WO1989006750A1 - Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur - Google Patents

Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur Download PDF

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Publication number
WO1989006750A1
WO1989006750A1 PCT/DE1989/000017 DE8900017W WO8906750A1 WO 1989006750 A1 WO1989006750 A1 WO 1989006750A1 DE 8900017 W DE8900017 W DE 8900017W WO 8906750 A1 WO8906750 A1 WO 8906750A1
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WO
WIPO (PCT)
Prior art keywords
hold
spring
ring
pressure
cylinder block
Prior art date
Application number
PCT/DE1989/000017
Other languages
German (de)
English (en)
Inventor
Michael Meyerle
Original Assignee
Michael Meyerle
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Michael Meyerle filed Critical Michael Meyerle
Priority to EP89901264A priority Critical patent/EP0357698B1/fr
Priority to DE58909319T priority patent/DE58909319D1/de
Publication of WO1989006750A1 publication Critical patent/WO1989006750A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/303—Control of machines or pumps with rotary cylinder blocks by turning the valve plate
    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means
    • 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
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure

Definitions

  • Hydrostatic axial piston machine in particular for a motor vehicle transmission with power split.
  • the invention relates to a hydrostatic axial piston machine, in particular for motor vehicle transmissions with power split according to the preamble of claim 1.
  • Hydrostatic axial piston machines of this type are widely known for their predominant use in construction machine gearboxes. These well-known hydrostatic transmissions are almost unsuitable for demanding use in gearboxes for passenger vehicles due to their unfavorable efficiency and the excessive noise level.
  • the object of the invention is to develop a hydrostatic axial piston machine, in particular for use in power split transmissions for cars or bus transmissions, in which the efficiency is improved and, moreover, the noise level is reduced.
  • Eigur 1 shows a longitudinal section of the hydrostatic axial piston machine according to the invention with positive and non-positive hold-down device and a device with spring force pressure and hydraulic pressure of the cylinder block on its valve plate.
  • Own 2a shows a partial section of a hydraulic hold-down device
  • Own 3a shows a partial section "Y" according to Eigur 3 in the installed state
  • FIG. 6 partial section of a piston for axially pressing the cylinder block onto the control surface with a special "molded sealing ring with a sealing lip
  • FIG. 8 shows an adjustable control disk according to section "Z"
  • FIG. 8 shows a longitudinal section of the hydrostatic axial piston machine according to the invention similar to FIG. 1, but with an additional hydraulic hold-down device
  • FIG. 9 shows a longitudinal section as in FIG. 8 with two internal springs for the hold-down device
  • the unfavorable hydraulic efficiency in the known hydrostatic axial piston machines is to a large extent also due to the fact that the form-fitting hold-down device is associated with a sealing problem, which is due to the fact that the sliding shoes 4 are not full enough of their counter sliding surface in all operating states Apply swash plate 11, which with the Hydrostatic circuit-related high-pressure oil of the hydrostatic sliding bearing between the sliding shoes 4 and the swash plate is lost to an increased extent, which leads to relatively high and uncontrollable leakage losses.
  • the invention has a hydraulic hold-down device 75 according to the invention, FIG.
  • the known hydrostatic axial piston machines have, for the axial pressing of the cylinder block against its control disc, depending on the embodiment, internal springs which have a sufficiently high spring force for the entire speed range.
  • the spring force depends on the maximum permissible speed and is adjusted with a correspondingly high value. This means that the spring force is unnecessarily high for lower engine speeds, which are approximately one third of the maximum engine speed in the main operating area, for example. The consequence of this is that unnecessarily high friction losses or power losses occur in the main operating area.
  • the invention provides an adaptation of the pressing forces of the cylinder block to its control disk which is specific to the operating conditions, in that the cylinder block 2 has a spring 24 with a for a low speed constant spring force and an additional variable hydraulic contact pressure is specifically pressed onto its control surface 37.
  • the variable hydraulic contact force is essentially dependent on the size of the speed of the drive motor. In special cases, it is possible to modulate or correct this pressure as a function of the hydrostatic pressure or the tensile force using a corresponding control device.
  • another annular piston 22 is provided, which is connected to the cylinder block 2 and via a fuse.
  • ring 27 is axially fixed.
  • This annular piston 22 has a sealing ring, which is expediently directed inwards to the shaft 10 and is designed as an O-ring 23 or as a shaped ring 28 with a radially elastic sealing lip 29 or as a piston ring with radial play to the groove base.
  • the sealing ring 28 is designed as a special shaped ring with an elastic sealing lip 29, which has a corresponding radial, largely free of lateral forces Allows displacement of the cylinder block 2. This also applies to the ring pistons
  • the hydraulic oil pressure is expediently supplied to the piston chamber 25 centrally through a shaft 55 or 10 via a bore 26.
  • This device causes a specifically metered pressing of the cylinder block 2 against its control surface 37 and thus an optimization of the efficiency within this functional range.
  • the hydraulic hold-down device 75 provides hydraulic pressing of the perforated disk 6 against the sliding shoes 4-.
  • this hold-down device 75 is equipped with a hold-down ring 7, which is non-rotatably but axially movable against the perforated disk 6 in the inclined body or in the swash plate 5.
  • the hold-down ring 7 is supported against a retaining ring 8 and possibly a washer 76, which serves as a one-piece washer.
  • a spring element 77 is located between the locking ring or disk 76 and the hold-down ring 7 arranged. This spring element 77 is preferably formed element or elastomer element as Gummi ⁇ , the 'nut in a ring of the retaining ring is inserted.
  • the spring element 77 acts against the hold-down ring 7 with a certain spring force.
  • the pressure oil required for generating the hydraulic contact pressure is led into the hold-down ring 7 via oil lines 79, the oil pressure against the sealing and Spring element 77 acts.
  • an axial force is exerted on the holding-down ring 7 against the perforated disk 6.
  • a specific oil pressure is generated, which is dependent, for example, on a speed signal or / and a load-dependent signal and / or a feed or supply pressure for the hydrostatic transmission and the control and regulating device.
  • the required contact forces are usually dependent on the speed.
  • a targeted contact pressure can be generated with this device via a speed-dependent pressure, which is present in this way in the automatic car transmission of this type.
  • the hold-down forces are thus relatively low in the main operating area, for example in the case of a passenger car, as a result of which the friction losses between the perforated disk 6 and the hold-down ring 7 can be substantially reduced.
  • the holding-down ring 7 has additional recesses on the sliding surface opposite the perforated disk 6, for example in the form of an annular groove 80 and a transverse groove 81, which are connected together with the hydraulic system of the hydraulic holding-down device and for lubricating the sliding surfaces between the holding-down ring 7 • and serve the perforated disc 6.
  • the amount of lubricating oil can be metered through a throttle bore 84 in the inflow to the lubrication system.
  • the sealing and spring element 77 when used in the hydraulic hold-down device 75, is expediently designed as a rubber element or elastomer element which, as shown, has one or two sealing lips projecting in the axial direction to support the axial spring force and at the same time seal tion of the hydraulic oil. A circumferential oil space is created between the two sealing lips, which ensures a uniform hydraulic pressure.
  • the hydraulic hold-down device 75 in the form shown, can be produced relatively inexpensively, since no high manufacturing accuracy of the height dimensions for the hold-down ring 7 and the perforated disk 6 is required, since even larger dimensional deviations can be compensated for by the sealing or spring element 77 .
  • a relatively simple dimension setting by means of the disk 76 which is designed as an insert disk in various thickness dimensions, can also be implemented very economically, even for very high production quantities. This also applies to the form-fitting, spring-loaded hold-down device 40 in connection with this adjusting disk 76, which is not shown in the drawings.
  • the oil feed pipe 78 for the hydraulic hold down bracket 75 is connected to 'the hold-down ring 7 and serves gleich ⁇ time to prevent rotation relative to the helical body positioned.- pivot body. 5
  • the form-fitting hold-down device 40 essentially consists of a perforated disk 6 which is held in place via the hold-down ring 7 and a locking ring 8 with little axial play "B".
  • the perforated disc 6 rotates with the cylinder block 2 and the piston 3, the holding-down ring 7 being mounted in the inclined or swiveling body 5 so as to prevent rotation.
  • protruding drivers 14, which engage in recesses 15 of the inclined body 5 serve on the holding-down ring 7.
  • the swash plate or pressure plate 11 likewise has drivers 12 which engage in recesses in the swivel body 5 for securing against rotation.
  • a spring element 9 or 46, 41 is, as shown in Figure 3, 3a, formed as an elastomer in the form that inwardly directed resilient segments 41 with the dimension "F" are connected to a closed ring 46 as possible, the engage in recesses 43 of the hold-down ring 7 and are resiliently supported against the retaining ring 8 and the hold-down ring 7.
  • These resilient sub-segments 41 have a special profile 52 which is designed such that, at a relatively high spring rate, a fairly exact axial force is generated on the hold-down ring 7 of the perforated disc 6 and the sliding shoes 4 against the slant plate or pressure plate 11 becomes.
  • the spring profile 52 is comb-shaped, the spring rate depending on the comb shape and the degree of softness of the elastomer.
  • the recesses 43 for the spring segment 41 can be cut inexpensively without cutting, for example when using the sintering or die-casting technique for the hold-down ring 7 or it can also be milled, all recesses being able to be produced very efficiently in one operation.
  • the hold-down ring 7 has a U leading edge 47 which lies in the diameter area of the inner diameter 48 for the locking ring 8 or is only slightly smaller. Since the supporting edge diameter 47 of the Niderhalteringes 7 and 48 for the locking ring 8 have almost the same diameter, it is prevented that an axial force-dependent tilting moment the locking ring 8 is prevented in order to ensure that the locking ring, which is open at one point, is securely seated in all operating situations.
  • the spring 4 is made in the form of a flat spring or from flat material and has inwardly directed spring parts 16 with projecting resilient tongues 17 which engage in recesses 19 of the hold-down ring 7 and against the hold-down ring 7 and the Support circlip 8.
  • the spring parts 16 can be connected to one another via a circumferential ring 18 and thus be formed in one piece or can be inserted loosely in the recesses 19 as separate individual members (FIGS. 4, 4a).
  • FIG. 5 and 5a show a form-fitting hold-down device with a spring element, which is designed as an elastomer in the form of an O-ring or profile ring 72 and lies in an annular groove 44 or 73 of the hold-down ring 7.
  • the profile ring 72 such as the Federelemerite 9; 6, 17 have the advantage of higher spring elasticity compared to the O-ring 45. and a lower spring force-related tilting moment on the locking ring 8 ..
  • the O-ring 45 or profile ring 72 there is also a steel spring made of flat material or. Steel wire with a cylindrical or square cross section, as not shown in the drawings, can be used. .
  • the invention provides for the cylinder block 2 to be formed with cast-in sleeves 35 and for the end face 54 of the cylinder block 2 to be conical with an angle oL which approximately corresponds to the maximum swivel angle, the piston running surface 57 with the conical end face 54 of the cylinder block 2 is flush. It is thereby achieved that a longer effective piston guidance is achieved with the same overall length of the axial piston machine compared to the prior art, whereby the lateral force-related frictional forces of the piston 3 are reduced in favor of a further improvement in efficiency.
  • the cylinder base 36 of the cylinder block 2 is also metallically connected to the cylinder block structure ' off, that is, it is cast together and consists of a special, low-friction and very resistant alloy known per se, which which has special emergency running properties.
  • This special sliding layer on the cylinder base 36 and on the piston running surface 35 can also be applied in a metal-bonding manner by other methods, for example by a spraying process.
  • control disk 31 is not. as is known, is fixedly arranged, but can be rotated automatically as a function of specific operating values.
  • the valve disk 31 is connected to an adjusting piston 32 which, depending on the speed of the drive motor or / and depending on the laser state or the hydrostatic pressure, can be rotated to a limited extent within an angular range.
  • the control disk 31 is provided with kidney-shaped recesses 38 for the two high-pressure lines and additional damping slots 34. Depending on the operating state, the control disk 31 is rotated with regard to noise optimization.
  • control disk 31 is hydrostatically supported axially on both pressure sides.
  • the control disk 31 is inexpensively designed as a sheet metal body, the kidney-shaped recesses 38 and the damping slots 34 being stamped.
  • FIG. 8 shows an axial piston machine which has a hydraulically effective hold-down device or hold-down device 71 for the piston sliding shoes 4.
  • This hold-down device 71 can be used as an alternative or in addition to the hold-down devices 40 described so far. It is characterized in that the perforated disk 68, which presses down the sliding shoes 40 of the pistons 3, is pressed axially against the sliding shoes 40 by a hydraulic force on the inside diameter.
  • This hold-down device 71 consists of a spherical cap 66 which is pressed axially with its spherical outer surface 67 onto the likewise spherical surface of a perforated disk 68.
  • the axial contact force is generated by a pressure medium in the piston chamber 70, which acts on an axially displaceable piston 64.
  • This axial force is transmitted from the annular piston 64 to the spherical cap 66 by intermediate members - preferably bolts 65 - which are loosely supported in corresponding recesses in the cylinder block 2.
  • A, preferably speed-dependent, pressure is generated in the piston chamber 25 or 70 via the oil line 26, which on one side presses the cylinder block 2 against the control surface 37 or 31, depending on the speed, in addition to the spring force of the spring 24 and on the other side Presses the perforated disk 68 against the sliding shoes 4 of the pistons 3 via the annular piston 64 and the intermediate members — bolts 65, spherical cap 66.
  • the piston ring 64 is additionally subjected to the spring force of the spring 24, the support ring 62 being omitted and the spring 24 ' and the piston 64 being adapted accordingly.
  • the spring force of the spring 24 acts with the same spring force on the cylinder block 2, and the hold-down device 71 via the calotte 66.
  • the spring 24 can be designed for a relatively low spring force in favor of lower frictional forces between the piston crown 36 and the Control surface 37 or 31 and in favor of correspondingly low frictional forces in the hold-down device 71.
  • the higher contact forces required for higher speeds are generated by the speed pressure in the piston chamber 70, 25, which is supplied via the oil line 26.
  • the contact pressure for the holding-down device 71, as well as the stabilizing force for the cylinder block 2 is automatically modulated depending on the operating speed, which means in particular that the frictional losses in all operating states are reduced to one
  • the minimum dimension is reduced, and the leakage-related losses on the slide shoes 4 and on the control surface 37 are also minimized to an optimal degree.
  • the hold-down 71 with hydraulic pressure in the various execution forms, as described and partly not shown in the drawings, can also be used very effectively as an independent hold-down device.
  • the prerequisite for this is that the calotte 66 is additionally spring-loaded, e.g. by a separate spring in the piston chamber 70 or by direct support of the spring 24 on the annular piston 64, the support ring 62 being omitted, or by a spring between the cylinder block 2 and the calotte 66.
  • the perforated disk 68 is made correspondingly thicker.
  • FIG. 9 Another embodiment shown in FIG. 9, similar to the embodiment according to FIG. 8, sees two piston surfaces of different sizes, e.g. an annular piston 64 with a small piston surface and an annular piston 22 with a large piston surface, the hydraulic pressing force of the cylinder block 2 against the control surface 37 and the hydraulic pressing force against the lower bracket 71 being of different sizes.
  • the outer diameter 69 of the annular piston 64 and its inner diameter 86 and the pressing of the cylinder block 2 in the opposite direction of the outer diameter 69 are decisive for the effective hydraulic forces for holding down the sliding shoes 4 of the inner ring piston 64 and the inner diameter 87 of the outer ring piston 22. This allows an optimal adaptation to different conditions or conditions.
  • the cylinder block 2 is rotatably connected to the drive shaft 10 and axially free.
  • one of the components - perforated disk 6, hold-down ring 7 or securing ring 8 - is designed as a dimension compensation element according to the system of a sorting method. This means that, with a view to efficient, economical assembly of the hold-down device, for example the locking ring 8, it is manufactured as a compensating member in various thicknesses with the setting dimension "E".
  • the locking ring 8 is selected with the appropriate setting dimension " ⁇ ".
  • the determination of the given dimensions "A” and “C” and the setting of the setting dimension “E” can be carried out electronically very efficiently for mass production. The. Axial play “B” is almost “zero” when new, so free of play.
  • the use of the known axial piston units is almost impossible due to their unfavorable efficiency. Even when used in a power split transmission, which only load the hydrostatic transmission with a partial output, the efficiency is often unsatisfactory.
  • the details of the invention allow a significant improvement in the overall efficiency of the hydrostatic axial piston machine despite the applicability of rational and cost-effective production methods.
  • the individual components are designed in such a way that they enable economical, modern production for mass production; this is an essential aim of the invention.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Arrangement Of Transmissions (AREA)
  • Hydraulic Motors (AREA)
  • Gear-Shifting Mechanisms (AREA)
  • Actuator (AREA)

Abstract

Un moteur hydrostatique à pistons axiaux, notamment pour boîtes de vitesses à dérivation de puissance de véhicules à moteur, comprend une fixation de préférence par crabotage (40; 75) et un dispositif stabilisateur sollicité par des ressorts (24) pour le bloc-cylindres (2). La fixation par crabotage (40; 75) comprend un accessoire hydraulique et/ou assisté par ressort de renforcement de la fixation. Le dispositif stabilisateur du bloc-cylindres (2) comprend un agencement hydraulique supplémentaire de renforcement de la stabilisation. Les forces de fixation sont automatiquement adaptées aux différentes conditions de fonctionnement et de charge afin d'améliorer le rendement. Un dispositif automatique d'ajustement de la lame de soupape (31) assure un ajustement automatique de la lame de soupape (31) en fonction de la charge ou adapté aux conditions de fonctionnement, également en vue d'améliorer le rendement et de réduire le bruit produit par le moteur.
PCT/DE1989/000017 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur WO1989006750A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP89901264A EP0357698B1 (fr) 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur
DE58909319T DE58909319D1 (de) 1988-01-16 1989-01-16 Hydrostatische axialkolbenmaschine, insbesondere für ein kraftfahrzeuggetriebe mit leistungsverzweigung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP3801144.1 1988-01-16
DE3801144 1988-01-16

Publications (1)

Publication Number Publication Date
WO1989006750A1 true WO1989006750A1 (fr) 1989-07-27

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ID=6345413

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1989/000017 WO1989006750A1 (fr) 1988-01-16 1989-01-16 Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur

Country Status (4)

Country Link
EP (1) EP0357698B1 (fr)
AT (1) ATE124498T1 (fr)
DE (1) DE58909319D1 (fr)
WO (1) WO1989006750A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0383167A1 (fr) * 1989-02-17 1990-08-22 Linde Aktiengesellschaft Moteur à pistons axiaux
DE4237506A1 (de) * 1992-11-06 1994-05-11 Danfoss As Axialkolbenmaschine
EP0856662A2 (fr) * 1997-01-31 1998-08-05 Zexel Corporation Compresseur à plateau en biais à capacité variable
EP0848162A3 (fr) * 1996-12-13 1999-12-08 Zexel Corporation Compresseur à plateau en biais à capacité variable
DE19900147C2 (de) * 1998-01-09 2002-03-07 Sauer Inc Hydraulische Einheit

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2546583A (en) * 1945-02-10 1951-03-27 Denison Eng Co Hydraulic apparatus
US3117529A (en) * 1960-01-23 1964-01-14 Council Scient Ind Res Swash plate pumps and motors
DE1226418B (de) * 1962-07-12 1966-10-06 Unipat A G Einrichtung zum Andruecken der winkelbeweglichen Kolbengleitschuhe an die Schiefscheibe oder Taumelscheibe einer Axialkolbenmaschine (Pumpe oder Motor)
DE2341106A1 (de) * 1972-11-16 1974-05-22 Abex Corp Hydraulische kraftuebertragungsvorrichtung des axialkolbentyps
DE2849772A1 (de) * 1978-11-16 1980-05-29 Linde Ag Axialkolbenmaschine in triebflanschbauform
DE2804912C2 (de) * 1977-02-14 1983-04-28 Commercial Shearing, Inc., 44501 Youngstown, Ohio Hydrostatische Axialkolbenmaschine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2546583A (en) * 1945-02-10 1951-03-27 Denison Eng Co Hydraulic apparatus
US3117529A (en) * 1960-01-23 1964-01-14 Council Scient Ind Res Swash plate pumps and motors
DE1226418B (de) * 1962-07-12 1966-10-06 Unipat A G Einrichtung zum Andruecken der winkelbeweglichen Kolbengleitschuhe an die Schiefscheibe oder Taumelscheibe einer Axialkolbenmaschine (Pumpe oder Motor)
DE2341106A1 (de) * 1972-11-16 1974-05-22 Abex Corp Hydraulische kraftuebertragungsvorrichtung des axialkolbentyps
DE2804912C2 (de) * 1977-02-14 1983-04-28 Commercial Shearing, Inc., 44501 Youngstown, Ohio Hydrostatische Axialkolbenmaschine
DE2849772A1 (de) * 1978-11-16 1980-05-29 Linde Ag Axialkolbenmaschine in triebflanschbauform

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0383167A1 (fr) * 1989-02-17 1990-08-22 Linde Aktiengesellschaft Moteur à pistons axiaux
US5079993A (en) * 1989-02-17 1992-01-14 Linde Aktiengesellschaft Axial piston machine
DE4237506A1 (de) * 1992-11-06 1994-05-11 Danfoss As Axialkolbenmaschine
EP0848162A3 (fr) * 1996-12-13 1999-12-08 Zexel Corporation Compresseur à plateau en biais à capacité variable
EP0856662A2 (fr) * 1997-01-31 1998-08-05 Zexel Corporation Compresseur à plateau en biais à capacité variable
EP0856662A3 (fr) * 1997-01-31 1999-12-08 Zexel Corporation Compresseur à plateau en biais à capacité variable
DE19900147C2 (de) * 1998-01-09 2002-03-07 Sauer Inc Hydraulische Einheit

Also Published As

Publication number Publication date
ATE124498T1 (de) 1995-07-15
EP0357698A1 (fr) 1990-03-14
DE58909319D1 (de) 1995-08-03
EP0357698B1 (fr) 1995-06-28

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