EP0051795A1 - Coaxial double-pump - Google Patents

Coaxial double-pump Download PDF

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Publication number
EP0051795A1
EP0051795A1 EP81109055A EP81109055A EP0051795A1 EP 0051795 A1 EP0051795 A1 EP 0051795A1 EP 81109055 A EP81109055 A EP 81109055A EP 81109055 A EP81109055 A EP 81109055A EP 0051795 A1 EP0051795 A1 EP 0051795A1
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EP
European Patent Office
Prior art keywords
working cylinders
coaxial double
drum
double pump
pistons
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EP81109055A
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German (de)
French (fr)
Inventor
Karl Schlecht
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—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

Definitions

  • the invention relates to a coaxial double pump of the type described in the preamble of claim 1, as has become known, for example, from US Pat. No. 3,319,576.
  • a heavy design of such pumps can reduce the noise, but this makes the use of such pumps as mobile pumps and their use, for example, in vehicle-mounted concrete pumps impossible, in which pumps of light and small design with high speed, high performance and low lubrication sensitivity be required.
  • the invention is therefore based on the object of providing coaxial double pumps which, with a small and light design, have a high output and a low level of noise, and, because of their simple construction, enable easy replacement of the components subject to wear.
  • the opposing movement of the pistons in the working cylinders of the two drums compensates for the pressure surges acting on the fixed housing having the suction and the pressure channel, so that the housing does not vibrate like a membrane, and due to the angular displacement of the working cylinders in the two
  • the pressure surges exerted on the pressure channel are halved to a certain extent on the drums rotating around the common shaft. In this way, sound radiation, especially in the axial direction, is largely avoided. While vibrations occurring in single drives increase at higher speeds, the damping effect increases in the coaxial double pump according to the invention at higher speeds.
  • the cylinder drums 7 and 8 are mounted with teeth on the shaft 4 and have a plurality of working cylinders each with a piston 13.
  • the pistons 13 are connected via their ends which have a partial spherical shape to sliding shoes 14 which bear against the swivel plates 5 and 6.
  • the swivel plate 5 is supported on the front part of the housing 1 by way of the swivel bearing 15 designed as a vaulted roller conveyor.
  • the swivel plate 5 is pivoted by means of the servo adjusting piston 17 via the driver 18 in a known manner and thus brings about the lifting movement of the pistons 13 in the rotating mirror-image cylinder drums 7 and 8.
  • the two swivel plates 5 and 6 are mechanically or hydraulically connected to one another in a known manner coupled and designed to control the flow rate continuously swiveling.
  • the pistons 13 suck in the pressure fluid via the common suction channel 11 arranged in the more rigid housing part 3 and convey it into the common pressure channel 12. The direction of flow is indicated by the arrows 9 and 10.
  • the swivel disk 20 is mounted in the middle region of the housing 1, 2 in a swivel bearing 21 arranged in recesses in the housing and is swiveled by means of the shaft 22.
  • the suction channels 11a and 11b as well as the pressure channels 12a and 12b are arranged in the front housing parts 19a and 19b, in which the shaft 4 is mounted.
  • the suction and pressure channels are, as indicated in dashed lines, connected to a common suction line 9 or pressure line 10 forming part of a closed, prestressed circuit, or open into a suction and a pressure channel of the housing.
  • This embodiment has the advantage that the delivery rate of the pump can be changed as desired by the stepless adjustment of the inclined position of only one swivel disk.

Abstract

In this coaxial double pump, to achieve a higher performance, a simple construction making the exchange of wearing parts easier and a low generation of noise, the working cylinders, the inlets and outlets of which open into a common suction and delivery channel (11, 12), are arranged concentrically in two rotating drums (7, 8) keyed on a common shaft (4), the working cylinders of one drum being arranged preferably angularly offset relative to the working cylinders of the other drum. The pistons (13) of the working cylinders are moved by two pivoting discs (5, 6) or, in a special exemplary embodiment according to Figure 2, by only one centrally arranged pivoting disc (20), the inclination of which can be changed continuously. <IMAGE>

Description

Die Erfindung betrifft eine Koaxial-Doppelpumpe der im Oberbegriff des Patentanspruchs 1 beschriebenen Gattung, wie sie beispielsweise durch die US-PS 3 319 576 bekannt geworden ist.The invention relates to a coaxial double pump of the type described in the preamble of claim 1, as has become known, for example, from US Pat. No. 3,319,576.

Solche Pumpen mit in einem feststehenden Gehäuse angeordneten Arbeitszylindern, deren Kolben von auf einer Welle umlaufenden Taumelscheiben angetrieben werden, weisen jedoch einen komplizierten Aufbau mit nur schwierig auszubauenden, einem Verschleiß unterworfenen Einzelbauteilen, wegen der einem hohen Verschleiß ausgesetzten gleitenden Teilen nur eine verhältnismäßige niedrige Tourenzahl und damit eine nur geringe Leistung sowie eine hohe Geräuschentwicklung auf, die mit steigendem Druck und höheren Drehzahlen zunimmt.Such pumps with working cylinders arranged in a fixed housing, the pistons of which are driven by swash plates rotating on a shaft, however, have a complicated structure with difficult-to-remove, subject to wear individual components, because of the sliding parts exposed to high wear only a relatively low number of revolutions and thus only a low output and a high level of noise, which increases with increasing pressure and higher speeds.

Durch eine schwere Bauart solcher Pumpen kann die Geräuschentwicklung zwar gesenkt werden, dies macht die Verwendung solcher Pumpen jedoch als mobile Pumpen und deren Einsatz beispielsweise bei auf Fahrzeugen montierten Betonpumpen unmöglich, bei denen Pumpen leichter und kleiner Bauart mit hoher Drehzahl, hoher Leistung und geringer Schmierempfindlichkeit gefordert werden.A heavy design of such pumps can reduce the noise, but this makes the use of such pumps as mobile pumps and their use, for example, in vehicle-mounted concrete pumps impossible, in which pumps of light and small design with high speed, high performance and low lubrication sensitivity be required.

Der Erfindung liegt daher die Aufgabe zugrunde, Koaxial-Doppelpumpen zu schaffen, die bei kleiner und leichter Bauart eine hohe Leistung und eine geringe Geräuschentwicklung aufweisen, sowie aufgrund ihres einfachen konstruktiven Aufbaus ein leichtes Auswechseln von dem Verschleiß unterworfenen Bauteilen ermöglichen.The invention is therefore based on the object of providing coaxial double pumps which, with a small and light design, have a high output and a low level of noise, and, because of their simple construction, enable easy replacement of the components subject to wear.

Diese Aufgabe wird gemäß der Erfindung mit den Mitteln gelöst, die die kennzeichnenden Merkmale des Patentanspruchs 1 bzw. des Anspruchs 5 sowie vorteilhafterweise die Merkmale der Unteransprüche bilden.This object is achieved according to the invention by the means which form the characterizing features of patent claim 1 or claim 5 and advantageously the features of the subclaims.

Durch die gegenläufige Bewegung der Kolben in den Arbeitszylindern der beiden Trommeln werden die auf das feststehende, den Saug- und den Druckkanal aufweisende Gehäuse wirkenden Druckstöße kompensiert, so daß das Gehäuse nicht wie eine Membran schwingt, und durch die Winkelversetzung der Arbeitszylinder in den beiden auf der gemeinsamen Welle umlaufenden Trommeln werden die auf den Druckkanal ausgeübten Druckstöße gewissermaßen halbiert. Auf diese Weise wird eine Schallabstrahlung, insbesondere in axialer Richtung, weitgehend vermieden. Während bei Einzelantrieben auftretende Schwingungen sich bei höheren Drehzahlen verstärken, verstärkt sich bei der erfindungsgemäßen Koaxial-Doppelpumpe bei höheren Drehzahlen der Dämpfungseffekt.The opposing movement of the pistons in the working cylinders of the two drums compensates for the pressure surges acting on the fixed housing having the suction and the pressure channel, so that the housing does not vibrate like a membrane, and due to the angular displacement of the working cylinders in the two The pressure surges exerted on the pressure channel are halved to a certain extent on the drums rotating around the common shaft. In this way, sound radiation, especially in the axial direction, is largely avoided. While vibrations occurring in single drives increase at higher speeds, the damping effect increases in the coaxial double pump according to the invention at higher speeds.

Dadurch, daß die im wesentlichen axial angeordneten Arbeitszylinder nur einen geringen radialen Abstand von der Antriebswelle aufweisen, wird die Gleitreibung der mit den Kolben der Arbeitszylinder verbundenen Gleitschuhe an den Schwenkscheiben reduziert, so daß auch bei hohen Tourenzahlen die Gefahr eines Abreißens des Schmierfilms nicht besteht.The fact that the essentially axially arranged working cylinders are only a small radial distance from the drive shaft reduces the sliding friction of the sliding shoes connected to the pistons of the working cylinders on the swivel plates, so that there is no risk of the lubricating film tearing off even at high speeds.

Durch die parallele Anordnung der beiden Schwenkscheiben üben die beiden Triebwerke auf die Welle entgegengesetzt gerichtete radiale Kräfte aus, so daß sich nur eine geringe Durchbiegung der gemeinsamen Welle ergibt.Due to the parallel arrangement of the two swivel plates, the two engines exert opposite radial forces on the shaft, so that there is only a slight deflection of the common shaft.

In der Zeichnung sind zwei Ausführungsbeispiele der erfindungsgemäßen Koaxial-Doppelpumpe in schematischer Weise dargestellt, wobei zur übersichtlicheren Darstellung auf die Einzeichnung der notwendigen Steuereinrichtungen, wie z.B. Überdruckventil, Einspeise- und Auslaßventil, Servoventile zur Steuerung verzichtet wird. Es zeigen

  • Fig. 1 einen axialen Längsschnitt durch das Gehäuse einer mittels zweier Schwenkscheiben angetriebenen Pumpe;
  • Fig. 2 einen axialen Längsschnitt durch das Gehäuse einer nur mit einer Schwenkscheibe angetriebenen Pumpe.
In the drawing, two exemplary embodiments of the coaxial double pump according to the invention are shown in a schematic manner, with the necessary control devices, such as pressure relief valve, feed and outlet valve, and servo valves for control, being omitted for a clearer illustration. Show it
  • 1 shows an axial longitudinal section through the housing of a pump driven by means of two swivel plates;
  • Fig. 2 is an axial longitudinal section through the housing of a pump driven only with a swash plate.

Bei dem in Fig. 1 dargestellten Ausführungsbeispiel sind in den beiden, an das mittlere Gehäuseteil 3 angeflanschten seitlichen Gehäuseteilen 1 und 2 die mit Verzahnung auf der Welle 4 montierten Zylindertrommeln 7 und 8 angeordnet, die eine Mehrzahl von Arbeitszylindern mit je einem Kolben 13 aufweisen. Die Kolben 13 sind über deren eine Teilkugelform aufweisenden Enden mit Gleitschuhen 14 verbunden, die gegen die Schwenkscheiben 5 und 6 anliegen. Die Schwenkscheibe 5 stützt sich über das als Gewölberollenbahn ausgebildete Schwenklager 15 an dem Stirnseitenteil des Gehäuses 1 ab. Die Schwenkscheibe 5 wird mittels des Servo-Verstellkolbens 17 über den Mitnehmer 18 auf bekannte Weise verschwenkt und bewirkt so die Hubbewegung der Kolben 13 in den rotierenden spiegelbildlich ausgebildeten Zylindertrommeln 7 und 8. Die beiden Schwenkscheiben 5 und 6 sind in bekannter Weise mechanisch oder hydraulisch miteinander gekoppelt und zur Steuerung der Fördermenge stufenlos schwenkbar ausgebildet. Die Kolben 13 saugen die Druckflüssigkeit über den im rittleren Gehäuseteil 3 angeordneten gemeinsamen Saugkanal 11 an und fördern diese in den gemeinsamen Druckkanal 12. Die Strömungsrichtung ist mit den Pfeilen 9 und 10 angegeben.In the embodiment shown in FIG. 1, in the two lateral housing parts 1 and 2 flanged to the middle housing part 3, the cylinder drums 7 and 8 are mounted with teeth on the shaft 4 and have a plurality of working cylinders each with a piston 13. The pistons 13 are connected via their ends which have a partial spherical shape to sliding shoes 14 which bear against the swivel plates 5 and 6. The swivel plate 5 is supported on the front part of the housing 1 by way of the swivel bearing 15 designed as a vaulted roller conveyor. The swivel plate 5 is pivoted by means of the servo adjusting piston 17 via the driver 18 in a known manner and thus brings about the lifting movement of the pistons 13 in the rotating mirror-image cylinder drums 7 and 8. The two swivel plates 5 and 6 are mechanically or hydraulically connected to one another in a known manner coupled and designed to control the flow rate continuously swiveling. The pistons 13 suck in the pressure fluid via the common suction channel 11 arranged in the more rigid housing part 3 and convey it into the common pressure channel 12. The direction of flow is indicated by the arrows 9 and 10.

Bei dieser Ausbildung der Pumpe heben sich von den Kolbenbewegungen verursachten Schwingungen infolge der symmetrischen Anordnung der gegeneinander arbeitenden Triebwerke auf. Auch im Druckkanal können sich keine Schwingungen des ausströmenden Mediums ausbilden, da die von den einzelnen Arbeitszylindern ausgehenden Druckimpulse sich aufheben. Dieser Effekt kann durch die aus der Zeichnung ersichtliche Formgebung des Druckkanals noch unterstützt werden.With this design of the pump, vibrations caused by the piston movements cancel each other out due to the symmetrical arrangement of the mutually operating engines. Even in the pressure channel, no vibrations of the outflowing medium can develop, since those of the individual Working cylinders outgoing pressure impulses cancel each other out. This effect can be supported by the shape of the pressure channel shown in the drawing.

Bei dem in Fig. 2 dargestellten Ausführungsbeispiel ist die Schwenkscheibe 20 im mittleren Bereich des Gehäuses 1,2 in einem in Aussparungen des Gehäuses angeordneten Schwenklager 21 gelagert und wird mittels der Welle 22 verschwenkt. Die Saugkanäle lla und llb sowie die Druckkanäle 12a und 12b sind in stirnseitigen Gehäuseteilen 19a und 19b angeordnet, in denen die Welle 4 gelagert ist. Die Saug- und die Druckkanäle sind, wie in gestrichelten Linien angedeutet, an eine gemeinsame, Teile eines geschlossenen vorgespannten Kreislaufs bildende Saugleitung 9 bzw. Druckleitung 10 angeschlossen bzw. münden in einen Saug- und in einen Druckkanal des Gehäuses. Diese Ausführungsform hat den Vorteil, daß durch die stufenlose Verstellung der Schräglage nur einer Schwenkscheibe die Fördermenge der Pumpe beliebig geändert werden kann.In the exemplary embodiment shown in FIG. 2, the swivel disk 20 is mounted in the middle region of the housing 1, 2 in a swivel bearing 21 arranged in recesses in the housing and is swiveled by means of the shaft 22. The suction channels 11a and 11b as well as the pressure channels 12a and 12b are arranged in the front housing parts 19a and 19b, in which the shaft 4 is mounted. The suction and pressure channels are, as indicated in dashed lines, connected to a common suction line 9 or pressure line 10 forming part of a closed, prestressed circuit, or open into a suction and a pressure channel of the housing. This embodiment has the advantage that the delivery rate of the pump can be changed as desired by the stepless adjustment of the inclined position of only one swivel disk.

Claims (7)

l. Koaxial-Doppelpumpe mit einer Mehrzahl von konzentrisch angeordneten, in einen gemeinsamen Saug- bzw. Druckkanal mündende Ein- und Ausliisse aufweisenden Arbeitszylindern mit von einer Schrägscheibe beaufschlagten Kolben, dadurch gekennzeichnet , daß die Arbeitszylinder in zwei getrennten, auf einer gemeinsamen Welle (4) aufgekeilten Trommeln (7,8) angeordnet sind und von einer Schwenkscheibe (5,6,20) hin und her bewegte Kolben (13) aufweisen.l. Coaxial double pump with a plurality of concentrically arranged working cylinders with inlets and outlets opening into a common suction or pressure channel with pistons loaded by a swashplate, characterized in that the working cylinders are wedged into two separate ones on a common shaft (4) Drums (7, 8) are arranged and have pistons (13) moved back and forth by a swivel plate (5, 6, 20). 2. Koaxial-Doppelpumpe nach Anspruch 1, dadurch gekennzeichnet , daß die Arbeitszylinder einander gegenüberliegende Ein- und Auslässe aufweisen und die Kolben (13) der in einer Trommel (7,8) angeordneten Arbeitszylinder von je einer Schwenkscheibe (5,6) beaufschlagt werden.2. Coaxial double pump according to claim 1, characterized in that the working cylinders have mutually opposite inlets and outlets and the pistons (13) of the working cylinders arranged in a drum (7, 8) are each acted upon by a swivel plate (5, 6) . 3. Koaxial-Doppelpumpe nach Anspruch 1, dadurch gekennzeichnet , daß die Kolben (13) der in den beiden Trommeln (7,8) angeordneten Arbeitszylinder von einer gemeinsamen, mittig angeordneten Schwenkscheibe (20) beaufschlagt werden.3. Coaxial double pump according to claim 1, characterized in that the pistons (13) of the working cylinders arranged in the two drums (7, 8) are acted upon by a common, centrally arranged swivel plate (20). 4. Koaxial-Doppelpumpe nach Anspruch 1, dadurch gekennzeichnet , daß die Arbeitszylinder einer Trommel (7) gegenüber den Arbeitszylindern der anderen Trommel (8) winkelversetzt angeordnet sind.4. Coaxial double pump according to claim 1, characterized in that the working cylinders of a drum (7) with respect to the working cylinders of the other drum (8) are arranged offset in angle. 5. Koaxial-Doppelpumpe nach Anspruch 1, dadurch gekennzeichnet , daß das eine, aus der Trommel (7) und der Schwenkscheibe (5) bestehende Triebwerk gegenüber dem aus der Trommel (8) und der Schwenkscheibe (6) bestehenden Triebwerk winkelversetzt ist.5. Coaxial double pump according to claim 1, characterized in that the one consisting of the drum (7) and the swivel plate (5) existing engine relative to the existing of the drum (8) and the swivel plate (6) existing engine is angularly offset. 6. Koaxial-Doppelpumpe nach Anspruch 1, dadurch gekennzeichnet , daß die Schwenkscheiben (5,6) mechanisch oder hydraulisch miteinander gekoppelt und in ihrer Neigung gegenüber einer zur Achse der Welle (4) senkrechten Ebene stufenlos einstellbar ausgebildet sind.6. Coaxial double pump according to claim 1, characterized in that the swivel plates (5, 6) are mechanically or hydraulically coupled to one another and are infinitely adjustable in their inclination with respect to a plane perpendicular to the axis of the shaft (4). 7. Koaxial-Doppelpumpe nach Anspruch 2, dadurch gekennzeichnet , daß die Schwenkscheiben (5,6) parallel zueinander angeordnet sind.7. Coaxial double pump according to claim 2, characterized in that the swivel plates (5,6) are arranged parallel to one another.
EP81109055A 1980-11-06 1981-10-28 Coaxial double-pump Withdrawn EP0051795A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803041832 DE3041832A1 (en) 1980-11-06 1980-11-06 COAXIAL DOUBLE PUMP
DE3041832 1980-11-06

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4922804A (en) * 1987-07-23 1990-05-08 Renato Brevini Variable speed hydraulic unit
DE10021485A1 (en) * 2000-05-03 2001-11-15 Brueninghaus Hydromatik Gmbh Hydrostatic machine
FR2977644A1 (en) * 2011-07-04 2013-01-11 Peugeot Citroen Automobiles Sa Hydraulic motor for hydraulic/thermal hybrid traction chain of car, has casing defining sealed cavity, and two identical axial-piston pumps aligned on two sides of common fluid port plate and fixed in inner side of cavity
CN108869223A (en) * 2018-08-06 2018-11-23 华中科技大学 A kind of two inclined plate plunger pump
WO2020182206A1 (en) * 2019-03-13 2020-09-17 青岛科而泰控股有限公司 Tandem-type axial plunger pump
DE102021200205A1 (en) 2021-01-12 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Axial piston machine with high drive speed

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE449391B (en) * 1982-04-07 1987-04-27 Asea Atom Ab Piston pump device for pumping a mixture of coarse-grained material and liquid
DE4225380B4 (en) * 1992-07-31 2004-07-15 Linde Ag Hydrostatic unit with a main pump and a secondary pump
US5540563A (en) * 1994-09-16 1996-07-30 Sauer Inc. Unitary housing for double hydraulic unit
DE19958829C1 (en) 1999-11-30 2001-08-02 Mannesmann Ag Fuel cell system with a device for supplying fuel
JP4677614B2 (en) * 2006-05-10 2011-04-27 独立行政法人 日本原子力研究開発機構 Sulfuric acid electrolysis hydrogen production method and apparatus
JP4756118B2 (en) * 2007-02-21 2011-08-24 独立行政法人 日本原子力研究開発機構 Sulfurous acid electrolysis cell
DE102019213675A1 (en) 2019-09-10 2021-03-11 Robert Bosch Gmbh Hydrostatic piston engine unit

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653374A1 (en) * 1967-01-02 1971-10-14 Louis Berholz Pressurized fluid axial piston machine that can be operated as a pump or motor
DE1653558A1 (en) * 1967-04-19 1971-11-11 Kloeckner Werke Ag Hydrostatic axial piston machine
DE2363553A1 (en) * 1972-12-28 1974-07-04 Tokyo Keiki Kk PUMP ARRANGEMENT

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653374A1 (en) * 1967-01-02 1971-10-14 Louis Berholz Pressurized fluid axial piston machine that can be operated as a pump or motor
DE1653558A1 (en) * 1967-04-19 1971-11-11 Kloeckner Werke Ag Hydrostatic axial piston machine
DE2363553A1 (en) * 1972-12-28 1974-07-04 Tokyo Keiki Kk PUMP ARRANGEMENT

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4922804A (en) * 1987-07-23 1990-05-08 Renato Brevini Variable speed hydraulic unit
DE10021485A1 (en) * 2000-05-03 2001-11-15 Brueninghaus Hydromatik Gmbh Hydrostatic machine
US6846165B2 (en) 2000-05-03 2005-01-25 Brueninghaus Hydromatik Gmbh Hydrostatic machine
DE10021485B4 (en) * 2000-05-03 2006-03-23 Brueninghaus Hydromatik Gmbh Hydrostatic machine
FR2977644A1 (en) * 2011-07-04 2013-01-11 Peugeot Citroen Automobiles Sa Hydraulic motor for hydraulic/thermal hybrid traction chain of car, has casing defining sealed cavity, and two identical axial-piston pumps aligned on two sides of common fluid port plate and fixed in inner side of cavity
CN108869223A (en) * 2018-08-06 2018-11-23 华中科技大学 A kind of two inclined plate plunger pump
WO2020182206A1 (en) * 2019-03-13 2020-09-17 青岛科而泰控股有限公司 Tandem-type axial plunger pump
DE102021200205A1 (en) 2021-01-12 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Axial piston machine with high drive speed

Also Published As

Publication number Publication date
JPS57108477A (en) 1982-07-06
JPH0149792B2 (en) 1989-10-26
DE3041832A1 (en) 1982-05-13
JPS57114677A (en) 1982-07-16

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