EP0205982A2 - Machine à pistons axiaux avec une plaque oscillante entre lesquels est disposée une articulation homocinétique - Google Patents

Machine à pistons axiaux avec une plaque oscillante entre lesquels est disposée une articulation homocinétique Download PDF

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Publication number
EP0205982A2
EP0205982A2 EP86107345A EP86107345A EP0205982A2 EP 0205982 A2 EP0205982 A2 EP 0205982A2 EP 86107345 A EP86107345 A EP 86107345A EP 86107345 A EP86107345 A EP 86107345A EP 0205982 A2 EP0205982 A2 EP 0205982A2
Authority
EP
European Patent Office
Prior art keywords
cylinder drum
joint
piston machine
axial piston
pin
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.)
Granted
Application number
EP86107345A
Other languages
German (de)
English (en)
Other versions
EP0205982B1 (fr
EP0205982A3 (en
Inventor
Ludwig Wagenseil
Reinhold Schniederjan
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.)
Hydromatik GmbH
Original Assignee
Hydromatik GmbH
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 Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0205982A2 publication Critical patent/EP0205982A2/fr
Publication of EP0205982A3 publication Critical patent/EP0205982A3/de
Application granted granted Critical
Publication of EP0205982B1 publication Critical patent/EP0205982B1/fr
Expired legal-status Critical Current

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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
    • F04B1/2092—Means for connecting rotating cylinder barrels and rotating inclined swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/10—Control of working-fluid admission or discharge peculiar thereto
    • F01B3/103—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block
    • F01B3/106—Control of working-fluid admission or discharge peculiar thereto for machines with rotary cylinder block by changing the inclination of the swash plate

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the outer part is attached to the cylinder drum and the inner part is connected to the drive pulley by an auxiliary cardan joint.
  • the auxiliary cardan joint allows both an axial and a radial adjustment of the inner part, whereby constraints due to unavoidable tolerances are avoided.
  • the outside and inside curvature of the cage corresponds to the curvatures of the inner surface of the outer part and the outer surface of the inner part, so that during the operation of the axial piston machine, the transmission of slight axial forces in the region of the joint would be possible, but this is not possible with the known design, because the inner part is not axially and radially supported in a defined manner.
  • the invention has for its object to design an axial piston machine of the type described above with simple means so that axial and radial support of the cylinder drum on the drive pulley is possible while avoiding malfunctions.
  • the recess in the drive pulley is used for the axial and radial mounting of the joint.
  • the cylindrical drum-side joint part is directly supported by the spherical outer surface resting on the cylinder drum-side joint part on the spherical inner surface of the recess. Therefore, the cage can be released from the transmission of axial or radial forces.
  • the configuration according to the invention not only comprises a simple and small construction, but also enables large angular differences, namely up to approximately 40 °, between the axis of rotation of the drive pulley and the axis of rotation of the cylinder drum.
  • the embodiment according to the invention is not only suitable for axial piston machines with a constant delivery or swallowing volume, but in particular also for axial piston machines with variable delivery or swallowing volumes.
  • Another advantage is that a joint with the features according to the invention fits for axial piston machines with different helix angles and can therefore be used both for axial piston machines with constant delivery or displacement volumes and different helix angles as well as for axial piston machines with variable delivery or absorption volumes.
  • the configuration according to the invention is also suitable with the simultaneous arrangement of an auxiliary cardan joint, as is present in the known embodiment, because the known auxiliary cardan joint with its adaptable arrangement of the drive disk-side joint part is harmless due to the direct support of the cylinder drum-side joint part on the drive flange or attachments thereof.
  • the embodiment according to claim 2 leads on the one hand to a simpler embodiment because the outer part is integrated into the drive pulley. It is possible both to form the spherical inner surface on the drive pulley and to insert a separate component with a spherical inner surface on or in the drive pulley. On the other hand, this configuration also leads to a reduction in the size, because there is no space for a separate component, namely a ring bearing the spherical inner surface.
  • the cage of the joint has a spherical inner and outer surface, and is, so to speak, mounted in addition to its guidance given by the balls between the outer and inner parts.
  • the articulation part on the cylinder drum side is supported directly on the drive pulley, the cage can be mounted between the outer and inner part in a manner known per se, the cage being clamped by the direct support of the articulation part on the cylinder drum side on the drive pulley are prevented.
  • the training contained in claim 6 leads to a simplification because an internal limitation of the inner part is eliminated.
  • the joint is nevertheless stable because the inner part is fixed on the one hand via the balls and on the other hand via the spherical outer surface on the spherical inner surface of the outer part in a predetermined position with respect to the center of the joint.
  • the end facing away from the joint is required the cylinder drum only from radially effective bearing surfaces for the cylinder drum.
  • the bearing at the end of the cylinder drum facing away from the joint is easily achieved by a convex or concave end face, which is formed on a correspondingly shaped sliding surface of the housing.
  • the radially effective bearing effect is present with both a convex and a concave front or sliding surface.
  • the aforementioned sliding surface is provided on a sliding block that can be adjusted according to the desired helix angle.
  • the embodiment according to claim 9 leads to an advantageous structure of the components, both for manufacturing reasons and for reasons of assembly and disassembly. This not only results in individual components of smaller dimensions, but also the optimal materials that are functionally moved for each component can be used. Due to the plug-in connection between the pin or the inner part and the cylinder drum, the rotational driving of the cylinder drum is ensured in a simple manner.
  • the spring force causes a tight yet elastic contact of the end face of the cylinder drum facing away from the drive pulley with the sliding surface on the housing side, as a result of which an increased seal is achieved in particular if control channels for controlling the pump or motor operation are arranged in these surfaces.
  • a permanent contact of the spherical outer surface on the inner part with the spherical inner surface on the outer part leads to a smooth running in the operation of the axial piston machine, whereby a long service life is inevitably predetermined.
  • the configuration according to the invention and the further developments according to the invention are not only suitable for axial piston machines with a constant delivery or displacement volume, but are also particularly suitable for axial piston machines with a variable delivery or absorption volume, because relatively simple oblique or swivel angles are achieved with simple components, namely those up to approx. 40 °.
  • the axial piston machine consists of a two-part housing 1 with a cover 2, a drive shaft 3, on which a drive pulley 4 is formed in one piece, a cylinder drum 5 rotating with the drive pulley 4, which is connected to the drive pulley 4 by a constant velocity joint 6, a plurality of pistons 7, which are in axial bores 8 of the cylinder drum 5 are displaceably mounted, and a generally designated 9 adjusting device, with which the helix angle a, which includes the axis of rotation 11 of the cylinder drum 5 with the axis of rotation 12 of the drive shaft 3, can be set.
  • the drive shaft 3 is mounted in the flange part 13 of the housing 1 by means of roller bearings 14 which are set up to absorb both radial and axial forces.
  • roller bearings 14 which are set up to absorb both radial and axial forces.
  • roller bearings 14 which are set up to absorb both radial and axial forces.
  • the homokinetic joint 6 consists of an outer part 15 with a spherical, concavely curved inner surface 16 in a recess 10 (ball socket) and an inner part 17 with a spherical outer surface 18 which bears on the spherical inner surface 16.
  • the inner part 17 comprises a ring 19, in the circumferential surface of which a plurality of curved grooves 21 are arranged.
  • the grooves 21 are also associated with curved grooves 22 in the spherical inner surface 16, and rolling elements, e.g. Balls 23, recorded, of which only one is shown.
  • the inner part 17 can be pivoted in the outer part 15 about the center point of the joint 24, the inner part 17 being guided both by the rolling elements and by the spherical outer surface 18 bearing against the spherical inner surface 16.
  • the rolling elements are assigned a cage 25 which has a spherical outer surface 26, the curvature of which corresponds to the spherical inner surface 16 of the outer part 15, and which has a spherical inner surface 27 which corresponds to the spherical outer surface 20 of the ring 19.
  • the ring 19 is non-rotatable by a tooth coupling 28, which is indicated, but can be displaced longitudinally arranged on a pin 29.
  • the ring 19 is fixed in its working position only on its side facing the drive pulley 4 by a shoulder 31 which is formed by a head 32 of the pin 29 which is integrally formed on the pin 29 or with a recess 33 on a shoulder 34 of the pin 29 can preferably be attached in a rotationally fixed manner.
  • the pin 29 extends into the cylinder drum 5 and is received in a bore 35 with little movement play therein.
  • a tooth coupling 36 is also arranged between the pin 29 and the cylinder drum 5, which ensures an axial displacement of the pin 29 in the bore 35 when the receptacle is secured against rotation.
  • a compression spring 37 is inserted, which is supported on the end face of the pin 29 and engages on a shoulder of the cylinder drum 5 and acts axially on it in the direction of a sliding surface 38 of the cover 2.
  • the reaction force acting on the pin 29 acts on the inner part 17 in the direction of the drive pulley 4, as a result of which the spherical outer surface 18 of the inner part 17 is constantly acted against the spherical inner surface 16 of the outer part 15.
  • the sliding surface 38 is spherically and convexly curved.
  • the end face 39 of the cylinder drum 5 resting on the sliding surface 38 is concavely curved with the same curvature.
  • the end face 39 of the cylinder drum 5 lies flat against the sliding surface 38, the system being permanent and elastic due to the compression spring force.
  • the cylinder drum 5 In operation of the axial piston machine, which is optionally available as Pump or motor can work, the cylinder drum 5 is driven by the drive pulley 4. This is made possible by three entrainment connections, namely by the rolling elements 23 guided in the grooves 21, 22 and the toothed couplings 28, 36. During the rotation of the cylinder drum 5, the pistons 7 are pushed back and forth in the bores 8, the hydraulic medium passing through Channels 41 is sucked or ejected, which emanate from the bores 8 and open into the end face 39. The channels 41 are arranged opposite suction or pressure channels, not shown, in the sliding surface 38. A detailed description of this configuration is omitted because it is generally known.
  • the roller bodies 23 and the cage 25 are released from forces acting in the direction of the drive pulley 4 on the cylinder drum 5 or on the journal 29, which are indicated by the arrow 42.
  • This is made possible by the direct support of the pin 29 on the drive pulley 4, specifically because of the contact of the spherical outer surface 18 with the spherical inner surface 16.
  • the pin 29 is supported not only axially but also radially in the outer part 15, and thereby the storage of the cylinder drum 5 at its end facing the joint 6 is also ensured.
  • the cylindrical drum 5 is due to the spherical shape of the end face 39 and Sliding surface 38 supported axially and radially.
  • the drive shaft 3 and the cylinder drum 5 with the piston 7 and the joint 6 represent a preassembled structural unit which is axially fixed on the one hand between a retaining ring 43 and on the other hand by the cover 2 or the sliding surface 38 in the housing 1.
  • This configuration enables not only a simple construction, but also a simple assembly or disassembly, because the assembly can be assembled or disassembled from the lid opening 44, the axial alignment being achieved by fitting the lid 2 or the component having the sliding surface 38 The unit is fixed.
  • the adjusting device 9 comprises, in a manner known per se, a sliding shoe 46 which, with a convex sliding surface 47 curved in the shape of an arc of a circle, lies against a correspondingly curved concave sliding surface 48 of the cover 2 and can be pivoted on the sliding surface 47 thereof, which is curved around the center of the joint 24.
  • the pivoting takes place in a manner known per se by means of a slide 49 which can be displaced transversely to the housing 1 in the cover 2 and which surrounds with a driver 51 in the slide shoe 46.
  • the cylinder drum 5 and the joint 6 rotate about the center of the joint 24.
  • the delivery or swallowing volume of the axial piston machine is 0.
  • the angle b which exists between the plane E 1 of the drive pulley 4 and the plane E2 in which the rolling elements are arranged, is approximately half of the swivel angle a.
  • the rolling elements 23 are always on a bisector of the angle denoted by c between the axes of rotation 11, 12 the drive shaft 4 and the cylinder drum 5, whereby the synchronism of the joint 6 is ensured.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP86107345A 1985-06-25 1986-05-30 Machine à pistons axiaux avec une plaque oscillante entre lesquels est disposée une articulation homocinétique Expired EP0205982B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853522716 DE3522716A1 (de) 1985-06-25 1985-06-25 Axialkolbenmaschine mit einer triebscheibe, einer zylindertrommel und einem dazwischen angeordneten homokinetischen gelenk
DE3522716 1985-06-25

Publications (3)

Publication Number Publication Date
EP0205982A2 true EP0205982A2 (fr) 1986-12-30
EP0205982A3 EP0205982A3 (en) 1988-01-13
EP0205982B1 EP0205982B1 (fr) 1988-12-21

Family

ID=6274150

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86107345A Expired EP0205982B1 (fr) 1985-06-25 1986-05-30 Machine à pistons axiaux avec une plaque oscillante entre lesquels est disposée une articulation homocinétique

Country Status (2)

Country Link
EP (1) EP0205982B1 (fr)
DE (2) DE3522716A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104976090A (zh) * 2014-04-08 2015-10-14 林德液压两合公司 带携动柱体转筒携动关节的斜轴结构式静液压轴向活塞机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE465281B (sv) * 1987-09-18 1991-08-19 Volvo Hydraulik Ab Ansaettningsanordning foer cylindertrumman vid en axialkolvmaskin med variabelt deplacement
DE3739927A1 (de) * 1987-11-25 1989-06-08 Man Nutzfahrzeuge Gmbh Gleichlaufgelenk
US5033358A (en) * 1988-01-04 1991-07-23 Hans Molly Axial piston type motor
DE3800031A1 (de) * 1988-01-04 1989-07-20 Molly Hans Dipl Ing Dr Ing E H Axialkolbenmaschine mit drehmomententwicklung an der hubscheibe
DE19829952A1 (de) * 1998-07-04 2000-01-05 Viktor Krenik Hochdruckölpumpe für hydraulische Getriebe

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
DE1220735B (de) * 1958-11-21 1966-07-07 Dowty Hydraulic Units Ltd Gelenkverbindung zwischen der umlaufenden Zylindertrommel und dem winklig dazu umlaufenden Triebflansch einer Axialkolbenmaschine

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129063A (en) * 1975-10-01 1978-12-12 Ifield Engineering Pty. Limited Bent axis pumps and motors

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2146133A (en) * 1936-06-01 1939-02-07 Waterbury Tool Co Power transmission
DE1220735B (de) * 1958-11-21 1966-07-07 Dowty Hydraulic Units Ltd Gelenkverbindung zwischen der umlaufenden Zylindertrommel und dem winklig dazu umlaufenden Triebflansch einer Axialkolbenmaschine

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104976090A (zh) * 2014-04-08 2015-10-14 林德液压两合公司 带携动柱体转筒携动关节的斜轴结构式静液压轴向活塞机
JP2015200317A (ja) * 2014-04-08 2015-11-12 リンデ ハイドロリックス ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフトＬｉｎｄｅ Ｈｙｄｒａｕｌｉｃｓ ＧｍｂＨ ＆ Ｃｏ． ＫＧ シリンダブロックを連行する連行ジョイントを備えた斜軸構造のハイドロスタティック式のアキシャルピストン機械
EP2937567A3 (fr) * 2014-04-08 2016-03-16 Linde Hydraulics GmbH & Co. KG Machine à piston axial hydrostatique dans une construction à axe oblique dotée d'un élément articulé d'entraînement destiné à l'entraînement d'un tambour cylindrique
US9963967B2 (en) 2014-04-08 2018-05-08 Linde Hydraulics Gmbh & Co. Kg Axial piston machine utilizing a bent-axis construction with a drive joint for driving the cylinder barrel
CN104976090B (zh) * 2014-04-08 2019-05-10 林德液压两合公司 带携动柱体转筒携动关节的斜轴结构式静液压轴向活塞机

Also Published As

Publication number Publication date
DE3522716C2 (fr) 1989-01-26
EP0205982B1 (fr) 1988-12-21
DE3522716A1 (de) 1987-01-08
DE3661489D1 (en) 1989-01-26
EP0205982A3 (en) 1988-01-13

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