EP0090206A2 - Machine hydraulique à piston axial - Google Patents

Machine hydraulique à piston axial Download PDF

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Publication number
EP0090206A2
EP0090206A2 EP83102218A EP83102218A EP0090206A2 EP 0090206 A2 EP0090206 A2 EP 0090206A2 EP 83102218 A EP83102218 A EP 83102218A EP 83102218 A EP83102218 A EP 83102218A EP 0090206 A2 EP0090206 A2 EP 0090206A2
Authority
EP
European Patent Office
Prior art keywords
axial piston
swivel body
piston machine
machine according
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
EP83102218A
Other languages
German (de)
English (en)
Other versions
EP0090206B1 (fr
EP0090206A3 (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 EP0090206A2 publication Critical patent/EP0090206A2/fr
Publication of EP0090206A3 publication Critical patent/EP0090206A3/de
Application granted granted Critical
Publication of EP0090206B1 publication Critical patent/EP0090206B1/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
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles
    • 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 a hydraulic axial piston machine according to the preamble of claim 1.
  • Rolling bearings for such tasks are expensive, place high demands on the geometry of the adjacent parts and, due to the internal clearance conditions and the point load caused thereby, can
  • the outer ring cannot be used according to the theoretical static load rating.
  • the vibrations and forces of the pump mechanism prematurely lead to material fatigue in the rolling contact zone or the bearings must be oversized in accordance with the required service life.
  • Hydrostatic bearings are lossy, produce very different friction conditions and require correspondingly high adjustment forces, which in turn is reflected in an increased volume of the adjustment and control devices.
  • the invention is based on the object of a hydraulic axial piston machine, i.e. to create a pump or motor that is compact. and is correspondingly stiff, so that a low-vibration construction arises, and in particular is low in noise.
  • All of the axial forces that occur during operation are transmitted through the curved surface to the linear roller bearing, which is a simple, mass-produced machine element.
  • the design and dimensioning is carried out so that the force transmitted to the running plate is evenly distributed over all rolling elements.
  • the storage according to the invention prevents bending vibrations and thus the noise generated by them. In practice, storage takes place where the resulting force of the axial piston occurs.
  • the axial piston machine is advantageously designed as specified in claims 3 and 4, then the span between the two linear roller bearings is small. If one makes the following theoretical considerations, essential advantages become clear.
  • the support of the resulting axial force on the pressure side of the machine - seen here as a mechanical model - represents a beam on two supports with line load. Since bending vibrations are primarily responsible for noise emissions over all other forms of vibration, the linear roller bearings are arranged as close as possible to the line of action of the resulting axial force . This line of action oscillates slightly (in a practical embodiment around an average of 0.63 of the pitch circle radius of the piston path). Thus, with minimal elastic deflection of the bearing points, the resulting axial force is applied to the corresponding support, i.e. transferred to the damping plates. Due to their good damping behavior, these effectively couple the excitation vibrations of the swivel body from the control floor.
  • the axial piston pump shown in the drawing has. a flange 1, which ensures the connection with the corresponding supply and discharge lines for the hydraulic oil.
  • the flange 1 is connected to a housing 2 by screws.
  • 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, namely 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 with the outer surface of the cylinder drum 7 . a fit that allows 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 - viewed from a functional point of view - 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 rotatably mounted on the two pins 14 of the pin ring 42 .
  • the axis of rotation is identical to the transverse or pin axis MM.
  • the rear side of the swivel body 12 has a radius R in the areas L, so that when the swivel body 12 rotates about the pin axis MM, a linear movement of the running plate 16 results.
  • swivel body 12 is fixed in the MM axis, and the documents - that is, running plate 16 - move transverse to the MM axis.
  • 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 in the vertical direction.
  • 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 to secure the position of the linear roller bearings 18, 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 elastic deflection of these entire bearings can be calculated by correspondingly calculating the rigidity of the running plate 16, the fixed plates 19 and the damping plates 21 place so influenced that the line force (Hertzian pressure) introduced between swivel body 12 and bearing plate 16 distributes the bearing force evenly over all rolling elements of the linear roller bearings.
  • the operating noises and the vibrations of the pump mechanism were isolated from the control floor 22 by the damping plates 21 made of plastic.
  • 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)
EP83102218A 1982-04-02 1983-03-07 Machine hydraulique à piston axial Expired EP0090206B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3212402A DE3212402A1 (de) 1982-04-02 1982-04-02 Hydraulische axialkolbenmaschine
DE3212402 1983-04-02

Publications (3)

Publication Number Publication Date
EP0090206A2 true EP0090206A2 (fr) 1983-10-05
EP0090206A3 EP0090206A3 (en) 1984-04-04
EP0090206B1 EP0090206B1 (fr) 1986-11-26

Family

ID=6160135

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102218A Expired EP0090206B1 (fr) 1982-04-02 1983-03-07 Machine hydraulique à piston axial

Country Status (3)

Country Link
EP (1) EP0090206B1 (fr)
JP (1) JPS58185982A (fr)
DE (2) DE3212402A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0928895A3 (fr) * 1998-01-09 2001-03-28 Brueninghaus Hydromatik Gmbh Machine à pistons axiaux avec support

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4301119C2 (de) * 1993-01-18 1995-03-30 Danfoss As Schrägscheibenanordnung in einer hydraulischen Axialkolbenmaschine

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1266132B (de) * 1959-10-20 1968-04-11 Materiels Hispano Suiza Sa Soc "Anordnung des Kardangelenks fuer den angetriebenen Schiefschei-benlaufring einer Axialkolben-maschine"
JPS5532910B2 (fr) * 1974-01-18 1980-08-27
IT1087011B (it) * 1976-10-19 1985-05-31 Linde Ag Macchina a stantuffi assiali del tipo di costruzione a flangia di trasmissione
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0928895A3 (fr) * 1998-01-09 2001-03-28 Brueninghaus Hydromatik Gmbh Machine à pistons axiaux avec support

Also Published As

Publication number Publication date
EP0090206B1 (fr) 1986-11-26
DE3212402A1 (de) 1983-10-13
JPS58185982A (ja) 1983-10-29
DE3367961D1 (en) 1987-01-15
JPH0341678B2 (fr) 1991-06-24
EP0090206A3 (en) 1984-04-04

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