EP0853726B1 - Twin pump with a charging pump - Google Patents

Twin pump with a charging pump Download PDF

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Publication number
EP0853726B1
EP0853726B1 EP96928452A EP96928452A EP0853726B1 EP 0853726 B1 EP0853726 B1 EP 0853726B1 EP 96928452 A EP96928452 A EP 96928452A EP 96928452 A EP96928452 A EP 96928452A EP 0853726 B1 EP0853726 B1 EP 0853726B1
Authority
EP
European Patent Office
Prior art keywords
pump unit
double pump
unit according
coupling piece
piece
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96928452A
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German (de)
French (fr)
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EP0853726A1 (en
Inventor
Hermann Hoffmeister
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
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Brueninghaus Hydromatik GmbH
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Publication of EP0853726A1 publication Critical patent/EP0853726A1/en
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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
    • F04B1/20—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 rotary cylinder block
    • F04B1/22—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 rotary cylinder block having two or more sets of cylinders or pistons
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type

Definitions

  • the invention relates to a double pump unit according to the preamble of the claim 1.
  • Such a double pump unit is known from DE-OS 33 24 583.
  • the known double pump unit has two hydraulic pumps with coaxial to each other arranged drive shafts, which are non-positively connected to one another by means of a coupling piece are coupled on.
  • the coupling piece is designed in the form of a hollow shaft and by means of a spline / groove toothing with the free drive shaft ends of the two Hydraulic pumps connected.
  • the coupling piece is from a connector enclosed that the suction and pressure channels leading to the hydraulic pumps receives.
  • the double pump unit known from DE-OS 33 24 583 sucks this in conveying pressure medium directly from a low pressure line without the To subject the media to pre-compression beforehand. This is the Efficiency of the known double pump unit is limited and there is also Risk of damage due to cavitation in the intake ducts.
  • DE-PS 30 18 711 To connect a hydraulic pump to a charge pump.
  • the charge pump consists of one Turbine-like impeller, which is in a suitably trained chamber rotates.
  • the present invention has the object based on developing a hydrostatic double pump unit so that a Charge pump is integrated in a structurally simple and inexpensive manner.
  • the connector Pre-pressure chamber provided in which the intake ducts open.
  • the Coupling piece has peripherally arranged blade elements which in the Pre-pressure chamber rotate and thus the pressure medium under a pre-pressure in the Feed intake ducts.
  • the invention is based on the knowledge that the already existing and with the drive shaft rotating coupling piece as a paddle wheel for the Charge pump can be used if a corresponding pre-pressure chamber in the Connection piece is provided and the coupling piece with corresponding Bucket elements is provided. This solution requires only a minor one additional design effort and is therefore particularly inexpensive.
  • the connector can be in two parts, consisting of one Main body and a lid-like closure part closing this, formed his.
  • the coupling piece with its blade elements by a appropriately sized opening in the main body through the closure member lockable are inserted into the main body of the connector.
  • the connector according to claim 4 can also take up the intake duct and pressure duct leading to the neighboring hydraulic pump.
  • the coupling piece, including its Blade elements can be designed as a one-piece blade wheel according to claim 5.
  • the coupling piece according to claim 6 can be made as a hollow shaft and with the free ends of the drive shafts of the hydraulic pumps according to claim 7 by means of a Wedge / groove toothing must be connected.
  • the intake ducts leading to the hydraulic pumps can either be used accordingly Claim 8 open into a common suction opening in the pre-pressure chamber and in Branch the flow direction above the suction opening to the two hydraulic pumps or it can according to claim 10 for each intake duct separate intake duct openings be provided. Accordingly, the coupling piece according to claim 9 only one of its ends is formed by arranging the blade elements as a blade wheel be or it can be paddle wheel-shaped symmetrically at both ends according to claim 11 be trained.
  • Fig. 1 shows an axial section through a first embodiment of the Double pump unit developed according to the invention.
  • the double pump unit comprises two hydraulic pumps 1 and 2, which in the present embodiment as Axial piston pumps are designed and enclosed by a housing 35 and 39, respectively are.
  • the basic structure of axial piston pumps is well known, so that in the illustrated embodiment, only the cylinder drums 3, 4, Drive shafts 5, 6 and the control discs 7, 8 are shown.
  • pistons 9, 10 and 11, 12 are arranged movably and are supported on one each Swashplate, not shown.
  • the control discs 7, 8 have a kidney shape trained control channels 13, 14, which are formed in the cylinder drum 3, 4 Cylinder bores 15, 16 or 17, 18 alternately with the intake duct 19 or 20 and connect the pressure channel 21 or 22.
  • the drive shafts 5 and 6 of the two Axial piston pumps 1 and 2 are via a coupling piece to be described in more detail 23 non-positively connected.
  • One of the two drive shafts 5 or 6 is on its free end, not shown, of a likewise not shown Drive device driven so that those connected to the drive shafts 5 and 6 respectively Cylinder drums 3 and 4 are set in rotation.
  • the drive shafts 5 and 6 are still in one on rolling bearings 24 and 25 descriptive connector 26 stored.
  • the connector 26 is in illustrated embodiment of a main body 27 with an axial, preferably circular opening 28 which can be closed by a closure part 29.
  • the coupling piece 23 has, according to the invention, peripherally arranged blade elements 30, 32 on.
  • the blade elements 30, 31 are over the entire circumference of the coupling piece 23 distributed at a uniform radial distance.
  • the coupling piece 23 is therefore by the Attachment of the blade elements 30, 31 at one end as a blade wheel or turbine educated.
  • the blade elements 30, 31 extend in the manner shown in FIG. 1 Embodiment substantially perpendicular to the axis of the drive shafts 5, 6 of the Hydraulic pumps 1, 2.
  • the pressure medium to be pumped by the double pump unit flows through the funnel-shaped intake manifold 32 in the provided according to the invention Pre-pressure chamber 33, in which the hydraulic pumps 1 and 2 operate Rotate blade elements 30, 31 of coupling piece 23.
  • the blade elements 30, 31 cause a pre-compression of the print medium, so that to be promoted Pressure medium is fed into the intake ducts 19, 20 under a pre-pressure.
  • the two intake channels 19 and 20 open into one common intake port opening 34 into the pre-pressure chamber 33.
  • the intake ducts 19 and 20 each branch off one of the two hydraulic pumps 1 and 2.
  • the intake duct 20 through the Main body 27 of the connecting piece 26 is guided below the sectional plane of FIG. 1 and passed through the closure member 29 so that it is the control channels 14 of the Control disc 8 reached.
  • the pressure channel 21 of the hydraulic pump 1 is through the Main body 27 of the connector 26 guided, while the pressure channel 22 of the Hydraulic pump 2 both through the main body 27 and through the closure part 29 is passed through.
  • the direction of flow of the pressure medium is through corresponding arrows marked.
  • the closure part 29 is designed so that the Coupling piece 23 together with the blade elements 30, 31 by means of the Closure part 29 closable opening 34 in the main body 27 of the Connector 26 can be inserted axially. This facilitates the assembly of the Double pump unit considerably.
  • the assembly can be carried out in the following steps: First, the main body 27 of the connector 26 is connected to the housing 35 of the hydraulic pump 1. The coupling piece 23 with the blade elements 30, 31 is then inserted through the opening 34. It is particularly advantageous if the coupling piece 23 is designed as a hollow shaft which has a spline / groove toothing 38 on its inner diameter, which engages in a corresponding spline / groove toothing on the free end 36 of the drive shaft 5 of the hydraulic pump 1. The opening 34 in the main body 27 of the connecting piece 26 can then be closed by means of the closure part 29.
  • the second hydraulic pump 2 can subsequently be attached to the connecting piece 26, the free end 37 of the drive shaft preferably likewise having a spline / groove toothing which engages in the corresponding spline / groove toothing 38 on the inside diameter of the coupling piece 23.
  • the two-part design of the connector 26 with a one-piece Main body 27 and the closure part 29 therefore enables fluidic Favorable guidance of the intake ducts 19, 20 and quick assembly with little Construction costs.
  • the one-piece construction of the main body 27 of the connecting piece 26 offers in addition, other significant advantages. So the overall length and weight of the Double pump unit can be significantly reduced compared to known training and largely leak-free can be achieved since there are no seals to the outside required are.
  • the outside surface of the main body 27 of the connector 26 stands for the attachment of further units, e.g. the controller, setting elements or for Connection thread and the like. Available without restriction. Inside the main body 27 additional cylinder bores, oil guide bores, threads etc. can be integrated become.
  • Fig. 2 shows a further embodiment of the double pump unit according to the invention.
  • the components already described with reference to FIG. 1 are included Matching reference numerals, so that there is a related description unnecessary.
  • the suction channels 19 and 20 in separate Intake channel openings 50, 51 into the pre-pressure chamber 33.
  • the coupling piece 33 has blade elements 52, 53 and 54, 55 at both ends, which, as in the case of Embodiment according to FIG. 1 at radially uniform intervals in the manner of a Paddle wheel or a turbine are arranged circumferentially on the coupling piece 33.
  • FIG. 1 In the exemplary embodiment according to FIG.
  • each intake duct 19 or 20 is therefore a separate one blade wheel or turbine consisting of blade elements 52, 53 or 54, 55, assigned, which causes a pre-compression of the pressure medium to be conveyed and the pressure medium under a pre-pressure in the respective intake duct 19 or 20 feeds.
  • the distribution on the intake channels 19 and 20 is therefore already in the Pre-pressure chamber 33.
  • the symmetrical embodiment according to FIG. 2 has the advantage of an increased Efficiency for the loading pump consisting of the blade elements 52 to 55, so that an increased admission pressure is available in the intake ducts 19 and 20.
  • the symmetrical design of the intake channels has the advantage that the in the drawing right intake duct 20 has a shorter length, which is fluidically advantageous.
  • the invention is of course not based on the illustrated embodiments limited.
  • the blade elements 30, 31 or 52 to 55 can also be any different be constructed constructively.
  • the blade elements can form a turbine be composed parallel to the axial direction of the drive shafts 5 and 6 promotes so that the suction channels 19 and 20 largely without curvatures can be.
  • the closure part 29 can also be arranged radially in order to Inserting the coupling piece 33 into the main body 27 of the connecting piece 26 in radial direction.
  • the present invention cannot only with an axial piston pump, but also with any other known one hydrostatic pump, especially a radial piston pump, are used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention concerns a twin pump assembly comprising two hydraulic pumps (1, 2) with mutually coaxial drive shafts (5, 6) which are interconnected in force-locking manner by means of a coupling part (23). The coupling part (23) is integrated in a connection part (26) which surrounds the coupling part at least partially and contains the intake ducts (19, 20) for the intake of the pressure medium to be delivered by the hydraulic pump (1, 2). According to the invention, the connection part (26) comprises an inlet pressure chamber (33) into which the intake ducts (19, 20) open. The coupling part (33) further comprises peripheral blade elements (30, 31) which rotate in the inlet pressure chamber (33) in order to feed the pressure medium into the intake ducts (19, 20) at an initial pressure. In a development according to the invention, the connection part (26) can be in two sections and comprise adjacent a main body (27) a cover-like closure part (29) which is dimensioned such that the coupling part (23) with its blade elements (30, 31) can be introduced into the main body (27) of the connection part (26) through the opening (34) which can be closed by the closure part (29).

Description

Die Erfindung betrifft ein Doppelpumpen-Aggregat nach dem Oberbegriff des Anspruchs 1.The invention relates to a double pump unit according to the preamble of the claim 1.

Ein derartiges Doppelpumpen-Aggregat ist aus der DE-OS 33 24 583 bekannt. Das bekannte Doppelpumpen-Aggregat weist zwei Hydropumpen mit koaxial zueinander angeordneten Antriebswellen, die mittels eines Kupplungsstücks kraftschlüssig miteinander gekoppelt sind, auf. Das Kupplungsstück ist dabei in Form einer Hohlwelle ausgebildet und mittels einer Keil/Nut-Verzahnung mit den freien Antriebswellenenden der beiden Hydropumpen verbunden. Das Kupplungsstück wird von einem Verbindungsstück umschlossen, das die zu den Hydropumpen führenden Ansaugkanäle und Druckkanäle aufnimmt. Das aus der DE-OS 33 24 583 bekannte Doppelpumpen-Aggregat saugt das zu fördernde Druckmedium unmittelbar aus einer Niederdruckleitung an, ohne das Druckmedium vorher einer Vorkompression zu unterwerfen. Dadurch ist der Wirkungsgrad des bekannten Doppelpumpen-Aggregats begrenzt und zudem besteht die Gefahr einer Beschädigung durch Kavitation an den Ansaugkanälen.Such a double pump unit is known from DE-OS 33 24 583. The known double pump unit has two hydraulic pumps with coaxial to each other arranged drive shafts, which are non-positively connected to one another by means of a coupling piece are coupled on. The coupling piece is designed in the form of a hollow shaft and by means of a spline / groove toothing with the free drive shaft ends of the two Hydraulic pumps connected. The coupling piece is from a connector enclosed that the suction and pressure channels leading to the hydraulic pumps receives. The double pump unit known from DE-OS 33 24 583 sucks this in conveying pressure medium directly from a low pressure line without the To subject the media to pre-compression beforehand. This is the Efficiency of the known double pump unit is limited and there is also Risk of damage due to cavitation in the intake ducts.

Um dieser Gefahr zu begegnen, ist es andererseits aus der DE-PS 30 18 711 bekannt, einer Hydropumpe eine Ladepumpe vorzuschalten. Die Ladepumpe besteht aus einem turbinenartig ausgebildeten Laufrad, das in einer entsprechend ausgebildeten Kammer rotiert.In order to counter this danger, it is known on the other hand from DE-PS 30 18 711 to connect a hydraulic pump to a charge pump. The charge pump consists of one Turbine-like impeller, which is in a suitably trained chamber rotates.

Ausgehend von der DE-OS 33 24 583 liegt der vorliegenden Erfindung die Aufgabe zugrunde, ein hydrostatisches Doppelpumpen-Aggregat so weiterzubilden, daß eine Ladepumpe in baulich einfacher und kostengünstiger Weise integriert ist.Starting from DE-OS 33 24 583, the present invention has the object based on developing a hydrostatic double pump unit so that a Charge pump is integrated in a structurally simple and inexpensive manner.

Die Aufgabe wird durch die kennzeichnenden Merkmale des Anspuches 1 in Verbindung mit den gattungsbildenden Merkmalen gelöst.The task is connected by the characterizing features of claim 1 solved with the generic features.

Entsprechend der erfindungsgemäßen Lösung ist in dem Verbindungsstück eine Vordruckkammer vorgesehen, in welche die Ansaugkanäle einmünden. Das Kupplungsstück weist peripher angeordnete Schaufelelemente auf, die in der Vordruckkammer rotieren und somit das Druckmedium unter einem Vordruck in die Ansaugkanäle einspeisen.According to the solution according to the invention there is a in the connector Pre-pressure chamber provided in which the intake ducts open. The Coupling piece has peripherally arranged blade elements which in the Pre-pressure chamber rotate and thus the pressure medium under a pre-pressure in the Feed intake ducts.

Der Erfindung liegt dabei die Erkenntnis zugrunde, daß das ohnehin vorhandene und mit den Antriebswellen rotierende Kupplungsstück gleichzeitig als Schaufelrad für die Ladepumpe genutzt werden kann, wenn eine entsprechende Vordruckkammer in dem Verbindungsstück vorgesehen wird und das Kupplungsstück mit entsprechenden Schaufelelementen versehen wird. Diese Lösung erfordert nur einen geringfügigen zusätzlichen konstruktiven Aufwand und ist daher besonders kostengünstig.The invention is based on the knowledge that the already existing and with the drive shaft rotating coupling piece as a paddle wheel for the Charge pump can be used if a corresponding pre-pressure chamber in the Connection piece is provided and the coupling piece with corresponding Bucket elements is provided. This solution requires only a minor one additional design effort and is therefore particularly inexpensive.

Die Ansprüche 2 bis 11 beinhalten vorteilhafte Weiterbildungen der Erfindung.Claims 2 to 11 contain advantageous developments of the invention.

Das Verbindungsstück kann gemäß Anspruch 2 zweiteilig, bestehend aus einem Hauptkörper und einem diesen verschließenden deckelartigen Verschlußteil, ausgebildet sein. Dabei kann das Kupplungsstück mit seinen Schaufelelementen durch eine entsprechend bemessene Öffnung im Hauptkörper, die durch das Verschlußteil verschließbar ist, in den Hauptkörper des Verbindungsstücks eingeführt werden. Dies ermöglicht eine besonders einfache Montage und Wartung des als Schaufelrad ausgebildeten Kupplungsstücks. Dabei kann das Verbindungsstück nach Anspruch 4 auch den zu der benachbarten Hydropumpe führenden Ansaugkanal und Druckkanal aufnehmen.The connector can be in two parts, consisting of one Main body and a lid-like closure part closing this, formed his. Here, the coupling piece with its blade elements by a appropriately sized opening in the main body through the closure member lockable, are inserted into the main body of the connector. This enables particularly easy assembly and maintenance of the paddle wheel trained coupling piece. The connector according to claim 4 can also take up the intake duct and pressure duct leading to the neighboring hydraulic pump.

In besonders vorteilhafter Weise kann das Kupplungsstück einschließlich seiner Schaufelelemente als ein einteiliges Schaufelrad nach Anspruch 5 ausgebildet sein.In a particularly advantageous manner, the coupling piece, including its Blade elements can be designed as a one-piece blade wheel according to claim 5.

Ferner kann das Kupplungsstück nach Anspruch 6 als Hohlwelle gefertigt sein und mit den freien Enden der Antriebswellen der Hydropumpen entsprechend Anspruch 7 mittels einer Keil/Nut-Verzahnung verbunden sein.Furthermore, the coupling piece according to claim 6 can be made as a hollow shaft and with the free ends of the drive shafts of the hydraulic pumps according to claim 7 by means of a Wedge / groove toothing must be connected.

Die zu den Hydropumpen führenden Ansaugkanäle können entweder entsprechend Anspruch 8 in einer gemeinsamen Ansaugöffnung in die Vordruckkammer münden und in Flußrichtung oberhalb der Ansaugöffnung zu den beiden Hydropumpen verzweigen oder es können nach Anspruch 10 für jeden Ansaugkanal getrennte Ansaugkanalöffnungen vorgesehen sein. Entsprechend kann das Kupplungsstück nach Anspruch 9 lediglich an einem seiner Enden durch Anordnung der Schaufelelemente als Schaufelrad ausgeformt sein oder es kann nach Anspruch 11 symmetrisch an beiden Enden schaufelradförmig ausgebildet sein.The intake ducts leading to the hydraulic pumps can either be used accordingly Claim 8 open into a common suction opening in the pre-pressure chamber and in Branch the flow direction above the suction opening to the two hydraulic pumps or it can according to claim 10 for each intake duct separate intake duct openings be provided. Accordingly, the coupling piece according to claim 9 only one of its ends is formed by arranging the blade elements as a blade wheel be or it can be paddle wheel-shaped symmetrically at both ends according to claim 11 be trained.

Die Erfindung wird nachfolgend anhand der Zeichnung näher beschrieben. Dabei zeigen:

Fig. 1
einen Schnitt durch ein erstesAusführungsbeispiel der Erfindung;
Fig. 2
einen Schnitt durch ein zweites Ausführungsbeispiel der Erfindung.
The invention is described below with reference to the drawing. Show:
Fig. 1
a section through a first embodiment of the invention;
Fig. 2
a section through a second embodiment of the invention.

Fig. 1 zeigt einen axialen Schnitt durch ein erstes Ausführungsbeispiel des erfindungsgemäß weitergebildeten Doppelpumpen-Aggregats. Das Doppelpumpen-Aggregat umfaßt zwei Hydropumpen 1 und 2, die im vorliegenden Ausführungsbeispiel als Axialkolbenpumpen ausgeführt sind und von je einem Gehäuse 35 bzw. 39 umschlossen sind. Der grundsätzliche Aufbau von Axialkolbenpumpen ist hinlänglich bekannt, so daß im dargestellten Ausführungsbeispiel lediglich die Zylindertrommeln 3, 4, die Antriebswellen 5, 6 und die Steuerscheiben 7, 8 dargestellt sind. In den Zylindertrommeln 3, 4 sind Kolben 9, 10 bzw. 11, 12 beweglich angeordnet und stützen sich an jeweils einer nicht dargestellten Schrägscheibe ab. Die Steuerscheiben 7, 8 weisen nierenförmig ausgebildete Steuerkanäle 13, 14 auf, die die in der Zylindertrommel 3, 4 ausgebildeten Zylinderbohrungen 15, 16 bzw. 17, 18 wechselseitig mit dem Ansaugkanal 19 bzw. 20 und dem Druckkanal 21 bzw. 22 verbinden. Die Antriebswellen 5 und 6 der beiden Axialkolbenpumpen 1 und 2 sind über ein noch näher zu beschreibendes Kupplungsstück 23 kraftschlüssig miteinander verbunden. Eine der beiden Antriebswellen 5 oder 6 wird an ihrem nicht dargestellten freien Ende von einer ebenfalls nicht dargestellten Antriebseinrichtung angetrieben, so daß die mit den Antriebswellen 5 bzw. 6 verbundenen Zylindertrommeln 3 bzw. 4 in Rotation versetzt werden.Fig. 1 shows an axial section through a first embodiment of the Double pump unit developed according to the invention. The double pump unit comprises two hydraulic pumps 1 and 2, which in the present embodiment as Axial piston pumps are designed and enclosed by a housing 35 and 39, respectively are. The basic structure of axial piston pumps is well known, so that in the illustrated embodiment, only the cylinder drums 3, 4, Drive shafts 5, 6 and the control discs 7, 8 are shown. In the cylinder drums 3, 4 pistons 9, 10 and 11, 12 are arranged movably and are supported on one each Swashplate, not shown. The control discs 7, 8 have a kidney shape trained control channels 13, 14, which are formed in the cylinder drum 3, 4 Cylinder bores 15, 16 or 17, 18 alternately with the intake duct 19 or 20 and connect the pressure channel 21 or 22. The drive shafts 5 and 6 of the two Axial piston pumps 1 and 2 are via a coupling piece to be described in more detail 23 non-positively connected. One of the two drive shafts 5 or 6 is on its free end, not shown, of a likewise not shown Drive device driven so that those connected to the drive shafts 5 and 6 respectively Cylinder drums 3 and 4 are set in rotation.

Die Antriebswellen 5 und 6 sind in Wälzlagern 24 und 25 an einem noch zu beschreibenden Verbindungsstück 26 gelagert. Das Verbindungsstück 26 besteht im dargestellten Ausführungsbeispiel aus einem Hauptkörper 27 mit einer axialen, vorzugsweise kreisförmigen Öffnung 28, die durch ein Verschlußteil 29 verschließbar ist.The drive shafts 5 and 6 are still in one on rolling bearings 24 and 25 descriptive connector 26 stored. The connector 26 is in illustrated embodiment of a main body 27 with an axial, preferably circular opening 28 which can be closed by a closure part 29.

Das Kupplungsstück 23 weist erfindungsgemäß peripher angeordnete Schaufelelemente 30, 32 auf. Die Schaufelelemente 30, 31 sind über den gesamten Umfang des Kupplungsstücks 23 in gleichmäßigem radialen Abstand verteilt. Das Kupplungsstück 23 ist daher durch die Anbringung der Schaufelelemente 30, 31 an einem Ende als Schaufelrad bzw. Turbine ausgebildet. Die Schaufelelemente 30, 31 erstrecken sich dabei im in Figur 1 dargestellten Ausführungsbeispiel im wesentlichen senkrecht zur Achse der Antriebswellen 5, 6 der Hydropumpen 1, 2.The coupling piece 23 has, according to the invention, peripherally arranged blade elements 30, 32 on. The blade elements 30, 31 are over the entire circumference of the coupling piece 23 distributed at a uniform radial distance. The coupling piece 23 is therefore by the Attachment of the blade elements 30, 31 at one end as a blade wheel or turbine educated. The blade elements 30, 31 extend in the manner shown in FIG. 1 Embodiment substantially perpendicular to the axis of the drive shafts 5, 6 of the Hydraulic pumps 1, 2.

Das von dem Doppelpumpen-Aggregat zu fördernde Druckmedium fließt über den trichterförmig ausgebildeten Ansaugstutzen 32 in die erfindungsgemäß vorgesehene Vordruckkammer 33, in der während des Betriebs der Hydropumpen 1 und 2 die Schaufelelemente 30, 31 des Kupplungsstücks 23 rotieren. Die Schaufelelemente 30, 31 bewirken dabei eine Vorkompression des Druckmediums, so daß das zu fördernde Druckmedium unter einem Vordruck in die Ansaugkanäle 19, 20 eingespeist wird. Durch den Vordruck in den Ansaugkanälen 19 und 20 wird der Wirkungsgrad der Hydropumpen 1 und 2 erhöht und gleichzeitig wird die Gefahr von Kavitationsschäden im Bereich der Ansaugkanäle 19, 20 oder der Steuerkanäle 13, 14 vermieden.The pressure medium to be pumped by the double pump unit flows through the funnel-shaped intake manifold 32 in the provided according to the invention Pre-pressure chamber 33, in which the hydraulic pumps 1 and 2 operate Rotate blade elements 30, 31 of coupling piece 23. The blade elements 30, 31 cause a pre-compression of the print medium, so that to be promoted Pressure medium is fed into the intake ducts 19, 20 under a pre-pressure. By the admission pressure in the intake channels 19 and 20 becomes the efficiency of the hydraulic pumps 1 and 2 increases and at the same time the risk of cavitation damage in the area of Intake channels 19, 20 or the control channels 13, 14 avoided.

Im Ausführungsbeispiel nach Fig. 1 münden die beiden Ansaugkanäle 19 und 20 in einer gemeinsamen Ansaugkanalöffnung 34 in die Vordruckkammer 33 ein. In Flußrichtung oberhalb der Ansaugkanalöffnung 34 verzweigen die Ansaugkanäle 19 und 20 jeweils zu einer der beiden Hydropumpen 1 und 2. Dabei wird der Ansaugkanal 20 durch den Hauptkörper 27 des Verbindungsstücks 26 unterhalb der Schnittebene der Fig. 1 geführt und durch das Verschlußteil 29 so hindurchgeführt, daß es die Steuerkanäle 14 der Steuerscheibe 8 erreicht. Abflußseitig ist der Druckkanal 21 der Hydropumpe 1 durch den Hauptkörper 27 des Verbindungsstücks 26 geführt, während der Druckkanal 22 der Hydropumpe 2 sowohl durch den Hauptkörper 27 als auch durch das Verschlußteil 29 hindurchgeführt ist. Zur Verdeutlichung ist die Flußrichtung des Druckmittels durch entsprechende Pfeile gekennzeichnet.In the embodiment of FIG. 1, the two intake channels 19 and 20 open into one common intake port opening 34 into the pre-pressure chamber 33. In the direction of the river Above the intake duct opening 34, the intake ducts 19 and 20 each branch off one of the two hydraulic pumps 1 and 2. In this case, the intake duct 20 through the Main body 27 of the connecting piece 26 is guided below the sectional plane of FIG. 1 and passed through the closure member 29 so that it is the control channels 14 of the Control disc 8 reached. On the discharge side, the pressure channel 21 of the hydraulic pump 1 is through the Main body 27 of the connector 26 guided, while the pressure channel 22 of the Hydraulic pump 2 both through the main body 27 and through the closure part 29 is passed through. For the sake of clarity, the direction of flow of the pressure medium is through corresponding arrows marked.

Im Ausführungsbeispiel nach Fig. 1 ist das Verschlußteil 29 so ausgebildet, daß das Kupplungsstück 23 mitsamt den Schaufelelementen 30, 31 durch die mittels des Verschlußteils 29 verschließbare Öffnung 34 in den Hauptkörper 27 des Verbindungsstücks 26 axial eingeführt werden kann. Dies erleichtert die Montage des Doppelpumpen-Aggregats erheblich.In the embodiment of FIG. 1, the closure part 29 is designed so that the Coupling piece 23 together with the blade elements 30, 31 by means of the Closure part 29 closable opening 34 in the main body 27 of the Connector 26 can be inserted axially. This facilitates the assembly of the Double pump unit considerably.

Die Montage kann dabei in folgenden Schritten erfolgen:
Zunächst wird der Hauptkörper 27 des Verbindungsstücks 26 mit dem Gehäuse 35 der Hydropumpe 1 verbunden. Sodann wird das Kupplungsstück 23 mit den Schaufelelementen 30,31 durch die Öffnung 34 eingeschoben. Dabei ist es besonders vorteilhaft, wenn das Kupplungsstück 23 als Hohlwelle ausgebildet ist, die an ihrem Innendurchmesser eine Keil/Nut-Verzahnung 38 aufweist, die in eine entsprechende Keil/Nut-Verzahnung am freien Ende 36 der Antriebswelle 5 der Hydropumpe 1 eingreift. Sodann kann mittels des Verschlußteils 29 die Öffnung 34 im Hauptkörper 27 des Verbindungsstücks 26 verschlossen werden. Nachfolgnd kann die zweite Hydropumpe 2 an das Verbindungsstück 26 angefügt werden, wobei vorzugsweise das freie Ende 37 der Antriebswelle ebenfalls eine Keil/Nut-Verzahnung aufweist, die in die entsprechende Keil/Nut-Verzahnung 38 am Innendurchmesser des Kupplungsstücks 23 eingreift.The assembly can be carried out in the following steps:
First, the main body 27 of the connector 26 is connected to the housing 35 of the hydraulic pump 1. The coupling piece 23 with the blade elements 30, 31 is then inserted through the opening 34. It is particularly advantageous if the coupling piece 23 is designed as a hollow shaft which has a spline / groove toothing 38 on its inner diameter, which engages in a corresponding spline / groove toothing on the free end 36 of the drive shaft 5 of the hydraulic pump 1. The opening 34 in the main body 27 of the connecting piece 26 can then be closed by means of the closure part 29. The second hydraulic pump 2 can subsequently be attached to the connecting piece 26, the free end 37 of the drive shaft preferably likewise having a spline / groove toothing which engages in the corresponding spline / groove toothing 38 on the inside diameter of the coupling piece 23.

Die zweiteilige Ausbildung des Verbindungsstücks 26 mit einem einteilig gefertigten Hauptkörper 27 und dem Verschlußteil 29 ermöglicht daher eine strömungstechnisch günstige Führung der Ansaugkanäle 19, 20 und eine schnelle Montage bei geringem Konstruktionsaufwand. Durch die Weiterbildung des Kupplungsstücks 23 mit den schaufelartigen Elementen 30, 31 wird eine wirkungsvolle Ladepumpe erzielt.The two-part design of the connector 26 with a one-piece Main body 27 and the closure part 29 therefore enables fluidic Favorable guidance of the intake ducts 19, 20 and quick assembly with little Construction costs. By developing the coupling piece 23 with the vane-like elements 30, 31 an effective charge pump is achieved.

Die einteilige Bauweise des Hauptkörpers 27 des Verbindungsstücks 26 bietet darüberhinaus weitere wesentliche Vorteile. So kann die Baulänge und das Gewicht des Doppelpumpen-Aggregats gegenüber bekannten Ausbildungen erheblich reduziert werden und eine weitgehende Leckfreiheit erreicht werden, da keine Abdichtungen nach außen erforderlich sind. Die außenseitige Oberfläche des Hauptkörpers 27 des Verbindungsstücks 26 steht für den Anbau weiterer Aggregate, z.B. der Regler, Einstellelemente oder für Anschlußgewinde und dgl. uneingeschränkt zur Verfügung. Innerhalb des Hauptkörpers 27 können weitere Zylinderbohrungen, Ölführungsbohrungen, Gewinde usw. integriert werden.The one-piece construction of the main body 27 of the connecting piece 26 offers in addition, other significant advantages. So the overall length and weight of the Double pump unit can be significantly reduced compared to known training and largely leak-free can be achieved since there are no seals to the outside required are. The outside surface of the main body 27 of the connector 26 stands for the attachment of further units, e.g. the controller, setting elements or for Connection thread and the like. Available without restriction. Inside the main body 27 additional cylinder bores, oil guide bores, threads etc. can be integrated become.

Fig. 2 zeigt ein weiteres Ausführungsbeispiel des erfindungsgemäßen Doppelpumpen-Aggregats. Die bereits in Bezug auf Fig. 1 beschriebenen Komponenten sind mit übereinstimmenden Bezugszeichen versehen, so daß sich eine diesbezügliche Beschreibung erübrigt.Fig. 2 shows a further embodiment of the double pump unit according to the invention. The components already described with reference to FIG. 1 are included Matching reference numerals, so that there is a related description unnecessary.

In Abweichung zu dem Ausführungsbeispiel nach Fig. 1 münden bei dem Ausführungsbeispiel nach Fig. 2 die Ansaugkanäle 19 und 20 in getrennten Ansaugkanalöffnungen 50, 51 in die Vordruckkammer 33 ein. Das Kupplungsstück 33 weist an beiden Enden jeweils Schaufelelemente 52, 53 bzw. 54, 55 auf, die wie beim Ausführungsbeispiel nach Fig. 1 in radial gleichmäßigen Abständen in der Art eines Schaufelrades bzw. einer Turbine umfänglich an dem Kupplungsstück 33 angeordnet sind. Im Ausführungsbeispiel nach Fig. 2 ist daher jedem Ansaugkanal 19 bzw. 20 ein separates aus den Schaufelelementen 52, 53 bzw. 54, 55 bestehendes Schaufelrad, bzw. Turbine, zugeordnet, das jeweils eine Vorkompression des zu fördernden Druckmediums bewirkt und das Druckmedium unter einem Vordruck in den jeweiligen Ansaugkanal 19 bzw. 20 einspeist. Die Verteilung auf die Ansaugkanäle 19 und 20 erfolgt daher bereits in der Vordruckkammer 33.In deviation from the embodiment of FIG. 1 lead to the Embodiment of FIG. 2, the suction channels 19 and 20 in separate Intake channel openings 50, 51 into the pre-pressure chamber 33. The coupling piece 33 has blade elements 52, 53 and 54, 55 at both ends, which, as in the case of Embodiment according to FIG. 1 at radially uniform intervals in the manner of a Paddle wheel or a turbine are arranged circumferentially on the coupling piece 33. In the exemplary embodiment according to FIG. 2, each intake duct 19 or 20 is therefore a separate one blade wheel or turbine consisting of blade elements 52, 53 or 54, 55, assigned, which causes a pre-compression of the pressure medium to be conveyed and the pressure medium under a pre-pressure in the respective intake duct 19 or 20 feeds. The distribution on the intake channels 19 and 20 is therefore already in the Pre-pressure chamber 33.

Die symmetrische Ausführungsform nach Fig. 2 weist den Vorteil eines erhöhten Wirkungsgrades für die aus den Schaufelelementen 52 bis 55 bestehende Ladepumpe auf, so daß in den Ansaugkanälen 19 und 20 ein erhöhter Vordruck zur Verfügung steht. Darüberhinaus bietet die symmetrische Ausbildung der Ansaugkanäle den Vorteil, daß der in der Zeichnung rechte Ansaugkanal 20 eine geringere Länge aufweist, was strömungstechnisch von Vorteil ist. The symmetrical embodiment according to FIG. 2 has the advantage of an increased Efficiency for the loading pump consisting of the blade elements 52 to 55, so that an increased admission pressure is available in the intake ducts 19 and 20. In addition, the symmetrical design of the intake channels has the advantage that the in the drawing right intake duct 20 has a shorter length, which is fluidically advantageous.

Die Erfindung ist selbstverständlich nicht auf die dargestellten Ausführungsbeispiele beschränkt. So können die Schaufelelemente 30, 31 bzw. 52 bis 55 auch beliebig anders konstruktiv ausgebildet sein. Insbesondere können die Schaufelelemente zu einer Turbine zusammengesetzt sein, die parallel zur axialen Richtung der Antriebswellen 5 und 6 fördert, so daß die Ansaugkanäle 19 und 20 weitgehend ohne Krümmungen ausgeführt werden können. Ferner kann das Verschlußteil 29 auch radial angeordnet sein, um das Einühren des Kupplungsstücks 33 in den Hauptkörper 27 des Verbindungsstücks 26 in radialer Richtung zu ermöglichen. Selbstverständlich kann die vorliegende Erfindung nicht nur bei einer Axialkolbenpumpe, sondern auch bei jeder anderen bekannten hydrostatischen Pumpe, insbesondere einer Radialkolbenpumpe, Verwendung finden.The invention is of course not based on the illustrated embodiments limited. The blade elements 30, 31 or 52 to 55 can also be any different be constructed constructively. In particular, the blade elements can form a turbine be composed parallel to the axial direction of the drive shafts 5 and 6 promotes so that the suction channels 19 and 20 largely without curvatures can be. Furthermore, the closure part 29 can also be arranged radially in order to Inserting the coupling piece 33 into the main body 27 of the connecting piece 26 in radial direction. Of course, the present invention cannot only with an axial piston pump, but also with any other known one hydrostatic pump, especially a radial piston pump, are used.

Claims (11)

  1. Double pump unit having
    two hydraulic pumps (1, 2) having drive shafts (5, 6) arranged coaxially with one another, which shafts are coupled with one another in a force-locking manner by means of a coupling piece (23), and having a connection piece (26) at least partially surrounding the coupling piece (23), in which connection piece suction channels (19, 20) for drawing in the pressure medium to be delivered through the hydraulic pumps (1, 2) are formed,
    characterised in that,
    the connection piece (26) has an inlet pressure chamber (33) into which the suction channels (19, 20) open, and in that the coupling piece (23) has peripherally arranged blade elements (30, 31; 52-55) which rotate in the inlet pressure chamber (33) in order to feed the pressure medium into the suction channels (19, 20) under an initial pressure.
  2. Double pump unit according to claim 1,
    characterised in that,
    the connection piece (26) is formed in two parts and, along with a main body (27) has a lid-like closure part (29) which is so formed that the coupling piece (23), with its blade elements (30, 31; 52-55), can be introduced into the main body (27) of the connection piece (26) through an opening (34) which can be closed by means of the closure piece (29) .
  3. Double pump unit according to claim 1 or 2,
    characterised in that,
    the connection piece (26) further has pressure channels (21, 22) for the discharge of the pressure medium.
  4. Double pump unit according to claim 2 or claim 3 when read as dependent upon claim 2,
    characterised in that,
    the suction channel (20) and/or the pressure channel (22) of one of the two hydraulic pumps (2) is led through the closure part (29).
  5. Double pump unit according to any of claims 1 to 4,
    characterised in that,
    the coupling piece (23), including its blade elements (30, 31; 52-55), is formed in one piece.
  6. Double pump unit according to any of claims 1 to 5,
    characterised in that,
    the coupling piece (23) is formed as a hollow shaft, which surrounds the ends of the drive shafts (5, 6) of the hydraulic pumps (1, 2) in the manner of a sleeve.
  7. Double pump unit according to claim 6,
    characterised in that,
    the coupling piece (23) is connected with the drive shafts (5, 6) of the hydraulic pumps (1, 2) by means of a spline/groove toothing (38).
  8. Double pump unit according to any of claims 1 to 7,
    characterised in that,
    the suction channels (19, 20) leading each to one of the two hydraulic pumps (1, 2) open into a common suction channel opening (34) in the initial pressure chamber (33) and branch off above, in the direction of flow, the suction channel opening (34).
  9. Double pump unit according to claim 8,
    characterised in that,
    the blade elements (30, 31) are provided at one end of the coupling piece (23) in the region of the suction channel opening (34).
  10. Double pump unit according to any of claims 1 to 7,
    characterised in that,
    the suction channels (19, 20) leading each to one of the two hydraulic pumps (1, 2) open into separate suction channel openings (50, 51) in the initial pressure chamber (33) .
  11. Double pump unit according to claim 10,
    characterised in that,
    the blade elements (52-55) are provided at both ends of the coupling piece (23), in each case in the region of a suction channel opening (50, 51).
EP96928452A 1995-10-04 1996-08-12 Twin pump with a charging pump Expired - Lifetime EP0853726B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19536997 1995-10-04
DE19536997A DE19536997C1 (en) 1995-10-04 1995-10-04 Double pump with charge pump
PCT/EP1996/003562 WO1997013065A1 (en) 1995-10-04 1996-08-12 Twin pump with a charging pump

Publications (2)

Publication Number Publication Date
EP0853726A1 EP0853726A1 (en) 1998-07-22
EP0853726B1 true EP0853726B1 (en) 2003-11-19

Family

ID=7774026

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96928452A Expired - Lifetime EP0853726B1 (en) 1995-10-04 1996-08-12 Twin pump with a charging pump

Country Status (5)

Country Link
US (1) US6022198A (en)
EP (1) EP0853726B1 (en)
JP (1) JP3736643B2 (en)
DE (2) DE19536997C1 (en)
WO (1) WO1997013065A1 (en)

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Also Published As

Publication number Publication date
JP3736643B2 (en) 2006-01-18
US6022198A (en) 2000-02-08
JPH11512800A (en) 1999-11-02
EP0853726A1 (en) 1998-07-22
WO1997013065A1 (en) 1997-04-10
DE19536997C1 (en) 1997-02-20
DE59610826D1 (en) 2003-12-24

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