EP0309762B1 - Machine à piston axial réglable du type à plateau incliné - Google Patents

Machine à piston axial réglable du type à plateau incliné Download PDF

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Publication number
EP0309762B1
EP0309762B1 EP88114329A EP88114329A EP0309762B1 EP 0309762 B1 EP0309762 B1 EP 0309762B1 EP 88114329 A EP88114329 A EP 88114329A EP 88114329 A EP88114329 A EP 88114329A EP 0309762 B1 EP0309762 B1 EP 0309762B1
Authority
EP
European Patent Office
Prior art keywords
housing
support surface
axial piston
piston machine
tilting body
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
EP88114329A
Other languages
German (de)
English (en)
Other versions
EP0309762A2 (fr
EP0309762A3 (en
Inventor
Josef Ing. Grad. Riedhammer
Horst Dipl.-Ing. Deininger
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.)
Linde GmbH
Original Assignee
Linde 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 Linde GmbH filed Critical Linde GmbH
Publication of EP0309762A2 publication Critical patent/EP0309762A2/fr
Publication of EP0309762A3 publication Critical patent/EP0309762A3/de
Application granted granted Critical
Publication of EP0309762B1 publication Critical patent/EP0309762B1/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
    • F01B3/10—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

  • Adjustable swash plate type axial piston machine Adjustable swash plate type axial piston machine.
  • the invention relates to an adjustable swash plate type axial piston machine with a cylinder drum which can be rotated in a housing coaxially to the axis of rotation of the machine and which has a plurality of cylindrical longitudinal bores with pistons, the pistons being operatively connected to an active surface of a swivel body, the swivel angle of the swivel body using an adjusting device can be changed relative to the axis of rotation of the machine and the pivoting body is supported with its support side opposite the active surface on a support surface in the housing.
  • Such axial piston machines are known.
  • the support side of the swivel body is semi-cylindrical and is supported in a hollow cylindrical support surface with the same radius in the housing.
  • the swivel movement of the swivel body takes place about a fixed swivel axis.
  • the pivoting movement is either made possible by a plain bearing or it is carried out with the help of rolling elements which are located between the Support side of the swivel body and the support surface of the housing are.
  • a disadvantage of such constructions is the large axial length of the machine caused by the semi-cylindrical design of the swivel body.
  • the use of material that supports the sliding movement and hydrostatic relief is also necessary.
  • the design with rolling elements between the bearing surfaces also increases the axial dimensions.
  • EP-A 0 163 995 describes a hydrostatic axial piston machine, the swash plate of which is pivotally mounted about a swivel axis in a swivel bearing, which is supported by two balls lying one behind the other along the swivel axis, in spherical recesses of the cup-shaped housing part and in spherical recesses of the swash plate consists.
  • This axial piston machine has the disadvantage that high sliding friction occurs when changing the swivel angle of the swash plate at the bearing points, which must be reduced by hydrostatic relief and the use of material with a low coefficient of friction in order to keep the actuating force low.
  • the invention has for its object to provide an axial piston machine of the type mentioned, which has short axial dimensions and avoids sliding movements in the swivel body bearing when changing the swivel angle of the swivel body.
  • This object is achieved in that the support side of the swivel body and the support surface in the housing have interacting contours that generate rolling movements of the swivel body relative to the support surface when the actuating device is actuated.
  • the pivot axis of the swivel body does not remain stationary, but moves on a path that is determined by the contour of the support surface in the housing and by the contour of the rolling path. It is therefore possible to design the swivel body as a flat disk, which is supported axially with the contours on the support side directly on corresponding contours in the support surface of the housing, with the interposition of rolling bodies or the structural design as a plain bearing being omitted.
  • An axial piston machine according to this construction then builds in the axial direction almost as short as the known constant machines, in which the active surface, which is inclinably adjustable to the axis of rotation of the machine, is formed on the inside of the housing. Nevertheless, such an axial piston machine according to the invention has the lowest possible bearing friction, namely rolling friction, when adjusting the swivel body.
  • guide devices for supporting the torque generated by the pistons are provided on the support side of the swivel body and on the support surface in the housing, which cooperate and guide the rolling movement in such a way that sliding movements between the support side of the swivel body and the support surface can be prevented in the housing.
  • the guide device can be designed as a toothing, preferably as an involute toothing. However, other types of toothing or other form-fitting means can also be provided, which prevent sliding of the swivel body relative to the housing and ensure a rolling movement.
  • the interacting teeth or guide devices are preferably located on the outer circumference of the support side and support surface.
  • the position of the rolling contour When used as a motor, the position of the rolling contour will be selected so that the resulting piston forces are pressed in the direction of the maximum swivel angle in all operating states and in the entire swivel range of the swivel forces.
  • the actuating device then acts in the direction of a small swivel angle.
  • a spring return or swing-out control piston can be omitted with this type. If the actuator fails, the Motor automatically on large swivel angle and develops the greatest torque.
  • the rolling contour can be placed so that the swivel plate always tends to the maximum swivel angle or always to the zero position.
  • the adjustable axial piston machine has a swivel body that can be moved from the zero stroke position of the machine to two opposite sides
  • at least one contour is assigned to each of the two swivel directions starting from the zero stroke position and the contours are parallel are spaced axially symmetrical to each other and to the axis of rotation of the machine in the zero stroke position.
  • Figure 1 shows the basic structure of the hydrostatic axial piston machine according to the invention.
  • An input or output shaft 2 is rotatably mounted in a housing 1.
  • a cylinder drum 3 with a plurality of cylindrical longitudinal bores 4, in which pistons 5 are displaceable, is firmly connected to the shaft 2, for example by toothing or similar means.
  • the longitudinal bores 4 are connected by bores 6 to a control mirror 7 and liquid supply and liquid discharge channels, not shown here, in a control floor 8.
  • the pistons 5 are formed at their ends protruding from the longitudinal bores 4 as ball heads 9, which are received in corresponding recesses in sliding shoes 10.
  • the slide shoes 10 support hydrostatically relieved on an active surface 11 of a swivel body 12 which is stationary with respect to a rotational movement of the cylinder drum 3 connected to the shaft 2 and its piston 5, so that there is a relative movement between the slide shoes 10 and the swivel body 12.
  • the slide shoes 10 are held in contact with the active surface 11 by a hold-down plate 13.
  • piston strokes are generated within the cylindrical longitudinal bore 4 when the shaft 2 is driven, that is to say during pump operation, with the result that fluid is displaced or sucked in and pressure is generated.
  • the swivel angle can be set as desired between the maximum position, that is, the swivel body position with maximum deflection of the swivel body 12, and the zero stroke position, that is, the position in which the swivel body 12 and its active surface 11 are perpendicular to the axis of rotation of the shaft 2.
  • a ring-shaped actuating device consisting of a bushing 14 which is displaceably mounted in the inner bore of the housing 1 and a sealing ring 15 which is supported against the control base 8. Between the bushing 14 and the sealing ring 15 there is a space 16 into which pressurized fluid passes , whereby the bush 14 is pushed out of the sealing ring 15 away from the inner bore of the housing 1.
  • This bushing 14 is articulated to the swivel body 12 with the aid of means not shown in the drawing and therefore moves it in the direction of the zero stroke position.
  • the counter movement of the bushing 14 or the swivel body 12 is advantageously achieved in that the swivel body mounting is carried out eccentrically, because then, due to the lever ratio present, the swivel body 12 swings back automatically as a result of the piston forces originating from the pistons 5.
  • the swing back movement can also be assisted by spring force or hydraulically.
  • the swivel body 12 is supported with its contour 18 formed on the support surface 17 opposite the active surface 11 on a support surface 19 in the housing 1.
  • the support surface 19 can be molded directly into the housing 1 or, as in the drawing, part of a component 20 integrated into the housing 1, which has the shape of a radially halved annular disk.
  • the contour 18 is convex, partially cylindrical, although other convex contours can also be provided. It consists of two individual contours with a common cylinder axis, which are located at a radial distance from the central axis of the annular disk-shaped swivel body 12 on both sides of the shaft 2 and each extend radially outwards starting at the inner diameter of the swivel body 12.
  • the counter contour interacting with the contour 18 on the support surface 19 of the component 20 is a flat surface located perpendicular to the axis of rotation of the shaft 2.
  • the part of the swivel body 12 located in the drawing below the axis of rotation of the shaft 2 is chamfered on the support surface 17, so that for this reason and because of the space available at this point, which results from the use of the described component 20, a swivel movement of the swivel body 12 is made possible with the same swivel angle as in the machines of the known prior art.
  • the support surface 17 lies in this area with maximum deflection of the swivel body 12 in a plane-parallel manner on the inside of the housing. This makes it possible to limit the swivel angle in a simple manner.
  • the flat construction of this construction is particularly advantageous, as it builds only insignificantly longer than the so-called constant machine in swash plate construction.
  • a tooth 21 is provided on the support side 17 on the outer circumference of the annular disk-shaped swivel body 12 as an extension of the common cylinder axis of the two convex, partially cylindrical individual contours, which in the opposite flanks 22 , 23 engages a tooth gap on the support surface 19.
  • This interacting toothing is designed as an involute toothing.
  • the teeth 21 on the support side 17 of the swivel body 12 are, as it were, teeth of a gearwheel, while the tooth flanks 22, 23 on the support surface 19 of the component 20 represent a tooth gap with the straight flanks of a rack.
  • the movement of one such a gear along a rack produces a rotation of the gear with simultaneous linear displacement of the gear axis parallel to the rack.
  • the illustrated cooperating toothing prevents displacement of the swivel body 12 relative to the support surface 19 and thus ensures a precisely defined rolling motion.
  • FIG. 4 shows a development of an axial piston machine in which, in contrast to the machine shown in the previous figures, the swivel body 12 can be swiveled to two sides.
  • Each swivel direction is assigned a contour 18a or 18b, which is attached to the support side 17 of the swivel body 12.
  • the contour 18a is hidden in the figure by the toothing means 21, 22 and 23 already known from the other representations, which ensure the rolling movement of the swivel body 12 on the component 20 under all conditions. If the swivel body 12 is deflected clockwise, a rolling motion takes place with the aid of the contour 18b.
  • the toothing means (not shown in this view) belonging to the contour 18b prevent a sliding movement.
  • the actuating device is designed in the machine shown such that the bushing 14 can both extend and retract depending on the pressurization from the inner bore of the housing 1 and thereby enable a deflection of the swivel body 12 to two opposite sides.
  • the sealing ring 15 serves as a stop, which is attached to the inner bore of the housing 1 in a non-positive or positive manner by conventional means. It is sufficient to effect only the swiveling movement starting from the zero stroke position by actuating the actuating device.
  • the pivoting back movement takes place through the self-pivoting forces which, because of the eccentric mounting of the pivot body 12, always act towards the zero stroke position.

Landscapes

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

Claims (5)

1. Machine à piston axial réglable du type à plateau incliné comprenant un tambour cylindrique susceptible de tourner dans un carter, coaxialement à l'axe de rotation de la machine, qui présente plusieurs alésages longitudinaux cylindriques avec un piston chacun, lesquels pistons sont en liaison active avec une surface active d'un corps pivotant, ou l'angle de pivotement du corps pivotant peut être modifié à l'aide d'un dispositif de réglage par rapport à l'axe de rotation de la machine et ou le corps pivotant s'appuie par sa face d'appui opposée à la surface active sur une surface d'appui dans le carter, caractérisée en ce que la face d'appui (17) du corps pivotant et la surface de section (19) du carter (1) présentent des profils accouplés, qui produisent, lors de la manoeuvre du dispositif de réglage, des mouvements de roulement du corps pivotant (12) par rapport à la surface d'appui (19).
2. Machine à piston axial réglable selon la revendication 1, caractérisée en ce que se trouvent sur la face d'appui (17) du corps pivotant (12) et sur la surface d'appui du carter (1) des dispositifs de guidage (21, 22, 23) accouplés, afin de soutenir le couple de rotation produit par le piston.
3. Machine à piston axial réglable selon la revendication 1 ou 2, caractérisée en ce que les profils sur la face d'appui (17) du corps pivotant (12), qui sont en prise avec la surface d'appui (19) du carter (1), présentent une forme convexe.
4. Machine à piston axial réglable selon la revendication 3, caractérisée en ce que la surface d'appui (19) du carter (1) est disposée perpendiculairement à l'axe de rotation et est constituée par une surface essentiellement plane.
5. Machine à piston axial réglable comportant un corps pivotant selon l'une des revendications précédantes comprenant un corps pivotant se déplaçant à partir d'une position de course zéro de la machine vers deux côtés opposés, caractérisée en ce qu'il est adjoint à chacune des deux directions de pivotement à partir de la position de course zéro un profil et un dispositif de guidage et en ce que les profils sont espacés parallèlement entre eux et sont symétriques par rapport à l'axe de rotation dans la position de course zéro.
EP88114329A 1987-09-30 1988-09-02 Machine à piston axial réglable du type à plateau incliné Expired - Lifetime EP0309762B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3733083 1987-09-30
DE19873733083 DE3733083A1 (de) 1987-09-30 1987-09-30 Verstellbare axialkolbenmaschine in schraegscheibenbauweise

Publications (3)

Publication Number Publication Date
EP0309762A2 EP0309762A2 (fr) 1989-04-05
EP0309762A3 EP0309762A3 (en) 1989-11-08
EP0309762B1 true EP0309762B1 (fr) 1991-05-08

Family

ID=6337320

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88114329A Expired - Lifetime EP0309762B1 (fr) 1987-09-30 1988-09-02 Machine à piston axial réglable du type à plateau incliné

Country Status (3)

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EP (1) EP0309762B1 (fr)
JP (1) JP2721198B2 (fr)
DE (2) DE3733083A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3942189C1 (fr) * 1989-12-20 1991-09-05 Hydromatik Gmbh, 7915 Elchingen, De
DE4030545C2 (de) * 1990-09-27 1999-03-18 Linde Ag Verstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4229007C2 (de) * 1992-08-31 2002-06-13 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise
KR0135479B1 (ko) * 1994-10-01 1998-04-28 서상기 사판식 액셜 피스톤 유압펌프 및 모터의 가변용량 기구
DE19620654B4 (de) * 1996-05-22 2005-04-07 Linde Ag Verstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE10035630C1 (de) 2000-07-21 2002-03-14 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
DE10251552C5 (de) * 2002-11-05 2010-07-15 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine und Steuerplatte für eine Axialkolbenmaschine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3199461A (en) * 1963-05-27 1965-08-10 Cessna Aircraft Co Hydraulic pump or motor
US3250227A (en) * 1963-08-09 1966-05-10 American Brake Shoe Co Torque control apparatus for hydraulic power units
SE406001B (sv) * 1972-10-23 1979-01-15 Ifield Richard J Kolvpump med variabel slagvolym
US3955475A (en) * 1974-10-04 1976-05-11 Daikin Kogyo Co., Ltd. Axial piston power transmission
US4581980A (en) * 1984-05-23 1986-04-15 Brueninghaus Hydraulik Gmbh Hydrostatic axial piston machine with swivelling inclined disc
DD228599A1 (de) * 1984-11-16 1985-10-16 Umform & Plastverarb Fz Geraeuscharmer druckstromerzeuger mit foerderrichtungsumkehr in axialkolbenausfuehrung
DE3519822A1 (de) * 1985-06-03 1986-12-04 Danfoss A/S, Nordborg Einstellbare axialkolbenmaschine
DE3642203A1 (de) * 1986-12-10 1988-06-30 Linde Ag Einstellbare axialkolbenmaschine in schraegscheibenbauform

Also Published As

Publication number Publication date
DE3862730D1 (de) 1991-06-13
DE3733083A1 (de) 1989-04-13
EP0309762A2 (fr) 1989-04-05
JP2721198B2 (ja) 1998-03-04
EP0309762A3 (en) 1989-11-08
JPH01113501A (ja) 1989-05-02
DE3733083C2 (fr) 1993-08-26

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