EP1510269B1 - Presse radiale pour sertir des corps creux à symétrie de rotation - Google Patents

Presse radiale pour sertir des corps creux à symétrie de rotation Download PDF

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Publication number
EP1510269B1
EP1510269B1 EP04019811A EP04019811A EP1510269B1 EP 1510269 B1 EP1510269 B1 EP 1510269B1 EP 04019811 A EP04019811 A EP 04019811A EP 04019811 A EP04019811 A EP 04019811A EP 1510269 B1 EP1510269 B1 EP 1510269B1
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EP
European Patent Office
Prior art keywords
press
radial
pressing
cheeks
press 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
EP04019811A
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German (de)
English (en)
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EP1510269A1 (fr
Inventor
Peter Dipl.-Ing. Schröck
Ursula Schröck-Horn
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Von Waitzische Beteiligungen Gbrvertreten Durch Di
Original Assignee
von Waitzische Beteiligungen GbR vertreten durch die Gesellschafter Harald v Waitz und Dr Friedrich v Waitz
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Publication of EP1510269A1 publication Critical patent/EP1510269A1/fr
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    • 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
    • B21D39/048—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 using presses for radially crimping tubular elements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/53—Means to assemble or disassemble
    • Y10T29/5367—Coupling to conduit
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/53—Means to assemble or disassemble
    • Y10T29/53987—Tube, sleeve or ferrule

Definitions

  • the invention relates to a radial press according to the preamble of patent claim 1.
  • Hollow workpieces are sleeve-shaped workpieces with outer cross sections in the form of circles and regular polygons such as six and octagonal profiles.
  • the workpiece outer surfaces can be linear, conical, cambered (barrel-shaped) or stepped in the axial direction. Such workpiece surfaces can be accommodated by appropriate design of the - preferably replaceable - pressing jaws with corresponding pressing surfaces.
  • a particular field of application for which the subject invention is particularly well suited is the connection of high-tensile metal (e.g., steel) hose fittings with flexible hose assemblies.
  • the hose consists essentially of a piece of hose, pushed over the ends of thick-walled press sleeves. In the ends nipples are plugged, which are provided with fittings, such. those with internal or external threads, flange plates, elbows, manifolds, pipe branches, etc., which protrude from the hose ends.
  • hose-pipe combinations Such complex shaped hose assemblies are also referred to as "hose-pipe combinations”. For reasons of safety and cost, their components should not be bolted together, but should be non-detachably pressed together.
  • the inner parts support the tube walls during the pressing process and then from the inside.
  • the ferrules whose shell diameter of the pressing surfaces of a pressing device are reduced to the desired final diameter, not only large pressing paths are covered, but also increase the pressing forces progressively.
  • the pressing operations in small and large series production must be carried out with high dimensional and repetitive accuracy. As hose lines with pressures of up to 1000 bar (100 MPa) and above often have to deal with safety-relevant components whose failure and failure can result in immense costs, personal injury and environmental damage.
  • US 3,744,114 is an inseparable in operation pressing tool, in which within a standing on the square, the corresponding bearing surfaces describes eight pressing surfaces are distributed in an alternating arrangement around the press axis around four outer control body and four inner dies, wherein the axes of symmetry of the outer control body Forming diagonals of the said square standing on the point.
  • the uppermost control body is rigidly connected to an upper press yoke and the lowermost control body is connected to a lower press yoke.
  • the two lateral control body are guided by two vertical plates which are fastened on one side on the press drive and on the press frame and on slots and guide pins to move the two lateral control body so that all eight pressing surfaces perform synchronous radial movements.
  • the support and movement of the inner pressing jaws takes place in that the four inner pressing jaws have at their outer ends in mirror-symmetrical arrangement to their direction of movement two control surfaces with an opening angle of 135 degrees, and that the outer control body on its inner sides each have two complementary control surfaces ,
  • This pressing tool is not divisible mainly because of the lateral one-piece control body, so that no complicated shaped and / or bulky workpieces inserted but only slender workpieces can be pushed through.
  • many radial presses operate according to the current state of the art, with the pressing tool also being designed to be divisible. But then the disadvantage occurs again. that the pressing jaws bridging the parting line and / or control body must be divided, which in turn suffers the accuracy.
  • the invention has for its object to provide a radial press of the type described above, in which the paths of all pressing surfaces even more uniform and the synchronization of the radial pressing surface movement from the beginning to the end of the pressing process is further improved, also the workpieces taken the opportunity
  • a radial press should also be able to press complex-shaped pipe bend structures at both ends of the hose lines, also such a press should also in be able to press without large expenditure on design and cost and large diameters heavy hose types with the workpieces (fittings)
  • a radial press of the type described above are created, the lower Antriebskräf te requires, is simpler in construction and has a lower number of high quality machined sliding surfaces, so that it is cheaper to produce, finally, the conditions should be created that the crimping tool in special cases also for inserting bulky hose fittings or other bulky Workpieces is
  • Qer core of the invention consists, in simple terms, in that the pressing tool with all the pressing surfaces from the beginning to the end of the pressing stroke between the pressure body and the other surrounding the pressing tool walls or sliding and supporting surfaces is included in the press yokes that There is no alternative for unauthorized movements of the pressing surfaces due to uncontrollable reaction forces of the workpiece. Even the pressure body itself, which bridges the parting line, is dependent exclusively on the movement of its control or sliding surfaces in the press yokes. In principle, it is about the rotation of the known press jaw sets with their support and sliding surfaces in the press yokes by 45 degrees.
  • the center axis M moves during the pressing process laterally about halfway in the press gap direction, while the pressure body moves on all the way in the press gap direction.
  • This entire path is just as large as the vertical path of the support body during the actual pressing process.
  • This procedure ensures that the games or lots between the press parts involved in the pressing process is minimized and despite the high pressing forces, the fittings pressed onto the hoses remain circular in cross-section. This result is not achievable in the prior art, since in this left and right of the press plane pressure bodies are arranged, while in the invention, only on one side of a movable pressure body is present.
  • the pressing tools are arranged on one side of a press frame, consisting of two tie rods, and the centroids of the wedge-shaped second sliding surfaces in the press yokes on the other side of the press frame or a plane defined by the axes of the tie rods. If the thus formed virtual mutual lever arms are at least substantially the same length, the opposing bending moments cancel on the tie rods at least largely, whereby the frictional forces are reduced and the overall construction including the drive can be performed easily.
  • FIG. 1 shows a radial press 1 with two press yokes 2 and 3 which are movable relative to one another in the direction of a plane EE in which the axes A1 and A2 of two tie rods shown in FIGS. 11, 12 and 13 lie.
  • This plane is perpendicular to the plane in Figure 1.
  • the press yokes 2 and 3 have mirror-image recesses 4 and 5, which are at least partially covered with self-lubricating lubricious coverings 6 and 7 and thereby form sliding surfaces.
  • First sliding surfaces 6a and 7a are parallel to each other and to the parting line T, but perpendicular to the plane EE. Lie on these first sliding surfaces 6a and 7a.
  • the opening angle " ⁇ " corresponds to that of the sliding surfaces 6b and 7b. If the press yokes 2 and 3 are closed by means of an idle stroke "L", the system initially moves into the position according to FIG. 2. This happens at least largely without force.
  • a wedge slope 12c on the pressure body 12 in this case prevents abutment of the support body 11 on the pressure body 12 during the closing movement.
  • the end face 12d of the pressure body 12 is formed by a lubricious lining 12e.
  • FIG. 3 shows the end position of all supporting bodies at the end of their radial pressing paths, in which the supporting bodies abut one another without joints. It is understood that in this case the workpiece axis "A" is shifted by half the pressing path in the direction of the parting line T, but this has no influence on the press result.
  • the center axis M of the pressing surfaces coincides in the end position with the workpiece axis A.
  • the pressing forces P 2 act on so-called centroid points S of the sliding surfaces 12 a and 12 b of the pressure body 12, which is shown particularly clearly in FIGS. 1 and 2, but also for the embodiments according to the remaining figures applies.
  • the support bodies 8 and 9 are screwed to the press yokes 2 and 3 ( Figures 5, 11 and 12), but they can also be integrally formed with the press yokes 2 and 3, so that the mutually parallel sliding surfaces 6a and 7a can be kept shorter in accordance ,
  • the essence of the invention consists of enclosing the supporting bodies and the pressing surfaces connected to them in a rectangular or square space in such a way that under the action of the reaction forces of the workpiece they can not perform uncontrolled evasive movements from the exact radial synchronous movement.
  • FIG. 4 shows - in an analogous representation to FIG. 1 - a pressing jaw set 16 which contains eight radially movable pressing surfaces 17 and 18, respectively.
  • four support bodies 19, 20, 21 and 22 are again present, but each have on their inner sides in the middle of a molded projection 19 a, 20 a, 21 a, and 22 a, which encloses an angle of 45 degrees and each one of four pressing surfaces 18th wearing.
  • On both sides of the projections of all support bodies are in mirror-symmetrical arrangement (relative to the circumference) in each case two sliding surfaces 23 and 24, which enclose an angle of 135 degrees.
  • Figure 5 shows a position analogous to Figure 2, i. the die set 16 after covering the idle stroke. If the press yokes 2 and 3 are now further pushed together, the pressure body 12 is moved in the direction of the arrow 26 until the support body and the pressing jaws have reached the position according to FIG. In extension of the boundary surfaces of the gap 15 and the parting line T adjacent corners 13 of the plane E-E facing away from the support body 19 and 20 are removed (see Figures 3 and 6). FIG. 5 also shows in which way the gap 15 and the removed corners of the support bodies 19 and 20 make it possible to press hose fittings with pipe bends 29 with tight bending radii, as shown in FIG. FIG.
  • FIG. 6 shows an enlarged detail from the middle of FIG. 5, but with the die set 16 closed at the end of the radial Pressing paths of the pressing surfaces.
  • gaps S1 and S2 remain between the press yokes 2 and 3 on the one hand and the support bodies 19, 20, 21 and 22 on the other hand.
  • Both these support bodies and the pressing jaws can be provided with exchangeable pressing jaw attachments 25b made of high-strength and hardened hollow-cylinder sectors (see FIG.
  • FIG. 7 shows the end of a high-pressure hose line 27 with press-fitted hose fitting 28 and a 180-degree pipe bend 29 with connecting nipple 30.
  • the bending diameter D1 of the axis of the pipe bend 29 is relatively very small in relation to the pipe diameter D2.
  • FIG. 8 shows such a mirror-symmetrical pressing jaw 25 enlarged in comparison with FIG. 6, which has a base jaw 25a and a pressing jaw attachment 25b.
  • the two common radial outer surfaces 33 enclose an angle of 45 degrees.
  • Between these outer surfaces 33 are sliding surfaces 34 which enclose an angle of 135 degrees on both sides of an axis-parallel edge 35 and cooperate with the sliding surfaces 23 and 24 of the support body (see FIG. 4).
  • these sliding surfaces 34 can be supplemented by means of the dot-dashed lines to form a uniform octagon with corner angles of 135 degrees, which results solely from the drawing.
  • Two opposite edges 35 of two pressing jaws 25 lie in a first plane of symmetry E1, which runs parallel to the pressing direction P; two in turn opposite edges of the two other pressing jaws 25 lie in a second plane of symmetry E2, which coincides at the beginning and at the end of the pressing process with the parting line T and perpendicular to Pressing direction P runs.
  • the base jaw 25a and the pressing jaw attachment 25b are interchangeable held together by a locking pin 36 which is fixedly connected to the pressing jaw attachment 25b by a locking ring 37 frictionally held in the base jaw 25a.
  • the complete radial press 1 is usable in still space conditions, i. the pressing direction P may be vertical or horizontal.
  • the following figures show embodiments with a vertical course of the pressing direction P. This is also a possibility for all embodiments according to FIGS. 1 to 3 and 4 to 8 and 10.
  • FIG. 9 shows, in accordance with FIG. 6, that both the support bodies 19, 20, 21 and 22 and the pressing jaws 25 (shown hatched) can carry pressing jaw attachments which, in the closed position including their pressing surfaces, complement one another on the circumference shown alternately hatched.
  • FIG. 10 shows that the protrusions 19a, 20a, 21a and 22a according to FIG. 4 can be replaced by pressing jaws 25 according to FIGS. 8 and 9, whereby a ring of eight identical pressing jaws 25 according to FIG. 8 is formed on the circumference.
  • the four lying in the diagonal radial planes of symmetry SE pressing jaws rest stationary on the support surfaces, the alternately arranged therebetween pressing jaws perform during the pressing stroke sliding movements on the support surfaces.
  • FIG. 11 now shows, in conjunction with FIG. 13, a completion of that of FIG. 4:
  • the upper movable press yoke 2 has on both sides a respective arm 38, each with an internal thread 39, into which a vertical tie rod 40 or 41 is respectively screwed.
  • the lower stationary press yoke 3 also has on both sides each have a boom 42 with each a bore 43 by means of which the upper press yoke 2 by means of tie rods 40 and 41 is vertically movable.
  • both press yokes 2 and 3 on both sides guide plates 44 and 45 are screwed, which enclose the recesses 4 and 5 between them, likewise the pressure body 12 in the closed position of the radial press 1.
  • the upper guide plates 44 each have a downwardly open partial arc-shaped cutout 46th , behind which the two upper support body 19 and 22 are arranged. The displaceability of the left support member 22 is ensured by a screw 47 in a horizontal slot 48.
  • the lower guide plates 45 each have an open upwardly part circular arc-shaped cutout 49, behind which the two lower support body 20 and 21 are arranged.
  • the displaceability of the left lower support body 21 is ensured by a screw 50 in a horizontal slot 51.
  • the pressure body 12 is guided on each side by a screw 52 in a slot 53 whose longitudinal axis extends at the same angle as the sliding surface 12a of the pressure body 12. In this way, an unwanted tilting or lifting of the pressure body 12 is prevented.
  • two annular sectors 54 and 55 are screwed on both sides and mirror symmetry to the plane E1, which leave an opening angle of 225 degrees at the top and prevent the pressing jaws 25 from falling out.
  • FIG. 12 differs from that of FIG. 11 in that here an asymmetrical pressure body 60 is used whose sliding surface 60a extends at an angle " ⁇ " of 45 degrees to the parting line T or to the horizontal. The same applies to the slot 61 under the screw 62.
  • the upper sliding surface 60b of the pressure body 60 also extends parallel to the parting line T as the sliding surface 63 in the upper press yoke.
  • FIG. 13 applies to FIGS. 11 and 12, in each case viewed from right to left. Particular attention should be paid here to the press drive 64 and its control.
  • a cylinder 65 presses with a piston 66, the piston rod 67 is screwed to a movable cross member 68 which connects the lower ends of the tie rods 40 and 41 together.
  • the lower press yoke 3 is placed on a base 69.
  • a hydraulic unit 70 consisting of a high pressure pump 71, a pump motor 72 and an oil pan 73 is shown only very schematically, as known per se.
  • an adjusting screw 74 and a limit switch 75 are provided for limiting the vertical stroke of the upper press yoke 2.
  • the final pressing diameter is reached here, and the limit switch 75 passes its signal via a control line 76 to a control valve 77 on.
  • the oil flow of the high-pressure pump 71 is fed to the lower annular surface of the piston 66 in order to raise the traverse 68.
  • This lifting movement is terminated by the limit switch 78 with the adjusting screw 79, whose signal is also fed via a line 80 to the control valve 77.
  • the radial press 1 is now in its starting position according to FIGS. 9, 10 and 11.
  • the edge length K in which the guide or sliding surfaces are. in a sense "on top”, ie the diagonal surfaces F1 and F2 of the pressing jaw insert run parallel and perpendicular to the plane EE. in the Tie rods lie.
  • the area diagonal F2 also coincides with the parting line T.
  • the mass M1 and M2 also grow by at least 1.4 times and thus also the mass M3 for the minimum distance of the axis of the elbow 29 from the center axis A of the pressing jaw insert, so that only elbows with a significantly greater bending radius can be processed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Automatic Assembly (AREA)

Claims (22)

  1. Presse radiale (1) adaptée pour sertir des pièces de travail creuses, en particulier des accessoires de tuyauterie (28), comportant un dispositif de sertissage avec des mâchoires de sertissage (2, 3) mobiles l'une par rapport à l'autre, un entraînement de sertissage (64) présentant une direction de sertissage déterminée (P) et un ensemble de mors (14, 16) qui constituent un outil de sertissage comprenant au moins quatre surfaces de sertissage (8a, 9a, 10a, 11a, 17, 18) disposées de façon mobile par rapport à un axe de la pièce de travail (A) dans leur pièce de support (8, 9, 10, 11 ; 19, 20, 21, 22 ; 81, 82, 83, 84), dans laquelle les mâchoires de sertissage (2, 3) comportent chacune un évidement (4, 5) de part et d'autre d'un plan de séparation (T) perpendiculaire à la direction de sertissage (P), lesdits évidements présentant des surfaces de glissement primaires (6a, 7a) sur lesquelles sont agencées de façon coulissante au moins deux pièces de support (8, 9, 10, 11 ; 19, 20, 21, 22 ; 81, 82, 83, 84) opposées par rapport au plan de séparation (T),
    caractérisée en ce que
    a) les surfaces de glissement primaires (6a, 7a) des pièces de support coulissantes (10, 11) sont agencées parallèlement les unes aux autres et perpendiculairement à la direction de sertissage (P), moyennant quoi les surfaces de glissement primaires (6a, 7a) constituent un quadrilatère de guidage,
    b) deux des pièces de support opposées (10, 11) coulissant en direction des surfaces de glissement parallèles (6a, 7a) peuvent entrer en connexion avec une pièce de sertissage (12, 60) en forme de coin et pouvant se déplacer parallèlement au plan de séparation (T), moyennant quoi la pièce de sertissage (12, 60) est montée entre deux surfaces de glissement secondaires (6b, 7b) dans les évidements (4, 5), ces surfaces de glissement secondaires (6b, 7b) constituant entre elles un angle "α" choisi de telle sorte que la course de la pièce de sertissage (12, 60) parallèlement au plan de séparation (T) est identique à la course de sertissage des mâchoires de sertissage (2, 3) qui lui sont perpendiculaires.
  2. Presse radiale selon la revendication 1, caractérisée en ce que, dans le cas d'une pièce de sertissage (12) en forme de coin présentant une symétrie miroir, l'angle "α" entre les surfaces de glissement secondaires (6b, 7b) et l'angle d'ouverture ("α") comporte 53 degrés et 8 minutes d'arc.
  3. Presse radiale selon la revendication 1, caractérisée en ce que, dans le cas d'un pièce de sertissage en forme de coin (60) à une seule face active, l'angle "α" entre les surfaces de glissement secondaires (60a, 63) comporte 45 degrés d'arc.
  4. Presse radiale selon la revendication 1, caractérisée en ce que les mâchoires de sertissage (2, 3) sont disposées entre deux barres de liaison parallèles (40, 41) auxquelles est fixée une des mâchoires de sertissage (2), en ce que l'autre mâchoire de sertissage (3) comporte des guides pour les barres de liaison (40, 41) et en ce que les axes médians (A1, A2) des barres de liaison (40, 41) définissent un plan virtuel (E-E) d'un côté duquel est agencé l'ensemble de mors (14, 16) et de l'autre coté duquel sont agencées les surfaces de glissement secondaires (6b, 7b ; 6a, 63) et au moins une longueur de la pièce de sertissage (12, 60).
  5. Presse radiale selon la revendication 4, caractérisée en ce que l'axe médian (M) de l'ensemble de mors (14, 16) est disposé parallèlement au plan (E-E) et à une distance "a" du plan (E-E) en position fermée de l'ensemble de mors (14, 16) et en ce que les centroïdes (S) des surfaces de glissement secondaires (6b, 7b ; 60a, 63) se trouvent alors à une distance "b" du plan (E-E), moyennant quoi les distances "a" et "b", et par conséquent les moments de levier agissant sur les barres de liaison (40, 41), sont identiques ou pratiquement identiques.
  6. Presse radiale selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les pièces de support (19, 20, 21, 22) comportent chacune au milieu de leur face interne une projection conformée (19a, 20a, 21a, 22a) portant chacune l'une de quatre surfaces de sertissage (18) et étant chacune délimitée par deux surfaces latérales constituant un angle de 45 degrés d'arc, en ce qu'une surface de guidage (23, 24) est disposée de chaque côté des projections (19a, 20a, 21a, 22a), ces surfaces de guidage constituant entre elles un angle de 135 degrés d'arc, et en ce que quatre mors de sertissage additionnels (25) de même forme sont agencés en alternance entre ces projections (19a, 20a, 21a, 22a), de telle manière que l'ensemble de mors (16) comporte en tout huit surfaces de sertissage radiales identiques et à déplacement synchrone.
  7. Presse radiale selon l'une quelconque des revendications 1 à 5, caractérisée en ce que les pièces de support (81, 82, 83, 84) présentent une forme de coin et possèdent des surfaces de support (81a, 82a, 83a, 84a) disposées par paires sur leurs faces internes, ces surfaces de support constituant entre elles un angle de 135 degrés d'arc et étant disposées sur les côtés d'un octogone régulier en position fermée, et en ce que huit mors de sertissage (25) de même forme sont agencés sur ces surfaces de support de telle manière que l'ensemble de mors (16) comporte en tout huit surfaces de sertissage radiales identiques et à déplacement synchrone.
  8. Presse radiale selon la revendication 6, caractérisée en ce que les surfaces de guidage (23, 24) des pièces de support (19, 20, 21, 22) sont disposées dans une surface prismatique octogonale virtuelle dont les angles entre les côtés sont de 135 degrés d'arc, dans laquelle deux côtés opposés (35) d'une paire de mors de sertissage (25) sont disposés dans un premier plan de symétrie (E1) parallèle à la direction de sertissage (P) et dans laquelle deux autres côtés opposés (35) d'une autre paire de mors de sertissage (25) sont disposés dans un deuxième plan de symétrie (E2) parallèle au plan de séparation (T).
  9. Presse radiale selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la presse radiale (1) possède un insert de mors de sertissage divisé (14, 16).
  10. Presse radiale selon la revendication 9, caractérisée en ce que les mâchoires de sertissage (2, 3) comportent des surfaces de glissement obliques (6b, 7b) divergeant vers l'extérieur depuis l'insert de mors de sertissage (14, 16) par rapport au plan de séparation (T).
  11. Presse radiale selon la revendication 9, caractérisée en ce que l'ensemble de mors de sertissage (14, 16) est constitué de deux pièces d'ensemble de mors présentant chacune un groupe de surfaces de sertissage, l'un desdits groupes comportant trois surfaces de sertissage et l'autre desdits groupes comportant cinq surfaces de sertissage.
  12. Presse radiale selon la revendication 11, caractérisée en ce que les mors de sertissage (25) sont montés sur les pièces de support (19, 29, 21, 22 ; 81, 82, 83, 84) au moyen de secteurs annulaires (54, 55) et sont guidés lorsqu'ils se déplacent en direction radiale vers l'axe de la pièce de travail (A).
  13. Presse radiale selon la revendication 1, caractérisée en ce que la longueur de la pièce de sertissage (12, 60) en direction du plan de séparation (T) est supérieure ou égale au diamètre d'un cercle virtuel enveloppant les pièces de support (8, 9, 10, 11 ; 19, 20, 21, 22 ; 81, 82, 83, 84).
  14. Presse radiale selon la revendication 1, caractérisée en ce que la presse comporte une mâchoire de sertissage mobile supérieure (2) et une traverse (68) unies par des barres de liaison (40, 41) et en ce que l'entraînement de sertissage (64) est agencé dans un châssis (69) et agit via les barres de liaison (40, 41) sur la mâchoire mobile supérieure (2).
  15. Presse radiale selon la revendication 14, caractérisée en ce que les barres de liaison (40, 41) coulissent à travers des bras (42) disposés de part et d'autre dans la mâchoire de sertissage inférieure (3).
  16. Presse radiale selon la revendication 4, caractérisée en ce que le plan virtuel (E-E) passant par les axes médians des barres de liaison (40, 41) s'étend en direction de la pièce de sertissage (12, 60) de telle façon que les surfaces externes des barres de liaison (40, 41) ne se trouvent pas dans une ligne de vue passant à travers l'ouverture constituée entre les surfaces de sertissage des inserts de mors de sertissage (14, 16).
  17. Presse radiale selon la revendication 1, caractérisée en ce qu'une fente (15) est constituée sur la face des inserts de mors de sertissage (12, 60) opposée à la pièce de sertissage (14, 16), cette fente constituant un espace libre permettant de disposer des coudes de tuyauterie (29) avec un angle de cintrage de plus de 90 degrés d'arc.
  18. Presse radiale selon la revendication 17, caractérisée en ce que la fente (15) présente une forme de coin divergeant vers l'extérieur.
  19. Presse radiale selon la revendication 17, caractérisée en ce que les mâchoires de sertissage (2, 3) comportent des projections (2a, 3a) qui recouvrent les ensembles de mors de sertissage (14, 15) du coté opposé à la pièce de sertissage (12, 60) et présentent un biseau divergeant vers l'extérieur de manière à constituer la fente (15).
  20. Presse radiale selon la revendication 17, caractérisée en ce que les coins (13) adjacents au plan de séparation (T) des pièces de support (8, 9) opposées à la pièce de sertissage (12, 60) sont distancés pour constituer la fente (15), de telle façon que ladite fente (15) diverge ainsi vers l'extérieur.
  21. Presse radiale selon la revendication 1, caractérisée en ce que la pièce de sertissage (12, 60) est constituée d'un seul élément.
  22. Presse radiale selon la revendication 1, caractérisée en ce que la pièce de sertissage (12, 60) est constituée de plusieurs éléments.
EP04019811A 2003-08-27 2004-08-20 Presse radiale pour sertir des corps creux à symétrie de rotation Expired - Lifetime EP1510269B1 (fr)

Applications Claiming Priority (2)

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DE10339291 2003-08-27
DE10339291A DE10339291B3 (de) 2003-08-27 2003-08-27 Radialpresse zum Verpressen von rotationssymmetrischen Hohlkörpern

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EP1510269A1 EP1510269A1 (fr) 2005-03-02
EP1510269B1 true EP1510269B1 (fr) 2008-01-02

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US (1) US7043806B2 (fr)
EP (1) EP1510269B1 (fr)
AT (1) ATE382442T1 (fr)
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Also Published As

Publication number Publication date
DE10339291B3 (de) 2004-12-16
DE502004005807D1 (de) 2008-02-14
EP1510269A1 (fr) 2005-03-02
US7043806B2 (en) 2006-05-16
ATE382442T1 (de) 2008-01-15
US20050061052A1 (en) 2005-03-24

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