EP0301229B1 - Machine à pistons axiaux avec disque oblique à paliers radiaux - Google Patents

Machine à pistons axiaux avec disque oblique à paliers radiaux Download PDF

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Publication number
EP0301229B1
EP0301229B1 EP88109855A EP88109855A EP0301229B1 EP 0301229 B1 EP0301229 B1 EP 0301229B1 EP 88109855 A EP88109855 A EP 88109855A EP 88109855 A EP88109855 A EP 88109855A EP 0301229 B1 EP0301229 B1 EP 0301229B1
Authority
EP
European Patent Office
Prior art keywords
piston machine
axial piston
bearing
swash plate
machine according
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 - Lifetime
Application number
EP88109855A
Other languages
German (de)
English (en)
Other versions
EP0301229A2 (fr
EP0301229A3 (en
Inventor
Manfred Lotter
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 EP0301229A2 publication Critical patent/EP0301229A2/fr
Publication of EP0301229A3 publication Critical patent/EP0301229A3/de
Application granted granted Critical
Publication of EP0301229B1 publication Critical patent/EP0301229B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01B3/02—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis with wobble-plate

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • the swash plate body is loaded not only axially but also radially, which results from the oblique course of the inclined surface of the swash plate body.
  • the swashplate body must therefore be stored so that these loads are absorbed. It is possible not to provide a separate bearing for the swashplate body, and to ensure the support of the swashplate body on the one hand by appropriate design of the drive shaft bearing and on the other hand by a stable design of the drive shaft, the latter being subject to considerable bending loads during operation of the axial piston machine. In such an embodiment, a large construction effort and a large construction result due to a stable drive shaft and a comparatively large drive shaft bearing.
  • the invention has for its object to design an axial piston machine of the type mentioned in such a way that the drive shaft or its mounting is essentially free of radial supporting or tilting forces of the swashplate body.
  • the bearing surface for the radial mounting of the swash plate body is arranged in the region of the projection of the inclined surface of the swash plate body onto the central axis.
  • the radial bearing according to the invention is thus suitable for absorbing the radial forces acting on the swashplate body essentially completely, whereby the drive shaft bearing is essentially free from radial forces and the drive shaft from bending forces and can therefore be made weaker, which on the one hand results in a small design and on the other hand small weight and low manufacturing costs for the axial piston machine leads.
  • the invention also makes it possible to include the drive shaft bearing in the swashplate body bearing, so that a separate drive shaft bearing can be dispensed with.
  • the design according to claim 5 also leads to a relief of the drive shaft bearing in the axial direction, so that the drive shaft bearing can also be designed axially much weaker, which enables a further reduction in size and manufacturing costs.
  • the features contained in claim 6 also contribute to this.
  • the embodiment according to claim 7 leads to a simple design for the swash plate body.
  • claims 10 and 11 enable simple and inexpensive production of the cavity, the cavity opening into a bearing surface area which is subject to lower radial loads.
  • the essential components of the axial piston machine are a housing 2 with a cup-shaped housing part 3 and a housing cover 4, a drive shaft 5 which extends axially through the interior 6 of the housing 2, an arranged on the drive shaft 5 and of this drivable swash plate body 8 with a slanted surface 9, a plurality of pistons 11 which are displaceable in piston bores 12 arranged in a partial circle in the housing cover 4, and a control valve arrangement to be described.
  • the swashplate body 8 which is arranged on the drive shaft 5 by means of a central opening and is connected in a rotationally fixed manner, has the shape of a cylinder with an oblique end face which forms the slanted surface 9, the cylindrical outer surface 15 of the swashplate body 8 and the radial end face of the swashplate body 8 facing away from the swashplate surface 9 are designed as appropriately machined and possibly hardened bearing surfaces 17, 18.
  • the swashplate body is supported with these bearing surfaces 17, 18 on the radial inner wall 19 and on the cylindrical inner wall 21 of the housing 2 radially and axially, whereby a radial force F r sustainable radial bearing 22 and an axial force F l axial bearing 23 is formed.
  • the length 1 of the radial bearing 22 extends over the entire height h of the swash plate body 8 and thus in the region of the projection P 1 of the slant surface 9 on the central axis 24, and it is also extended to the side of the slant plate body 8 facing away from the slant surface 9 by the dimension V.
  • a force field is formed by the radial forces Fr and the axial forces F l or the resulting force F R.
  • the force field denoted by K extends radially in the region of the radial projection P 1 of the inclined surface 9 and axially in the axial projection P 2 of the inclined surface 9.
  • the swash plate body 8 is thus supported completely radially and axially, so that the axial piston machine operates during operation
  • Drive shaft is exempt from radial and axial forces as well as tilting forces.
  • the drive shaft 5 can thus be made relatively weak, ie with a relatively small diameter.
  • the configuration according to the invention makes it possible to include the mounting of the drive shaft in the mounting of the swash plate body at least at the drive end. This means that there is no need for a conventional or separate drive shaft bearing in the radial wall of the housing.
  • the component denoted by 10 is a shaft seal.
  • a separate drive shaft bearing can also be designed to be relatively weak, both in the radial and in the axial direction. In any case, both the cost of materials and the size are significantly reduced.
  • the drive shaft 5 in the present embodiment is mounted in the housing cover 4, preferably in a plain bearing.
  • the radial force F r is on an axial surface line 26 or on an axially extending bearing surface section 27 directed in the region of the greatest height h of the swashplate body 8.
  • the resulting surface pressure is relatively low because a large bearing surface is predetermined due to the radial bearing length 1 extending over the entire projection P 1.
  • the effective length 1 of the radial bearing 22 is smaller, but this is irrelevant because the radial load is significantly lower in these circumferential areas.
  • Both the radial bearing 22 and the axial bearing 23 are assigned a bearing ring 28 or a bearing disc 29 made of wear-resistant material, on the bearing surfaces of which the swash plate body 8 slides. It is therefore a radial and axial slide bearing.
  • a cavity 33 is formed in the half 31 of the swashplate body 8 facing the longest axial surface line 26 or the longest bearing surface section 27, through a bore 32 formed through a secant to the surface line 26 or the bearing surface section 27.
  • the cavity 33 is preferably open on both sides, specifically in areas of the bearing surface 18 in which there is less surface pressure. That is, in the area of the greatest surface pressure, namely in the area of the axial surface line 26 or the bearing surface section 27, the cavity 33 is covered and thus the bearing surface 18 is not reduced.
  • the cavity 33 communicates with the interior 6 of the housing 2 through an inclined channel 34.
  • Another axial channel 35 extends from the cavity 33 to the bearing surface 18 of the axial bearing 23.
  • This configuration provides effective lubrication of both the bearing surface 18 of the radial bearing 22, see mouths 36 of the cavity 33 and the bearing surface 18 of the thrust bearing 23, see mouth 36.1.
  • This lubrication is forced because the oil in the cavity 33 is under pressure due to the distance a of the cavity 33 from the central axis 24 and due to the resulting centrifugal force during operation of the axial piston machine, whereby the oil is pressed against the bearing surfaces 17, 18 and forms the desired lubricating film there.
  • the axial piston machine 1 is a pump with inlet valves 36 and outlet valves 37 assigned to each piston 11 or each piston bore 12.
  • the inlet valves 36 are each formed by a channel connection running inside the piston 11 and emerging radially at a specific point on the piston jacket 38.
  • the arrangement is such that this point, designated 39, is exposed to the interior 6 of the housing 2 in the retracted position of the piston 11 (shown), but is covered by the associated piston bore wall 12 in the advanced position of the piston 11.
  • the distance b of this point 39 from the edge 41 of the piston bore 12 in the retracted position of the piston 11 is to be adapted to the functional requirements of the pump and is approximately 2 mm in the present exemplary embodiment.
  • the piston bore 12 is filled by negative pressure.
  • pistons 11 with a bore 43 extending from its end face are formed by at least one, preferably four radial bores 44.
  • the outlet valves 37 are non-return valves which are arranged in an annular body 45 which is arranged between the cup-shaped housing part 3 and the housing cover 4.
  • the closing members 46 of the outlet valves 37 are arranged in radial bores 47 in ring bodies 45 which open at their radially outer ends into a common ring channel 48 which is delimited on the outside by the housing jacket part and from which a discharge line 49 extends radially inwards.
  • the closing members 46 are spring-biased radially inwards against radially outwardly directed channels 40 emanating from the piston bores 12, whereby the valve seat is formed in each case.
  • the radial channel 48 is sealed by two 0-rings 50 arranged in grooves on both sides.
  • a feed line 51 opens radially inward into the interior 6 of the housing 2.
  • a retraction plate 52 is provided for holding the pistons 11 on the inclined surface 9, which is supported by means of a spherical head bearing 53 on an axially displaceable support sleeve 54 and acts against the sliding shoes 55 which are articulated with the pistons 11.
  • the support sleeve 54 is acted upon by a spring 56 against the inclined surface 9.

Landscapes

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

Claims (13)

1. Machine à piston axial avec un support de disque à nutation (8) disposé dans un carter (2) de manière à permettre une rotation moyennant un arbre moteur, logé radialement dans un palier (22) et supporté axialement par une butée (23), caractérisée en ce que la longueur d'appui (1) du palier (22) s'étend essentiellement dans la section représentée par la projection (P₁) de la surface oblique (9) du support de disque à nutation sur l'axe (24).
2. Machine à piston axial suivant la revendication 1, caractérisée en ce que la surface d'appui (18) du support de disque à nutation (8) est formée par la surface circonférentielle du support de disque à nutation (8) entourant au moins partiellement la surface oblique (9).
3. Machine à piston axial suivant la revendication 2, caractérisée en ce que la surface d'appui (18) du palier (22) est prolongée vers le coté opposé à la surface oblique (9).
4. Machine à piston axial suivant une des revendications 1 à 3, caractérisée en ce que la surface d'appui (18) s'étend essentiellement sur toute la hauteur (h) du support de disque à nutation (8).
5. Machine à piston axial suivant une des revendications 1 à 4, caractérisée en ce que le support de disque à nutation (8) est supporté axialement par une butée (23) disposée entre le côté du support opposé à la surface oblique (9) et la surface intérieure (19) du carter (2) située en face dudit côté.
6. Machine à piston axial suivant une des revendications 1 à 5, caractérisée en ce que la butée (23) et/ou le palier (22) est/sont un/des palier-glisseur(s).
7. Machine à Piston axial suivant une des revendications 1 à 6, caractérisée en ce que le support de disque à nutation (8) a la forme d'un cylindre ayant une face oblique formant la surface oblique (9).
8. Machine à piston axial suivant une des revendications 1 à 7, caractérisée en ce qu'une cavité (33) est située dans la moitié du support contenant la partie plus grande de la masse du support de disque à nutation (8).
9. Machine à piston axial suivant la revendication 8, caractérisée en ce que la cavité (33) est close dans la section d'enveloppe (27) comprenant la hauteur maximale (h) du support de disque à nutation (8).
10. Machine à piston axial suivant une des revendications 9 ou 10, caractérisée en ce que la cavité (33) a au moins une sortie dans l'enveloppe du support de disque à nutation (8) qui est décalée le long la circonférence par rapport à la ligne axiale (26) d'enveloppe ou par rapport à la section d'enveloppe (27) s'étendant dans la zone de hauteur maximale (h).
11. Machine à piston axial suivant la revendication 10, caractérisée en ce que la cavité (33) est formée par un alésage secant et plus particulièrement par un alésage de passage.
12. Machine à piston axial suivant une des revendications 1 à 11, caractérisée en ce que la cavité (33) communique avec l'intérieur (6) du carter (2) moyennant un canal (34).
13. Machine à piston axial suivant la revendication 12, caractérisée en ce qu'un canal (35) sortant dans la région de la surface radiale d'appui (17) du support de disque à nutation (8), part de la cavité (33).
EP88109855A 1987-07-28 1988-06-21 Machine à pistons axiaux avec disque oblique à paliers radiaux Expired - Lifetime EP0301229B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873724968 DE3724968A1 (de) 1987-07-28 1987-07-28 Axialkolbenmaschine mit einem radial gelagerten schiefscheibenkoerper
DE3724968 1987-07-28

Publications (3)

Publication Number Publication Date
EP0301229A2 EP0301229A2 (fr) 1989-02-01
EP0301229A3 EP0301229A3 (en) 1989-08-30
EP0301229B1 true EP0301229B1 (fr) 1991-04-03

Family

ID=6332529

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88109855A Expired - Lifetime EP0301229B1 (fr) 1987-07-28 1988-06-21 Machine à pistons axiaux avec disque oblique à paliers radiaux

Country Status (2)

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EP (1) EP0301229B1 (fr)
DE (2) DE3724968A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6354186B1 (en) 1998-12-08 2002-03-12 Caterpillar Inc. Hydrostatic thrust bearing for a wobble plate pump

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1409274A (fr) * 1964-04-28 1965-08-27 Perfectionnements aux pompes hydrauliques
US3726609A (en) * 1970-01-30 1973-04-10 Applied Power Ind Inc Load controller
FR2205943A5 (fr) * 1972-11-08 1974-05-31 Leduc Rene Fils Ets

Also Published As

Publication number Publication date
DE3862256D1 (de) 1991-05-08
EP0301229A2 (fr) 1989-02-01
EP0301229A3 (en) 1989-08-30
DE3724968A1 (de) 1989-02-09

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