; 4c) der ersten Pumpeneinheit (3) in einer ersten Hälfte (11) der Mehrkolbenpumpe und die Kolbenpumpen (4a, 4b; 3c) der zweiten Pumpeneinheit (4) in einer zweiten Hälfte (12) der Mehrkolbenpumpe angeordnet sind.6. A multi-piston pump according to one of the preceding claims, characterized in that the piston pumps (3a, 3b; 4c) of the first pump unit (3) in a first half (11) of the multi-piston pump and the piston pumps (4a, 4b, 3c) of the second pump unit (4) are arranged in a second half (12) of the multi-piston pump.
7. Mehrkolbenpumpe nach Anspruch 6, dadurch gekennzeichnet, dass die Kolbenpumpen einer Pumpeneinheit (3, 4) in einem Winkelbereich von ca. 120° in der ersten Hälfte (11) und/oder zweiten Hälfte (12) angeordnet sind. 7. A multi-piston pump according to claim 6, characterized in that the piston pumps of a pump unit (3, 4) in an angular range of about 120 ° in the first half (11) and / or second half (12) are arranged.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US12/093,981 US20080298982A1 (en) | 2005-11-18 | 2006-10-26 | Multi-Piston Pump |
CN200680042861XA CN101310108B (en) | 2005-11-18 | 2006-10-26 | Multi-piston pump |
EP06807580A EP1952020A1 (en) | 2005-11-18 | 2006-10-26 | Multi-piston pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102005055057.6 | 2005-11-18 | ||
DE102005055057A DE102005055057A1 (en) | 2005-11-18 | 2005-11-18 | Multi-piston pump |
Publications (1)
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WO2007057285A1 true WO2007057285A1 (en) | 2007-05-24 |
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Family Applications (1)
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PCT/EP2006/067824 WO2007057285A1 (en) | 2005-11-18 | 2006-10-26 | Multi-piston pump |
Country Status (5)
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EP (1) | EP1952020A1 (en) |
CN (1) | CN101310108B (en) |
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WO (1) | WO2007057285A1 (en) |
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-
2006
- 2006-10-26 EP EP06807580A patent/EP1952020A1/en not_active Withdrawn
- 2006-10-26 WO PCT/EP2006/067824 patent/WO2007057285A1/en active Application Filing
- 2006-10-26 US US12/093,981 patent/US20080298982A1/en not_active Abandoned
- 2006-10-26 CN CN200680042861XA patent/CN101310108B/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2697403A (en) * | 1949-06-06 | 1954-12-21 | Melba L Benedek | Hydraulic pump or motor |
FR2307985A1 (en) * | 1975-04-14 | 1976-11-12 | Leduc Gerard | Hydraulic pump of eccentric design - has twin spherical eccentrics with geometrically aligned axes and sliding shoe system |
DE10353834A1 (en) * | 2003-11-18 | 2005-06-16 | Robert Bosch Gmbh | Multi-piston pump |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009053266A1 (en) * | 2007-10-19 | 2009-04-30 | Continental Teves Ag & Co. Ohg | Hydraulic unit for slip-controlled braking systems |
US8500215B2 (en) | 2007-10-19 | 2013-08-06 | Continental Teves Ag & Co. Ohg | Hydraulic unit for slip-controlled braking systems |
Also Published As
Publication number | Publication date |
---|---|
US20080298982A1 (en) | 2008-12-04 |
CN101310108B (en) | 2010-06-02 |
EP1952020A1 (en) | 2008-08-06 |
CN101310108A (en) | 2008-11-19 |
DE102005055057A1 (en) | 2007-05-24 |
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