EP0090953B1 - Machine hydraulique à piston axial - Google Patents

Machine hydraulique à piston axial Download PDF

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Publication number
EP0090953B1
EP0090953B1 EP83102220A EP83102220A EP0090953B1 EP 0090953 B1 EP0090953 B1 EP 0090953B1 EP 83102220 A EP83102220 A EP 83102220A EP 83102220 A EP83102220 A EP 83102220A EP 0090953 B1 EP0090953 B1 EP 0090953B1
Authority
EP
European Patent Office
Prior art keywords
bearing
axial piston
piston machine
ring
housing
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
Application number
EP83102220A
Other languages
German (de)
English (en)
Other versions
EP0090953A2 (fr
EP0090953A3 (en
Inventor
Wilhelm Nolden
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.)
PepsiAmericas Inc
Original Assignee
Abex Corp
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 Abex Corp filed Critical Abex Corp
Publication of EP0090953A2 publication Critical patent/EP0090953A2/fr
Publication of EP0090953A3 publication Critical patent/EP0090953A3/de
Application granted granted Critical
Publication of EP0090953B1 publication Critical patent/EP0090953B1/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
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels
    • 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
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/12—Coating

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • Hydraulic axial piston machines i.e. Pumps or motors are known in a wide variety of designs.
  • Such hydraulic axial piston machines have a permanent place in the drive technology due to the high power density, the possibility of continuously variable gear ratio to adapt to different operating data, a natural overload protection and the relatively large mobility between drive (pump) and drive (motor, cylinder).
  • They have the disadvantage that they generate strong operating noises.
  • the demand for higher capacities and power densities higher pressures, speeds and flow velocities with a reduced construction mass
  • stands in the way of effective noise reduction at the point of origin so that expensive and time-consuming secondary measures (encapsulation and isolated installation) are often necessary to keep the noise pollution bearable .
  • the hydraulic axial piston machines have a large number of different components, which, including the associated transmission lines, form a complicated vibration system with many excitation points, which mutually influence each other and, via complex transmission mechanisms, the vibratory components of such a machine - and that almost all components - cause vibrations in a variety of ways stimulate.
  • Known hydraulic axial piston machines have a housing made of gray cast iron or a light metal alloy, to which the vibrations are transmitted directly, so that the noise is also radiated directly here.
  • the force flow of the excitation forces, i.e. The forces generated during operation lead through the housing and thus cause the direct noise emission to the outside.
  • the invention has for its object to provide a hydraulic axial piston machine according to the preamble of claim 1, which runs quietly and at the same time enables a higher power and power density without the construction mass being increased by additional components.
  • a support frame which essentially consists of the central tube, the distributor and the control floor.
  • the distributor and the control floor are connected to the central pipe in a positive or non-positive manner.
  • the central tube also serves as the bearing for the radial bearing of the cylinder drum.
  • the central tube which is not a component that is visible from the outside - it lies in the housing cap - can be made of a material which is advantageous for its technical task and can be constructed in such a way as is necessary to absorb the forces and to support it.
  • the entire flow of power, which originates from the excitation forces - generated between the piston and the cylinder drum - remains in the distributor, in the central tube, in the control floor and in the swashplate. In addition to the piston and cylinder drum, these are the components through which the power flow takes place. The power flow does not take place through the housing, so that direct noise emission to the outside is prevented.
  • the noise damping is supported by the damping ring.
  • the axial piston pump shown in the drawing has a flange 1 which ensures the connection to the corresponding supply and discharge lines for the hydraulic oil.
  • the flange 1 is connected to a housing 2 by screws.
  • the axial piston machine can advantageously be designed as specified in claim 5.
  • the advantages of plain bearing technology can be exploited without having to accept disadvantages in terms of service life and the like.
  • the floating and freely rotating bearing ensures a correspondingly long service life.
  • the advantages of lower noise generation in relation to rolling bearings can be used in connection with the other measures for noise reduction and damping.
  • the bearing between the swash plate and the control base is constructed in such a way that a damping plate (claim 4) can be used, so that transmission of noise to the outside is suppressed in this area as well.
  • the drive shaft 5 is passed through the distributor 3 and the control plate 6.
  • the drive shaft drives a cylinder drum 7 with a piston 8.
  • the connection between the drive shaft 5 and the cylinder drum 7 takes place via a toothing sleeve 38 made of plastic or similar damping material with an internal and external tooth profile for transmitting the torque.
  • a helical spring 39 ensures a corresponding preload.
  • a housing cap 4 which surrounds the other components of the axial piston pump, is fastened to the housing 2 with the aid of a tensioning band 35 and with the interposition of a sealing ring 37.
  • the sliding shoes 11 are biased against the swash plate 10 by a pressure plate 9.
  • the drive shaft 5 led out of the housing 2 on one side is supported in a slide bearing 52 with corresponding bearing shells and bearing rings.
  • a sealing ring 53 which also rotates, ensures a corresponding seal. It is biased by several springs 56.
  • a pin 55 ensures that the sealing ring 53 also rotates.
  • a cover 54 forms the closure of the housing 2.
  • the actual stator of the axial piston pump is formed by a central tube 41 which is mounted in the housing 2 via two plastic damping rings 57.
  • This central tube 41 practically forms a support frame for absorbing all hydraulic forces, both in the axial and in the radial direction.
  • the central tube serves to support the cylinder drum 7 forming the rotor and a pin ring 42 for guiding the swash plate 10 and for fastening the control base 22, which absorbs the axial forces of the swivel body bearing.
  • the cylinder drum is supported by a freely rotating bearing ring 43 which has a number of radial lubrication bores 48.
  • the cylinder drum 7 is received by a sleeve 45 which is supported axially and radially against the bearing ring 43.
  • the sleeve forms a fit with the outer surface of the cylinder drum 7, which enables a relative axial movement.
  • a relative rotational movement is prevented by a pin 46.
  • Wave springs 47 which generate an axial preload, ensure that the bearing ring 43 runs smoothly.
  • the preload simultaneously forms the static pressure of the cylinder drum 7 on the control plate 6.
  • the freely rotating bearing ring 43 forms an inner lubricating gap Si with the sleeve 45 and an outer lubricating gap Sa with the central tube 41, so that two gaps functionally considered - are connected in series.
  • the mean resulting lateral force of all pistons loaded on the pressure side of the pump runs in the direction of arrow Z (FIG. 6) and loads the bearing ring 43 in the center.
  • the build-up of two heavy-duty hydrodynamic oil pressure films in the Si and Sa columns is supported by pressure oil from the high-pressure side of the pump, which is forced in front of the pressure zone via a flow restrictor.
  • the supply takes place via a supply line 51.
  • the lubrication gap Si is supplied by the radial lubrication holes 48 in the bearing ring 43.
  • appropriately designed lubrication channels 50 are formed on the bead 44 of the sleeve 45, depending on the direction of rotation. As a result, the bearing ring 43 is flooded with splash oil from the pump housing during operation.
  • the bearing ring 43 is supported on the other side against a support ring 49 provided with openings. Due to the flooding of the bearing ring 43 described, a highly loaded hydrodynamic lubricating film also forms in the gap to the support ring 49 during operation.
  • the central tube 41, the pin ring 42, the support ring 49 and the control plate 6 are to be considered as stator parts.
  • the cylinder drum 7 with the sleeve 45 rotate at the pump speed.
  • a drag torque acts on the bearing ring 43 during operation, so that it rotates at about half the pump drive speed under normal operating conditions (approx. 100 ° C.).
  • the swash plate 10 is pivotally mounted so that a variable piston stroke results when pivoted about a corresponding transverse axis.
  • the swash plate 10 is screwed onto a swivel body 12.
  • Lateral guide arms 13 of the swivel body 12 laterally each comprise a sliding block 15 which is rotatably mounted on the two pins 14 of the pin ring 42.
  • the axis of rotation is identical to the transverse or pin axis M-M.
  • the rear of the swivel body 12 has a radius R in the areas L, so that when the swivel body 12 is rotated about the pin axis MM, there is a linear movement of the running plate 16.
  • a frictional engagement occurs between the swivel body 12 and the running plate 16, similar to how a loaded roller rolls on a flat surface, with the only difference that the roller - i.e. swivel body 12 - is fixed in the MM axis here is, and the documents - ie running plate 16 - moves transversely to the axis MM.
  • the swivel body 12 and the running plate 16 are coupled via guide grooves and rollers 17.
  • the movement of the running plate 16 runs vertically.
  • the running plate 16 is in turn supported on two linear roller bearings 18 which roll on fixed plates 19.
  • a cage 20 is used which, like a frame, encompasses the linear roller bearings and secures them in the respective position without play.
  • the running plate 16 runs through twice the distance as the cage 20 or the linear roller bearing 18.
  • the fixed plates 19 rest on damping plates 21 made of plastic, which in turn are arranged in corresponding chambers in the control floor 22.
  • the control base 22 is screwed to the pin ring 42.
  • the pump regulator 24 with the adjusting piston 25 is accommodated in the control base 22.
  • the adjusting piston 25 is designed as a differential piston.
  • a yoke 26 is screwed onto the rod end of the adjusting piston and comprises a bolt 27 in the form of a fork.
  • the bolt is rotatably mounted in a bridge 28.
  • the bridge 28 is screwed to the swivel body 12.
  • control slots 32 and 33 are formed in the control plate, which ensure a connection to the suction line 30 and the pressure line 31, respectively.
  • Sleeves 34 made of plastic represent an acoustic decoupling of the distributor 3 from the housing 2 and therefore contribute to noise reduction.
  • a line 36 is supplied with pressure oil from the pressure side, which in turn supplies the pump regulator 24 and the channel 51 with pressure oil.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)

Claims (6)

1. Machine hydraulique à piston axial du type à disque en mutation avac un arbre sortant vers l'extérieur à une extrémité pour le tambour du cylindre, avec un distributeur et un palier radial entre le stator fixé sur le bâti et le tambour de cylindre, caractérisée en ce que le stator est constitué comme un tube central (41) sur lequel s'appuient le palier radial (43), le distributeur (3) et un fond de commande (22) servant au positionnement du disque en mutation (10), qu'un anneau d'amortissement (57) est placé entre la bâti (2) et le tube central (41) et que les éléments de la pompe qui ne se trouvent pas dans le bâti (2) sont recouverts par un capuchon de bâti nonportant, relié au bâti.
2. Machine à piston axial selon la revendication 1, caractérisée en ce que le capuchon de bâti (40) est fabriqué en un matériau amortisseur de bruit.
3. Machine à piston axial selon la revendication 1 ou 2, caractérisée en ce que le disque en mutation (10) est positionné de manière pivotante de manière connue en soi dans le pivot (14) d'un anneau de pivot d'un corps pivotant (12) et que le corps pivotant (12) avec le disque en mutation (10) est mobile verticalement par rapport à l'axe de pivot M-M et au-dessus d'une surface recourbée (29), dont le rayon de courbure R se trouve avec son centre sur l'axe de pivot M-M, et qu'il roule sur une plaque de roulement (16) qui s'appuie à son tour par l'intermédiaire d'un palier à rouleaux linéaires (18, 19) sur un fond de commande (22) relié à l'anneau de pivot (42).
4. Machine à piston axial selon la revendication 3, caractérisée en ce qu'une plaque d'amortissement (21) en plastique ou équivalent est placée entre le palier à rouleaux linéaires (18,19) et le fond de commande (22).
5. Machine à piston axial selon l'une des revendications précédentes, caractérisée en ce que le palier entre le tube central (41) et le tambour de cylindre (7) présente un anneau de palier (43) placé de manière flottante et à rotation libre.
6. Machine à piston axial selon la revendication 5, caractérisée en ce que l'anneau de palier (43) est pourvu de forures radiales de graissage (48) alimentées en huile de pression (par 51).
EP83102220A 1982-04-02 1983-03-07 Machine hydraulique à piston axial Expired EP0090953B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19823212429 DE3212429A1 (de) 1982-04-02 1982-04-02 Hydraulische axialkolbenmaschine
DE3212429 1983-04-02

Publications (3)

Publication Number Publication Date
EP0090953A2 EP0090953A2 (fr) 1983-10-12
EP0090953A3 EP0090953A3 (en) 1984-03-28
EP0090953B1 true EP0090953B1 (fr) 1987-02-04

Family

ID=6160147

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102220A Expired EP0090953B1 (fr) 1982-04-02 1983-03-07 Machine hydraulique à piston axial

Country Status (3)

Country Link
EP (1) EP0090953B1 (fr)
JP (1) JPS58185984A (fr)
DE (2) DE3212429A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4203619C2 (de) * 1992-02-07 1996-07-25 Rexroth Mannesmann Gmbh Hydrauliksystem
DE19957568B4 (de) * 1999-11-30 2014-02-13 Linde Hydraulics Gmbh & Co. Kg Anordnung mit einem Schwungrad und einer hydrostatischen Axialkolbenmaschine
DE19957565B4 (de) * 1999-11-30 2013-02-07 Linde Material Handling Gmbh Geräuschgedämpfte hydrostatische Kolbenmaschine
DE102010047431A1 (de) * 2010-10-04 2012-04-05 Robert Bosch Gmbh Axialkolbenmaschine mit einer in eine Nut eines Gehäuseteils eingesetzten Steuerplatte
DE102011009537A1 (de) * 2011-01-27 2012-08-02 Robert Bosch Gmbh Hydrostatische Maschine, insbesondere Axialkolbenmaschine
DE102012215238A1 (de) * 2012-08-28 2014-03-06 Robert Bosch Gmbh Schrägscheibenmaschine
DE102013200729A1 (de) * 2013-01-18 2014-07-24 Robert Bosch Gmbh Schrägscheibenmaschine
DE102013210070B3 (de) * 2013-05-29 2014-05-28 Sauer-Danfoss Gmbh & Co. Ohg Axialkolbenmaschine mit Korb
CH714321A1 (de) 2017-11-11 2019-05-15 Liebherr Machines Bulle Sa Verstellvorrichtung für eine Axialkolbenmaschine.
DE102019212074A1 (de) * 2019-08-13 2021-02-18 Robert Bosch Gmbh Motor-Hydromaschinen-Einheit zum Anbau an ein Hydraulikaggregat

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1359244A (fr) * 1963-03-12 1964-04-24 Hispano Suiza Sa Perfectionnements apportés aux machines à pistons du type à barillet, notamment aux pompes hydrauliques de ce genre
CH451853A (fr) * 1966-03-10 1968-05-15 Bennes Marrel Machine hydraulique à barillet rotatif
JPS5735198B2 (fr) * 1972-08-31 1982-07-27
JPS5948218B2 (ja) * 1977-06-24 1984-11-24 住友化学工業株式会社 合成樹脂ペレットの気体輸送に於けるフロス発生低減方法
DE3026765A1 (de) * 1980-07-15 1982-02-11 Linde Ag, 6200 Wiesbaden Axialkolbenpumpe fuer zwei foerderstroeme

Also Published As

Publication number Publication date
DE3212429A1 (de) 1983-10-13
EP0090953A2 (fr) 1983-10-12
JPS58185984A (ja) 1983-10-29
EP0090953A3 (en) 1984-03-28
DE3369719D1 (en) 1987-03-12

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