EP0090952B1 - Machine hydraulique à piston axial - Google Patents

Machine hydraulique à piston axial Download PDF

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Publication number
EP0090952B1
EP0090952B1 EP83102219A EP83102219A EP0090952B1 EP 0090952 B1 EP0090952 B1 EP 0090952B1 EP 83102219 A EP83102219 A EP 83102219A EP 83102219 A EP83102219 A EP 83102219A EP 0090952 B1 EP0090952 B1 EP 0090952B1
Authority
EP
European Patent Office
Prior art keywords
bearing
piston machine
axial piston
machine according
bearing ring
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
EP83102219A
Other languages
German (de)
English (en)
Other versions
EP0090952A2 (fr
EP0090952A3 (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 EP0090952A2 publication Critical patent/EP0090952A2/fr
Publication of EP0090952A3 publication Critical patent/EP0090952A3/de
Application granted granted Critical
Publication of EP0090952B1 publication Critical patent/EP0090952B1/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
    • 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.
  • Such an axial piston machine is known from DE-A-2 101 078. If such a design is chosen in which the radial bearing is a plain bearing, the service life of such a plain bearing is short. Among other things, this is attributable to the fact that such a radial slide bearing consists of a stationary bearing shell and a rotating shaft. When the shaft rotates, a hydrodynamic lubricating film forms in the pressure zone due to its eccentric displacement.
  • the invention has for its object to provide an axial piston machine of the type mentioned, which reduces the noise generated by the radial bearing between the stator and cylinder drum, without significantly reducing the life of this bearing.
  • the bearing ring runs in relation to both the stator and the rotor, i.e. to the cylinder drum.
  • This design resulted in a significant reduction in noise generation in this area without reducing the life of this bearing in relation to rolling bearings. Furthermore, such storage is very inexpensive.
  • This surprising result was confirmed by tests even under extreme conditions. Experiments were carried out (Sommerfeld numbers from minimum 0.1 to maximum 30), whereby a completely wear-free lubrication of the bearing point was ensured.
  • the thickness of the lubrication gaps on the outer and inner circumference was calculated depending on the material properties so that the gaps were the same thickness at an operating temperature of approx. 100 ° C.
  • the results achieved with regard to smooth running were remarkable.
  • the service life was no less than that of conventionally used rolling bearings.
  • the bearing according to the invention is not a normal plain bearing, since in the case of the invention not part of the bearing is stationary and the other rotates alone, but the bearing ring rotates relative to the stator and cylinder drum.
  • Claims 2 to 4 are directed to bearing rings designed in an advantageous manner.
  • the claim 5 protects a certain arrangement of the bearing ring with the help of an additional sleeve between the bearing ring and cylinder drum.
  • the claims 7 and 8 are directed to the special design and storage of the stator as a central tube in connection with the storage.
  • 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 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 journal 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 (FIG. 6) and an outer lubricating gap Sa with the central tube 41, so that two column functions are considered in series - 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.
  • the axis of rotation is identical to the transverse or pin axis MM that there is a linear movement of the running plate 16 when the pivot body 12 rotates about the pin axis MM.
  • 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 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 this entire bearing point can be influenced in such a way that the bearing force introduced via a line contact (Hertzian pressure) between the swivel body 12 and the running plate 16 increases evenly distributed all rolling elements of the linear roller bearings.
  • the operating noises and the vibrations of the pump mechanism are isolated from the control base 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)
  • Details Of Reciprocating Pumps (AREA)

Claims (8)

1. Machine à piston axial hydraulique du type disque en mutation avec un arbre pour le tambour de cylindre qui sort d'un côté et avec un palier à glissement radial entre le stator et le tambour de cylindre, caractérisée en ce que le palier à glissement radial entre le stator (41) et le tambour de cylindre (7) présente un anneau de palier (43) placé de manière à être flottant et rotatif librement par rapport au stator et au tambour de cylindre.
2. Machine à piston axial selon la revendication 1, caractérisée en ce que l'anneau de palier (43) est pourvu de forures radiales de graissage qui sont alimentées en huile sous pression (par 51).
3. Machine à piston axial selon la revendication 2, caractérisée en ce que l'alimentation en huile sous pression (51) est effectuée dans le sens de la rotation, ceci étant vu peu avant la zone de refoulement du palier.
4. Machine à piston axial selon la revendication 3, caractérisée en ce que l'alimentation en huile sous pression est effectuée par une soupape d'étranglement de débit (non représentée).
5. Machine à piston axial selon la revendication 1, caractérisée en ce qu'une douille est placée entre l'anneau de palier (43) et le tambour de cylindre (7), douille qui est précontrainte contre la face latérale adjacente de l'anneau de palier (43) par un ensemble de ressorts (47) avec un bourrelet.
6. Machine à piston axial selon la revendication 5, caractérisée en ce que des canaux de graissage (50) qui sont obliques par rapport au sens de rotation et qui sont orientés vers la face latérale de l'anneau de palier (43) sont formés dans le bourrelet (44).
7. Machine à piston axial selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que le stator présente un tube central (41) sur lequel s'appuie l'anneau de palier (43) et qui est relié au palier du disque en mutation (42, 22).
8. Machine à piston axial selon la revendication 1, caractérisée en ce qu'au moins un anneau amortisseur (57) en plastique ou en matière équivalente est placé entre le tube central (41) et le bâti (2).
EP83102219A 1982-04-02 1983-03-07 Machine hydraulique à piston axial Expired EP0090952B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3212374 1982-04-02
DE19823212374 DE3212374A1 (de) 1982-04-02 1982-04-02 Hydraulische axialkolbenmaschine

Publications (3)

Publication Number Publication Date
EP0090952A2 EP0090952A2 (fr) 1983-10-12
EP0090952A3 EP0090952A3 (en) 1984-03-28
EP0090952B1 true EP0090952B1 (fr) 1987-07-01

Family

ID=6160125

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102219A Expired EP0090952B1 (fr) 1982-04-02 1983-03-07 Machine hydraulique à piston axial

Country Status (3)

Country Link
EP (1) EP0090952B1 (fr)
JP (1) JPS58185983A (fr)
DE (2) DE3212374A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102242700A (zh) * 2011-06-28 2011-11-16 张坚 新型变量油泵

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4220922B1 (fr) * 1960-04-28 1967-10-18
GB1082807A (en) * 1964-11-19 1967-09-13 Serck R & D Ltd Hydraulic machines with reciprocatory pistons
JPS4411531Y1 (fr) * 1965-08-24 1969-05-14
BE755124A (fr) * 1969-08-21 1971-02-22 Caterpillar Tractor Co Palier de butee pour pompe ou moteur a pistons notamment d'engins de terrassement
DE2036868A1 (de) * 1970-07-24 1972-01-27 Integral Ltd., London Taumelscheibenpumpe oder -motor
DE2101078A1 (de) * 1971-01-12 1972-08-03 Robert Bosch Gmbh, 7000 Stuttgart Axialkolbenmaschine
US3898917A (en) * 1974-01-31 1975-08-12 Abex Corp Variable displacement fluid translating device

Also Published As

Publication number Publication date
DE3212374A1 (de) 1983-10-06
DE3372299D1 (en) 1987-08-06
EP0090952A2 (fr) 1983-10-12
JPS58185983A (ja) 1983-10-29
EP0090952A3 (en) 1984-03-28

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