EP1248906B1 - Ensemble a piston pour machine a piston - Google Patents

Ensemble a piston pour machine a piston Download PDF

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Publication number
EP1248906B1
EP1248906B1 EP00951318A EP00951318A EP1248906B1 EP 1248906 B1 EP1248906 B1 EP 1248906B1 EP 00951318 A EP00951318 A EP 00951318A EP 00951318 A EP00951318 A EP 00951318A EP 1248906 B1 EP1248906 B1 EP 1248906B1
Authority
EP
European Patent Office
Prior art keywords
piston
arrangement according
joint
recess
piston arrangement
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
EP00951318A
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German (de)
English (en)
Other versions
EP1248906A2 (fr
Inventor
Josef Beck
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1248906A2 publication Critical patent/EP1248906A2/fr
Application granted granted Critical
Publication of EP1248906B1 publication Critical patent/EP1248906B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F04B1/124—Pistons

Definitions

  • the invention relates to a piston assembly according to the Preamble of claim 1.
  • a piston arrangement is described in DE 197 34 217 A1 described.
  • This known piston assembly has a Piston with a base portion of which in the an axial direction extends a hinge part and in the another axial direction a hollow cylindrical peripheral wall up extends to the front free end of the hollow piston, the encloses a cylindrical cavity in the piston. That I is in the other axial direction extending hinge part formed by a hemispherical joint recess, in the pivot ball of a shoe mounted pivotally is, with the equator of the joint recess superior Aus biologyungsrand in a the ball joint form-fitting cramped behind position is.
  • the one Guide surface forming lateral surface of the piston is up in extend the region of the recess edge, whereby the an improved guidance for the piston is achieved and on the other hand, a shorter construction for the Piston assembly and resulting also for the Achieve piston engine.
  • a piston assembly as defined in the preamble of claim 1 is e.g. from patent application EP 0 808 988 A known.
  • the invention is based on the object Piston arrangement of the type described above so to design that the length of the sliding surface is increased and a compressed dead volume is avoided.
  • the hollow piston on a ring cavity the inside through a center pin is defined, extending from the base section of the hollow piston extends to a lid, with the Peripheral wall of the piston is connected while the Ring cavity closes.
  • the forms Center pin an axial support and stabilization element, which is able to support axially on the lid and thereby the Base section significantly stabilized.
  • the base portion with a smaller axial length be formed.
  • Stabilization can also be material and weight save, which is due to the reduced longitudinal dimension of Hollow piston is conditional.
  • the generally designated 1 piston assembly comprises a Hollow piston 2, preferably made of steel, and a sliding shoe 3, preferably made of bronze or brass, by a Ball joint connection 1A with one-sided guarantee limited pivoting movements between the hollow piston 2 and the shoe 3 are pivotally connected together.
  • the Central axes of the piston 2 and the sliding block 3 are 2a and 3a.
  • the hinge 1A has a dome-shaped or spherical segment-shaped joint recess 5 with a depth a which is larger than the spherical radius r of one in it pivotally mounted joint ball 4, wherein the equator. 6 the joint recess 5 axially superior recess edge. 7 the ball joint 4 engages behind and while in this Ball ring zone convergent shape of the joint ball 4 at Maintaining a movement game at least partially can follow.
  • the axial Length b of the recess edge 7 dimensioned so long that they are in the maximum pivoting position shown in Fig. 1 itself into the corner area between the joint ball 4 and a Ball neck or a base part 8 of the shoe 3 extends.
  • the recess edge 7 towards its free end, wherein the outer circumferential surface preferably be a conical surface can.
  • the trained as an annular space cavity 9 extends from a rear base portion 11 in which the Joint recess 5 is arranged, up to a front-side end portion, which by a cover 12th is formed and preferably by a friction welding process is connected to the peripheral wall of the remaining piston part.
  • the gap existing before the friction welding process The welded parts is indicated by a dashed line clarified.
  • the annular cavity 9 surrounds a cylindrical center pin 13, which is in one piece from Base section 11 extends forward and also by Friction welding with the lid 12 or one of this receding center pin approach 14 is connected.
  • the channels 19a, 19b can in Functional operation of the hydrostatic machine Working pressure in the hydraulic medium to the recess 22nd reproduce where the hydraulic medium lubrication and the pressure is a pressure relief in a conventional manner causes.
  • the hollow piston 2 is preferably made of hardenable steel, in particular from nitriding hardenable steel.
  • nitriding hardenable steel For the purpose of Increased strength and hardness is its lateral surface preferably nitrided and hardened.
  • the present ball joint 1A is suitable for pivotable support of a piston 2 for piston engines, in particular axial piston machines, on a support surface S, where the shoe 3 rests with its foot 21.
  • An axial piston machine may be in the support surface S around the oblique surface of a so-called oblique letter act.
  • the sliding block 3 can as a final finished component produced in large numbers and for connection with the hollow piston 2 are provided.
  • the hollow piston 2 is used as a prefabricated piston blank preferably also prefabricated in large numbers and provided. In this preformation extends the recess edge 7 axially with an inner diameter d, the considering a movement play to the Diameter of the joint ball 4 or the joint recess. 5 can be adapted so that the ball joint 4 in the Joint recess 5 is inserted.
  • the order of the process steps before or after welding, namely the incorporation of the cavity. 9 the joint recess 5 and the channel 19a be arbitrary. It is advantageous the positive connection of the Joint ball 4 with the hollow piston 2 after nitriding and / or hardening and finishing the lateral surface 2c as to carry out last operation.
  • the recess edge 7 by means of a suitable heating device, e.g. in shape a suggestively illustrated heating ring 23 approximately in the width of the axial length b, heated to a temperature, in which the hardness of the material is reduced, so that too after cooling the material of the recess edge 7 with lower deformation forces can be crimped or on a temperature can be heated at which the strength of the material is reduced and the recess edge. 7 can be hot-rolled. In both cases, the Recess edge 7 with relatively small forces plastically in the illustrated in Fig. 1, the ball joint 4 positively crimping behind the form.
  • a suitable heating device e.g. in shape a suggestively illustrated heating ring 23 approximately in the width of the axial length b, heated to a temperature, in which the hardness of the material is reduced, so that too after cooling the material of the recess edge 7 with lower deformation forces can be crimped or on a temperature can be heated at which the strength of the material is reduced and the recess edge. 7 can
  • the relatively low deformation forces sure that the recess edge 7 without a mechanical Overload of e.g. made of softer material Sliding shoe 3 is deformed.
  • Heating can be by direct Heating e.g. by means of a flame or inductively by a inductive electric heater done.
  • By the Local heating of the recess edge 7 is in this Soften the hardened material and it can thus easily deformed without the rest of the area the piston 2 suffers significant hardness losses.
  • a significant advantage of the method described above is that the hollow piston 2 prior to assembly and connecting with the shoe 3 completely finished can be edited without the above Heating special measures with regard to beading would be required, such as Covering the to be deformed Ausappelungsrandes 7 during nitriding, in particular Gas nitriding, twisting already nitrided areas before the Flaring, etc.
  • Heating, Beading and cooling can be the optimal game of Ball joint 1 is very easy to adjust and also in the series production are reproduced safely.
  • the embodiment of the invention leads to a substantial stabilization of the hollow piston 2 and not only in terms of bending stresses but with respect to axial Compressive stresses, which the hollow piston 2 in particular at is subjected to a pressure stroke, in which one by the arrow 25 clarified compressive force against his work surface 26 at his free end acts from the shoe 3 in the Articulated connection 1A is included. It is the with the Arrow 27 illustrated equal and opposite directed resistance force introduced into the hollow piston 2 is against the base section 3. The base section 3 is thus the directly exposed to the compressive stresses Part of the hollow piston 2.
  • the Center pin 13 forms the Center pin 13 an axially effective support or Connecting part, which in the effectiveness of compressive forces 25, 27, the compressive stress on the base portion 3 and the Cover 12 distributed so that these parts with a lower Compressive stress can be applied. Therefore, the Base section 3 and / or the cover 12 with a smaller one axial dimension, i. be formed thinner. consequently can the hollow piston 2 or a hollow piston this second having piston engine, in particular Axial piston machine, with a correspondingly shorter Length.
  • a comparable supporting and stabilizing effect exercises the Center pin 13 even with a suction stroke of the hollow piston. 2 from, in the counter to the pressure forces 25, 27 directed Traction forces are effective at it. These traction will be through the center pin 13 both on the lid 12 and distributed on the base portion 13 and thereby in their Impact reduced.
  • the support and stabilization function of the center pin 13 is already met when the center pin 13 itself extends between the base portion 3 and the cover 12, which may be a separate component, the held between the base portion 3 and the lid 12 is.
  • the support and Stabilization function of the center pin 13 to a Compressive stress limited, since he lack of connection with the Base section 3 and the lid 12 only compressive stresses can pass on. In the presence of tensile stresses such a center pin 13 would be ineffective.
  • the Functional operation of the piston engine occurring Tensile forces are much lower during the suction stroke than at Pressure stroke, can also such a center pin 13 in the form an additional component, the functionality of the Ensure piston engine, as the risk of Overload mainly consists only at a pressure stroke.
  • a preferred production measure for the center pin 13 and the peripheral wall 15 is passing through these parts Cold or hot extrusion to produce. In such a Manufacturing process will not only provide higher strength in the Material structure of these parts achieved, but it will be through Extruding also with respect to the reason of Ring cavity 9 U-shaped fiber structures in the material created, thereby further enhancing the stability is enlarged.
  • the inventorsbeispeil of FIG. 2 in the same or comparable parts provided with the same reference numerals are different from the above Embodiment in that instead of a one-piece trained center pin 13 a two-piece educated Center pin 13 is provided by a pin or a sleeve is formed, which in axial holes 12a corresponding cross-sectional size in the base section 3 and in Lid 12 is seated and secured therein, e.g. by Welding, soldering or gluing.
  • FIGS. 3 to 5 include Embodiments, the sliding bearing of the shoe 3 improve. These measures enable, inter alia, the Body 24 of the shoe 3 from a less slippery To manufacture material, e.g. from a metal larger Strength, e.g. from steel. In contrast, it is common for the Slide shoe 3 made of copper and zinc alloys, such as e.g. To form brass or bronze. Although these materials have a good sliding property, however, is their strength relatively small and less than steel.
  • the Embodiment of Fig. 3 is the hemispherical surface the joint recess 5 through a sliding material layer 25, e.g. Brass or bronze, lined. This layer 25 extends to the equator 6 of the joint recess. 5 When the sliding material layer 25 is thicker than a film, it requires an increase in the radial dimension of the Recess 5 to the layer thickness.
  • the sliding bearing layer 25 also extends into the region of the recess edge 7 even when tensile forces on the piston assembly 1 occur a relatively low wear on the Ring-zone-shaped sliding surface of the recess edge. 7 guaranteed.
  • the recess edge 7 through the Sliding material to form and thereby is due to the lower strength of the plain bearing material in comparison to steel easier beading of the recess edge. 7 allows.
  • FIG. 5 wherein the same or comparable parts provided with the same reference numerals are, is a corresponding plain bearing layer 26 at the preferably flat foot surface 21 of the Gleitschuh stresses 24th arranged.
  • This sliding material layer 25 can over the entire surface of the foot surface 21 or only over partial surfaces, e.g. in the form of preferably concentric rings extend.
  • the Slide bearing embodiments according to Fig. 3 and / or 4 also be educated.
  • the sliding material layer 25, 26 may be a prefabricated material layer, e.g. by soldering, Welding and gluing attached to the supporting surface or it can also be a shift order, applied in a liquid or doughy state and then hardened.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (12)

  1. Structure de piston (1) pour une machine à pistons, avec un piston creux (2) et un patin de glissement (3), qui sont liés entre eux de manière orientable par une liaison à rotule (1a), formée d'une sphère d'articulation (4) et d'une cavité d'articulation (5) demi sphérique,
    un rebord de cavité (7) de la cavité d'articulation (5) dépassant de l'équateur (6) de la cavité d'articulation (5) et enserrant la sphère d'articulation (4) par codage de forme, le piston creux (2) présentant un tronçon de base (11),
    une paroi périphérique (15) qui entoure l'espace creux (9), s'étendant d'un seul tenant depuis le tronçon de base (11), en direction axiale opposée à la cavité d'articulation (5),
    l'espace creux (9) étant fermé par un couvercle (12), relié à la paroi périphérique (15), et le piston creux (2) présentant une tige centrale (13), qui s'étend d'un seul tenant du tronçon de base (11) jusqu'au couvercle (12),
    caractérisé en ce que
    la sphère d'articulation (4) est formée sur le patin de glissement (3) et la cavité d'articulation (5) est formée dans le piston creux (2), la cavité d'articulation (5) et le rebord de cavité (7) étant disposés à l'extrémité du tronçon de base (11) et la tige centrale (13) étant formée par formage plastique sur le tronçon de base (11).
  2. Structure de piston selon la revendication 1,
    caractérisée en ce que
    la paroi périphérique (15) est formée par formage plastique sur le tronçon de base (11).
  3. Structure de piston selon la revendication 2,
    caractérisée en ce que
    la tige centrale (13) et / ou la paroi périphérique (15) sont formés par extrusion, en particulier par extrusion à froid, de préférence simultanément au tronçon de base (11).
  4. Structure de piston selon l'une des revendications précédentes,
    caractérisée en ce que
    le couvercle (12) est relié à la tige centrale (13).
  5. Structure de piston selon l'une des revendications précédentes,
    caractérisée en ce que
    le couvercle (12) est relié par soudage, en particulier par soudage à friction, à la paroi périphérique (15), et de préférence, aussi à la tige centrale (13).
  6. Structure de piston selon l'une des revendications précédentes,
    caractérisée en ce que
    le rebord de cavité (7) est serti à froid ou à chaud.
  7. Structure de piston selon l'une des revendications précédentes,
    caractérisée en ce que
    le piston creux (2) et/ou le patin (3) se compose d'acier.
  8. Structure de piston selon la revendication 7,
    caractérisée en ce que
    la cavité d'articulation (5) est garnie d'une couche de matériau de glissement (25).
  9. Structure de piston selon la revendication 8,
    caractérisée en ce que
    la couche de matériau de glissement (25) s'étend jusque dans la zone du rebord de cavité (7).
  10. Structure de piston selon la revendication 9,
    caractérisée en ce que
    le rebord de cavité (7) est formé par la couche de matériau de glissement (25).
  11. Structure de piston selon l'une des revendications 7 à 10,
    caractérisée en ce que
    la surface d'appui (21) du patin glissement (3) est formée au niveau du matériau de glissement.
  12. Structure de piston selon la revendication 11,
    caractérisée en ce que
    la surface d'appui (21) est disposée au niveau d'une couche de matériau de glissement (26).
EP00951318A 1999-07-21 2000-06-29 Ensemble a piston pour machine a piston Expired - Lifetime EP1248906B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE1999134217 DE19934217A1 (de) 1999-07-21 1999-07-21 Kolbenanordnung für eine Kolbenmaschine
DE19934217 1999-07-21
PCT/EP2000/006072 WO2001007757A2 (fr) 1999-07-21 2000-06-29 Ensemble a piston pour machine a piston

Publications (2)

Publication Number Publication Date
EP1248906A2 EP1248906A2 (fr) 2002-10-16
EP1248906B1 true EP1248906B1 (fr) 2005-10-26

Family

ID=7915558

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00951318A Expired - Lifetime EP1248906B1 (fr) 1999-07-21 2000-06-29 Ensemble a piston pour machine a piston

Country Status (3)

Country Link
EP (1) EP1248906B1 (fr)
DE (2) DE19934217A1 (fr)
WO (1) WO2001007757A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102814629A (zh) * 2011-06-10 2012-12-12 罗伯特·博世有限公司 用于制造活塞的方法和用于活塞机的活塞

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DE10306792B4 (de) * 2003-01-23 2007-03-22 Valeo Compressor Europe Gmbh Kolben, insbesondere für einen Axialkolben-Verdichter, und Verfahren zur Herstellung desselben
DE102007008049A1 (de) * 2007-02-17 2008-08-21 Thyssenkrupp Vdm Gmbh Gleitender Reibung ausgesetztes Bauteil
DE102008060841B4 (de) 2008-12-05 2021-10-28 Robert Bosch Gmbh Hohlkolben für eine Kolbenmaschine
EP2466136A1 (fr) * 2010-12-15 2012-06-20 Continental Automotive GmbH Piston et pompe à pression
CN102865221A (zh) * 2012-10-07 2013-01-09 四川省宜宾普什驱动有限责任公司 一种空心柱塞
CH707789A1 (de) 2013-03-25 2014-09-30 Liebherr Machines Bulle Sa Kolben für eine Axialkolbenmaschine.
DE102013211888A1 (de) * 2013-06-24 2014-12-24 Robert Bosch Gmbh Hohlkolben für eine Schrägscheibenmaschine und Schrägscheibenmaschine
CN103711689A (zh) * 2014-01-09 2014-04-09 北京理工大学 一种空心结构高压液压泵柱塞
CH714075A1 (de) 2017-08-21 2019-02-28 Liebherr Machines Bulle Sa Verfahren zur Herstellung einer Kugel-Gelenk-Verbindung sowie Kugel-Gelenk-Verbindung.

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US3188973A (en) * 1960-04-14 1965-06-15 Council Scient Ind Res Hydraulic pumps and motors
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DE2364725C2 (de) * 1973-12-27 1985-12-12 Sundstrand Corp., 61101 Rockford, Ill. Verfahren zur Herstellung eines Kolbens
FR2532367B1 (fr) * 1982-08-24 1987-04-10 Bronzavia Sa Pompes a pistons axiaux solidaires de patins glissants sur une surface inclinee
DE4108786C2 (de) * 1991-03-18 1995-01-05 Hydromatik Gmbh Leichtkolben für hydrostatische Axial- und Radialkolbenmaschinen
US5490446A (en) * 1994-03-22 1996-02-13 Caterpillar Inc. Apparatus and method for a piston assembly
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DE19620167C2 (de) * 1996-05-20 1998-11-12 Brueninghaus Hydromatik Gmbh Hohlkolben mit radial verschweißtem Deckel
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DE19712838C2 (de) * 1997-03-26 1999-03-18 Brueninghaus Hydromatik Gmbh Verfahren zum Herstellen einer Kugelgelenkverbindung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102814629A (zh) * 2011-06-10 2012-12-12 罗伯特·博世有限公司 用于制造活塞的方法和用于活塞机的活塞

Also Published As

Publication number Publication date
DE19934217A1 (de) 2001-02-01
DE50011468D1 (de) 2005-12-01
EP1248906A2 (fr) 2002-10-16
WO2001007757A2 (fr) 2001-02-01
WO2001007757A3 (fr) 2002-08-01

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