EP0239875B1 - Presse radiale - Google Patents

Presse radiale Download PDF

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Publication number
EP0239875B1
EP0239875B1 EP87103930A EP87103930A EP0239875B1 EP 0239875 B1 EP0239875 B1 EP 0239875B1 EP 87103930 A EP87103930 A EP 87103930A EP 87103930 A EP87103930 A EP 87103930A EP 0239875 B1 EP0239875 B1 EP 0239875B1
Authority
EP
European Patent Office
Prior art keywords
control
press
jaws
radial
bodies
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
EP87103930A
Other languages
German (de)
English (en)
Other versions
EP0239875A2 (fr
EP0239875A3 (en
Inventor
Peter Dipl.-Ing. Schröck
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.)
Uniflex Hydraulik GmbH
Original Assignee
Uniflex Hydraulik 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 Uniflex Hydraulik GmbH filed Critical Uniflex Hydraulik GmbH
Priority to AT87103930T priority Critical patent/ATE81311T1/de
Publication of EP0239875A2 publication Critical patent/EP0239875A2/fr
Publication of EP0239875A3 publication Critical patent/EP0239875A3/de
Application granted granted Critical
Publication of EP0239875B1 publication Critical patent/EP0239875B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B7/00—Presses characterised by a particular arrangement of the pressing members
    • B30B7/04—Presses characterised by a particular arrangement of the pressing members wherein pressing is effected in different directions simultaneously or in turn
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • B21D39/046—Connecting tubes to tube-like fittings

Definitions

  • workpiece shapes are to be provided with circular cross sections and cross sections in the form of regular polygons, as can be found, for example, in hexagonal or octagonal profiles.
  • the workpiece outer surfaces can be straight, cambered (barrel-shaped) or stepped in the axial direction. Such workpiece surfaces can be taken into account by appropriate design of the press jaws.
  • a special field of application, for which the subject matter of the invention is preferably suitable, is the connection of hose fittings made of steel with flexible hose lines and the production of so-called rope thimbles.
  • both the control surfaces of the pressing jaws and the control surfaces of the control bodies are conical surfaces or cutouts from these conical surfaces, ie the generatrices of the control surfaces are surface lines of these conical surfaces.
  • the control surfaces of the press jaws are cutouts from truncated cone surfaces, the base surfaces of the same size are identical.
  • two intersecting surface lines of these conical surfaces form a wide-open "V" whose bisector is exactly radial to the axis A of the press and the workpiece.
  • one of the two control bodies is mounted in a stationary manner, and the other control body is displaced in the axial direction against the stationary control body by a hydraulic drive. Due to the above-mentioned design of all control surfaces, the pressing jaws cover exactly half of the path in the axial direction through which the movable control body travels. It goes without saying that a precisely flat contact between the respective interacting control surfaces is only possible in a single, very specific axial position with respect to one another. On this side and beyond this two-dimensional contact, contact takes place only along a central surface line of the control surface of the press jaw or along the two outermost longitudinal edges of the control surface of the respective press jaw.
  • control surfaces are usually hardened. This requires either the use of house made of hardenable materials or the use of such materials that can be hardened by a so-called application process by diffusion processes at high temperatures in the surface area.
  • the heat treatment required in any case regularly leads to a distortion of the workpieces, which must be limited to a minimum by complex construction measures, the distortion which cannot be completely avoided being compensated for by grinding to measure.
  • Such materials, their manufacturing and processing methods are expensive and complex and yet do not always lead to the desired success.
  • the disadvantage of using tapered control surfaces is that the press jaws have a tendency to be distributed non-uniformly on the circumference of the workpiece, so that the so-called press center, i.e. the sum of the vectors of all individual forces no longer corresponds to the press axis. This also leads to non-uniform results.
  • the return springs usually used for spreading the press jaws cannot prevent the non-uniform distribution of the press jaws.
  • the usable stroke is smaller when pressing jaws are loaded on one side by a control body, because the pressing jaws are stressed by the wandering force application of the control body to tilting, so that a greater overlap of the control surfaces is required.
  • the flat control surfaces for the press jaws are formed by the surfaces of wedge-shaped bodies which alternately interlock from opposite directions and are guided in end plates of a press frame.
  • a considerable part is lost as a control surface, i.e. the pressing jaws are supported by the wedges only on a maximum of half of their outer surfaces, so that at a given pressing force at least twice the surface pressure occurs.
  • the guidance in the press frame takes place only indirectly and in the manner of a flying storage, so that the lateral guidance is only small in spite of the enormous space requirement of the arrangement.
  • the axially parallel contact surfaces for the wedges do not convey any lateral or transverse guidance to the press jaws. With the given design, it is not possible to arrange more than four pairs of control wedges or more than four press jaws around the workpiece. Finally, maintenance is also problematic, since points to be lubricated are arranged in a very hidden manner, so that the press must be at least partially disassembled for lubrication purposes only.
  • the invention is therefore based on the object of improving a radial press of the type described at the outset in such a way that its efficiency is increased, uniform pressures are made possible until the end of the pressing process and both the production and the maintenance costs are reduced accordingly.
  • the features mentioned ensure that the entire surfaces of the control surfaces of the press jaws are used at the end of the press stroke, so that the press jaws are fully supported.
  • the press jaws are guided properly in the control bodies, ie in their grooves, the bottom of which is the respective control surface forms.
  • This direct guidance of the jaws in the transverse direction serves not only to guide the jaws, but also to reliably hold the plates made of a bearing material.
  • the guidance and the transmission of the very high pressing forces is consequently possible in the smallest space, which in turn makes it possible to arrange more than four pressing jaws distributed over the circumference of the workpiece. This greatly improves the distribution of the pressing forces. It should be noted here that the flow of the workpiece that occurs during pressing is very dependent on an even distribution of the pressing forces.
  • the bearing plates simply inserted into the grooves of the control bodies eliminate all lubrication problems. If these bearing plates wear out, it is very easy to replace them with new bearing plates. No disturbing wear occurs on the other parts of the press, and cheaper, non-hardened materials can be used, so that there is no delay in hardness.
  • the relatively lower surface pressure compared to the conditions according to US Pat. No. 4,535,689 also leads to a further advantage, namely to the possibility of giving the control surfaces a larger angle of attack with respect to the press axis. The greater this angle of attack, the greater the radial stroke of the press jaws in the axial relative movement of the control bodies. The greater this radial stroke, in turn, the more bulky can be parts that are placed in the press, e.g. Faucets with complicated shapes, elbows or the like.
  • control surfaces interacting in pairs are arranged mirror-symmetrically with respect to a radial plane E lying between the control bodies. This makes it possible to achieve a short axial length of the entire press despite a large radial stroke of the press jaws.
  • This advantage is particularly important in connection with the hose presses described at the outset, because with these either because of the complicated shape of the fittings and / or because of the need to press individual hose sections with fittings into "endless lines", a correspondingly large amount of free space behind radial and axial direction is required. The shorter the press, the more universally it can be used.
  • the plates that can be used consist of a bearing material with self-lubricating properties.
  • a bearing material is commercially available under the name "KS-DU” in the form of multilayer plates or strips, for example under license from the company Glacier Metal Company Limited / Great Britain.
  • Such plain bearing plates have an extremely low coefficient of friction of 0.02. As a result, the friction losses are only a maximum of about 5% compared to 30% in conventional designs, so that the driving forces can be reduced, without reducing the closing force of the press tool.
  • a hose press equipped with such bearing plates is practically maintenance-free, since the self-lubricating bearing material eliminates the need to relubricate the highly stressed surfaces.
  • the plates made of bearing material have angled flanges in the axial direction on both sides of the supporting part for gripping over the radial end faces of the control bodies. Such plates can then simply be inserted into the press between the control surfaces. It is then only necessary to screw through the angled flanges.
  • the construction of the radial press according to the invention enables the slope of the control surfaces with respect to the press axis to be increased considerably compared to conventional constructions, for example from about 10 degrees to over 20 degrees. Even an increase in the control surfaces of 26.5 degrees has proven to be feasible in one embodiment.
  • Such a large slope leads, given the axial displacement path of the control bodies relative to one another, to a correspondingly large radial stroke of the press jaws, and this in turn is decisive for the insertion of workpieces with a complicated shape, for example in the case of curved fittings. For this there is a corresponding at the radially outer end of the press jaw stroke large idle stroke required.
  • radial presses with composite control surfaces of different pitch have already been created in the prior art, but their manufacture is very cost-intensive. This design effort can also be avoided by the subject matter of the invention.
  • the hydraulic drive device 3 consists of two or four hydraulic cylinders 4, which are supported on the control body 2, and pistons 5 and piston rods 6, which simultaneously act as tie rods and are firmly connected to the control body 1 via screws 7. If a hydraulic fluid is conveyed into the hydraulic cylinders 4 to the left of the piston 5, the control body 2 shifts to the left in accordance with the delivery capacity of the hydraulic unit (not shown) until the end position shown in FIG. 2 is reached.
  • the piston rods 6 are guided as guide elements through the movable control body 2, which is equipped with bearing bushes 8 at the penetration points of the piston rods.
  • the control bodies 1 and 2 are mirror-symmetrical with respect to a radial plane of symmetry E-E between them, including the control surfaces described in more detail below.
  • the control body 1 and 2 which consist of a cast iron alloy and are designed as plane-parallel plates with a square outline, have an insertion opening 9 or a push-through opening 10, the envelope surface of which is in each case the outer surface of a truncated cone, the larger base surfaces of the truncated cones of the plane of symmetry EE are facing.
  • the openings 9 and 10 serve to insert or push through a workpiece 11, which consists of a hose 11a and a sleeve 11b to be pressed on, which belongs to a hose fitting with a bend 11c and a connecting nut 11d. It can be seen that the workpiece 11 is relatively bulky, so that a large opening stroke of the pressing jaws described in more detail below is required in order to be able to insert the workpiece into the press at all.
  • control surfaces 14 and 15 are flat and have a defined gradient of, for example, 26.5 degrees with respect to the axis A-A.
  • the surface normals placed through the centroids of the control surfaces 14 and 15 all intersect said axis A-A.
  • the grooves 12 and 13 have side walls 16 and 17 which run parallel with respect to a respective groove and represent guide surfaces for press jaws 18, a part of which has been omitted in FIG. 1 for the sake of clarity.
  • Each of the press jaws 18 consists of a base jaw 18a and a jaw attachment 18b (the latter shown in phantom in FIG. 1), at least the base jaws 18a being made of a cast iron alloy.
  • the pressing jaws 18 In a mirror-symmetrical arrangement to the plane of symmetry EE, the pressing jaws 18 have on their outer sides 2 control surfaces 19 and 20, which have the same pitch in the axial direction as the control surfaces 14 and 15 in the control bodies 1 and 2.
  • the control surfaces 19 and 20 can also be represented by V -form-oriented generators think, which are, however, shifted in a straight line parallel to themselves.
  • control surfaces 19 and 20 extend between two parallel lateral guide surfaces 21 and 22, of which the rear one is covered, however. With these guide surfaces, the pressing jaws 18 engage in the grooves 12 and 13, i.e. the guide surfaces bear against the side walls 16 and 17 of the grooves.
  • the guide surfaces 21 and 22 it is not necessary for the guide surfaces 21 and 22 to be stepped away from the outer surfaces of the base jaws 18a above. Rather, a stepless transition is also possible, as is shown in FIG. 2 for the lower press jaw 18 shown there.
  • plates 23 and 24 which consist of a bearing material.
  • these plates 23 and 24 have a central, load-bearing part which is delimited by plane-parallel surfaces 23a / 23b and 24a / 24b, respectively.
  • the plates 23 and 24 have angled flanges 23c and 23d or 24c and 24d in the axial direction on both sides of the supporting part. With these flanges, the plates 23 and 24 overlap the radial end faces of the control bodies 1 and 2, as shown in FIGS. 1 and 2.
  • the base jaws 18a each have a locking screw 25 in their center, with which the jaw attachments 18b are fixed interchangeably.
  • the jaw attachments 18b On the side opposite the dovetails 18c, the jaw attachments 18b have a working surface 18d which is decisive for the shaping of the workpiece and in the present case is formed by a cutout from a cylindrical surface.
  • FIG. 1 also shows that a micrometer screw 27 is attached to the control body 2 and a limit switch 28 is attached to the control body 1. As soon as the end piece 27a of the micrometer screw abuts a switching pin 28a of the limit switch, the end of the deformation is reached and the drive device 3 is stopped by the limit switch 28. Such an end position is shown in Figure 2.
  • FIG. 2 also shows that instead of pressing on a workpiece 11 with a bend 11c, it is also possible to connect a workpiece 11 to another workpiece 29, to which a hose 29a belongs, to which a sleeve 29b has previously been attached Way has been pressed.
  • FIG. 3 shows that the hydraulic drive device can optionally consist of two or four hydraulic cylinders 4, which are connected in parallel by a hydraulic line 30 and are supplied with hydraulic fluid via a connecting piece 31. It can also be seen in which way the grooves 12 are distributed equidistantly around the circumference of the insertion opening 9. Between the grooves 12 there are webs 32 which are delimited by the side walls 16 of the grooves 12. The maximum outside position of the working surfaces 18d of the pressing jaws 18 is indicated by a circle with the diameter D a , the maximum inside position, which corresponds to the final final diameter of the workpiece, is indicated by the circle with the diameter D i .
  • FIG. 3 also shows that there are 18 compression springs 33 between immediately adjacent pressing jaws, which are supported in the tangential direction against the pressing jaws 18 and, when the control bodies 1 and 2 are moved apart, the pressing jaws 18 through their radial force component into their starting position according to FIG 1 return.
  • the compression springs 33 have no influence on the position of the press jaws in the circumferential direction, since this position is determined exclusively by the side walls 16 and 17 of the grooves 12 and 13 in connection with the guide surfaces 21 and 22 on the press jaws. This can also be seen very clearly in the lower half of FIG. 3.
  • FIG. 7 also shows a microscopic image of a cross section through the plates 23 and 24 according to FIGS. 5 and 6.
  • These plates consist of a bearing back 34 made of sheet steel and the actual bearing material 35, which are bonded to one another by a copper layer 36.
  • the bearing material 35 consists of an originally highly porous tin-bronze layer 37, the spaces between which are filled with a solid mass of polytetrafluoroethylene (PTFE) with lead particles.
  • PTFE polytetrafluoroethylene
  • control surface The bottom of the grooves 12 and 13 is always referred to as the control surface.
  • control surfaces it would also be conceivable to designate the radially inwardly directed load-bearing surfaces of the plates 23 and 24 as control surfaces, especially since the surfaces mentioned are only displaced in the radial direction parallel to the thickness of the plates 23/24.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Diaphragms And Bellows (AREA)
  • Diaphragms For Electromechanical Transducers (AREA)
  • Mechanical Treatment Of Semiconductor (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Claims (6)

  1. Presse radiale pour pièces ayant une surface extérieure à symétrie de révolution, comprenant
    a) plusieurs mâchoires de pressage (18) disposées en un cercle autour de l'axe (A) de la surface extérieure de la pièce, qui sont déplaçables radialement par rapport à cet axe et dont les côtés extérieurs présentent chacun au moins deux premières faces d'attaque ou de poussée (19, 20) planes, inclinées par rapport à l'axe et disposées en V, s'étendant entre deux faces de guidage latérales (21, 22) parallèles agencées sur les mâchoires, la bissectrice du "V" étant orientée radialement et les normales aux faces de poussée passant par les centres de gravité de ces faces coupant l'axe (A),
    b) des pièces d'attaque ou de poussée (1, 2) dont les côtés intérieurs présentent chacun au moins une seconde face d'attaque ou de poussée (14, 15), également plane, coopérant avec les faces de poussée coordonnées des mâchoires, et
    c) un dispositif de commande (3) produisant la translation axiale des pièces de poussée (1, 2) l'une par rapport à l'autre
    caractérisée en ce que
    d) les secondes faces de poussée (14, 15) sont disposées en deux pièces de poussée (1, 2) réalisées sous la forme de plaques,
    e) les pièces de poussée (1, 2) sont pourvues chacune de rainures radiales (12, 13) dont le nombre correspond à celui des mâchoires (18), dont les parois latérales ou flancs (16, 17) sont parallèles et constituent des faces de guidage pour les mâchoires (18) et dont le fond, constituant la face de poussée (14, 15) de la pièce en question, est plan et présente la même pente en direction axiale que la face de poussée (19, 20) correspondante de la mâchoire (18),
    f) les faces de poussée, coopérant par paire (14, 19 et 15, 20) sont réalisées et disposées symétriquement par rapport à un plan radial (E) situé entre les pièces de poussée (1, 2) et
    g) des plaques (23, 24), faites d'un matériau pour paliers lisses, sont placées entre les faces de poussée (14, 15) des pièces de poussée (1, 2) et les faces de poussée (19, 20) des mâchoires (18), plaques dont la partie portante est délimitée par des faces planes et parallèles (23a, 23b ou 24a, 24b)
  2. Presse radiale selon la revendication 1, caractérisée en ce que les plaques (23, 24) sont faites d'un matériau pour paliers lisses ayant des propriétés autolubrifiantes.
  3. Presse radiale selon la revendication 2, caractérisée en ce que les plaques (23, 24) comportent, des deux côtés de la partie portante, en direction axiale, des bords tombés (23c, 23d ou 24c, 24d) destinés à recouvrir les extrémités radiales des pièces de poussée (1, 2).
  4. Presse radiale selon la revendication 1, caractérisée en ce que la pente des faces de poussée (14, 15; 19, 20) est d'au moins 20 degrés par rapport à l'axe (A).
  5. Presse radiale selon la revendication 1, caractérisée en ce que les pièces de poussée (1, 2) sont faites d'un alliage de fonte de fer.
  6. Presse radiale selon la revendication 1, caractérisée en ce qu'au moins les mâchoires de base (18a) des mâchoires (18) sont faites d'un alliage de fonte de fer.
EP87103930A 1986-04-04 1987-03-18 Presse radiale Expired - Lifetime EP0239875B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87103930T ATE81311T1 (de) 1986-04-04 1987-03-18 Radialpresse.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863611253 DE3611253A1 (de) 1986-04-04 1986-04-04 Radialpresse
DE3611253 1986-04-04

Publications (3)

Publication Number Publication Date
EP0239875A2 EP0239875A2 (fr) 1987-10-07
EP0239875A3 EP0239875A3 (en) 1989-08-30
EP0239875B1 true EP0239875B1 (fr) 1992-10-07

Family

ID=6297889

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87103930A Expired - Lifetime EP0239875B1 (fr) 1986-04-04 1987-03-18 Presse radiale

Country Status (4)

Country Link
US (1) US4766808A (fr)
EP (1) EP0239875B1 (fr)
AT (1) ATE81311T1 (fr)
DE (2) DE3611253A1 (fr)

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DE102017108399B4 (de) 2017-04-20 2019-05-16 Uniflex-Hydraulik Gmbh Radialpresse
DE102017119403A1 (de) 2017-08-24 2019-02-28 Uniflex-Hydraulik Gmbh Radialpressensystem
DE202017007489U1 (de) 2017-08-24 2022-02-07 Uniflex - Hydraulik GmbH Radialpressensystem
US10675838B2 (en) * 2017-11-29 2020-06-09 Fourté International, Sdn. Bhd Molding processes for metallic foams, apparatuses, and products
JP7545403B2 (ja) 2019-03-29 2024-09-04 ユニフレックス－ハイドロウリック ゲゼルシャフト ミット ベシュレンクテル ハフツング 複数の複合構造体の製造方法
CN110116384B (zh) * 2019-05-10 2021-01-01 中车青岛四方机车车辆股份有限公司 齿轮箱轴承盖组装工装及组装方法
US11203053B2 (en) 2019-10-03 2021-12-21 Shyam Newar Peripheral combination hydraulic press to forge and method of manufacturing thereof
AT523160B1 (de) 2019-12-23 2021-06-15 Gfm Gmbh Verfahren zum Bearbeiten eines im Querschnitt runden, metallischen Gießstrangs durch eine Querschnittsreduktion im Enderstarrungsbereich
DE102020121142B4 (de) 2020-08-11 2022-03-10 Uniflex - Hydraulik GmbH Radialpresse
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FI772651A (fi) * 1977-09-07 1979-03-08 Lillbackan Konepaja Maskin foer fastpressning av kopplingsstycken foer slangar
FI801834A (fi) * 1980-06-09 1981-12-10 Jorma Lillbacka Anordning foer fastpressning av kopplingsstycken foer slangar
DE3140963C1 (de) * 1981-10-15 1982-12-16 Werner 4005 Meerbusch Bothe Keilpresse für die Warm- und Kaltumformung
AT376589B (de) * 1982-02-04 1984-12-10 Karl Sauder Vorrichtung zum verpressen rohrfoermiger teile
CA1230517A (fr) * 1982-08-25 1987-12-22 Ladislao W. Putkowski Presse a coins de calage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10149924A1 (de) * 2001-10-10 2003-04-30 Uniflex Hydraulik Gmbh Radialpresse

Also Published As

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US4766808A (en) 1988-08-30
ATE81311T1 (de) 1992-10-15
DE3611253C2 (fr) 1989-03-16
EP0239875A2 (fr) 1987-10-07
DE3611253A1 (de) 1987-10-08
EP0239875A3 (en) 1989-08-30
DE3782074D1 (de) 1992-11-12

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