EP1510269A1 - Radial press for pressing rotationally symmetrical hollow components - Google Patents

Abstract

Radial press (1) comprises a press frame with press yokes (2, 3) that move relative to each other, and a press drive with a press jaw assembly (14) forming a press tool. The press jaw assembly has at least four press surfaces (8a-11a) which are arranged together with their support bodies (8-11) so that they can be moved relative to a workpiece axis. Each press yoke has a recess (4, 5) with first sliding surfaces (6a, 7a) on which at least two support bodies lying opposite each other are displaceably arranged relative to a separating gap (T). The first sliding surfaces are parallel to each other and perpendicular to the press direction (P) and form a control square. Two of the support bodies interact with a wedge-shaped pressure body (12) moving parallel to the separating gap. The pressure body is mounted in the recesses between two second sliding surfaces (6b, 7b). The second sliding surfaces enclose an angle (alpha ) selected so that the path of the pressure body paralle l to the separating gap is the same length as that of the press path of the press yokes perpendicular to the separating gap.

Description

The invention relates to a radial press according to the preamble of claim 1

Under "hollow workpieces" are sleeve-shaped workpieces with external cross sections in the form of circles and regular polygons like six and one Octagonal profiles to understand. The workpiece outer surfaces can straight in the axial direction, conical, cambered (barrel-shaped) or graduated. Such workpiece surfaces can by appropriate Training of - preferably replaceable - pressing jaws be taken into account with appropriate pressing surfaces.

A special field of application for which the subject invention is particularly well suited, is the compound of high-strength metal (e.g., steel) existing hose fittings with flexible hose assemblies. The hose consists essentially of a Hose piece, pushed over the ends of thick-walled compression sleeves become. In the ends of nipples are plugged, which with fittings are provided, such as those with internal or external threads, flange plates, Pipe bends, manifolds, pipe branches, etc., from the Protruding hose ends.

Such complex shaped hose assemblies are also called "Hose-tube combinations" referred to. For safety reasons and because of the cost, their components should not be together but should be pressed together inextricably.

The inner parts, the so-called nipples, support the tube walls during the Pressing process and then from the inside. In the outer parts, the Press sleeves, whose shell diameter of the pressing surfaces a pressing device reduced to the desired final diameter, where not only large pressing paths are covered, but also the Press forces progressively increase. The press operations must be in small and large series production with high dimensional and repeat accuracy respectively. because it is the hose lines, the pressures up to 1000 bar (100 MPa) and beyond, very often safety relevant Components, their failure and failure immense Costs, personal injury and environmental damage.

In addition, such hose-pipe combinations by the constant Advances in technology become more complicated in shaping. Increasingly compacting machines and systems reduce this Installation volume of such hose-tube combinations, so that whose designers are confronted with ever new problems tightest rooms properly and perfectly functioning Install hose-pipe combinations. Modern, computer controlled Bending machines have become an indispensable aid to them, if thereby fast, precise and inexpensive complicated, several times curved pipe bends are economically produced even in small batches can. The elbows can also be those a bending angle of 180 degrees with the smallest possible bending radius have. Such bending radii are for example equal to the pipe diameter.

According to the current state of the art is a pressing of such Hose / tube combinations for the high and highest pressure range, For example, in the field of construction machinery hydraulics, not possible when the pipe and fitting parts to be pressed into the disc-shaped Protruding space around the pressing jaws or pressing tools. There namely are - due to the design - machine parts of the radial presses. These must have pressing forces up to 3500 MN, partially also about it. muster.

Taking into account the above explanations becomes the following state of the art:

By US 3,744,114 is an inseparable in operation pressing tool known in which within a standing on a square, the describes corresponding bearing surfaces, eight pressing surfaces in alternating Arrangement around the press axis around four outer control body and four inner pressing jaws are distributed, the axes of symmetry of the outer control body the diagonals of said, on the Form tip of standing square. Here is the topmost tax body rigid with an upper press yoke and the lowest control body with connected to a lower press yoke. The two lateral control bodies are guided by two vertical plates on one side on the one hand Press drive and on the other hand are fixed to the press frame and via elongated holes and guide pins, the two lateral control body should move so that all eight pressing surfaces synchronous radial movements To run. The support and movement of the inner pressing jaws takes place in that the four inner pressing jaws at their outer ends in mirror-symmetrical arrangement to their direction of movement two control surfaces each with an opening angle of 135 degrees have, and that the outer control body on their insides 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 slim workpieces can be pushed through. According to this principle, many work according to the current state of the art Radial presses, wherein the pressing tool was also carried out divisible. But then the disadvantage occurs again. that the bridging the parting line Pressing jaws and / or control body must be divided, among which again the accuracy suffers.

From EP 0 539 787 A1 and the corresponding DE 41 35 465 A1 a radial press with two press yokes and outer and inner Control bodies known, which also has eight pressing surfaces, so that a somewhat more uniform pressing process with reduced edge pressure he follows. The planes of symmetry of two of the inner, fixed position control body run in the direction of the press stroke and the symmetry planes the other two inner control body perpendicular thereto. Cover it the two last mentioned inner control body a possible Parting line of the pressing tool, which consequently also not divisible is. Such a division, the insertion of bulky hose fittings is neither described, nor intended or possible. In addition, the press jaw set of the press yokes and two tie rods of the press frame is enclosed, so too for this reason, a lateral insert bulky hose fittings is excluded.

From DE 198 14 474 C1 also a radial press is known, the pressing tool has eight pressing jaws, each with a pressing surface. However, the control surfaces in the two press yokes are multiple formed angled, and two transverse thereto movable inner control body have been replaced by four plungers, in pairs above and are arranged below a parting line to two tool halves that can be moved far apart to that To allow for bulky hose fittings. This construction However, it requires a variety of complicated shaped moving Parts with numerous sliding surfaces, which are processed high quality have to. This results in corresponding production costs. in addition also comes here that the press jaw set of the press yokes and two tie rods of the press frame is enclosed, so too For this reason, the space for a lateral insert bulkier, Angled and U-shaped bent hose fittings is missing. in the Basically, here is an irregular polygon, the control surfaces for four of the pressing jaws and for the four additional pressure pieces makes "on the top". Here, the center axis M of the pressing surfaces remains unchanged in their position. However, this requires the mutual arrangement of additional pressure bodies, which are in the direction of the press nip each half the way in the direction of the center axis M back.

From DE 199 58 103 C1 and the corresponding EP 1 106 276 A2 turn a radial press with a divisible pressing tool with eight Pressing surfaces and four control bodies known, in which the four control surfaces in the press yokes in the axial plan view in the result again by a standing on the top square or rectangle are described. As practical experiments have shown, too here absolutely synchronous ways of the pressing surfaces only with small pressing forces reachable. At higher press forces and increasing friction losses the four control bodies do not continue to drive these in sync, and the pressing jaws located in the parting line remain in the pressing path behind the press jaws arranged on both sides of the parting line. A constricting compression sleeve is a very unstable Object. For a full cylinder, with no deformation takes place, the pressing forces of the individual pressing jaws would be uniform to distribute. The disadvantage of this prior art is therefore based that the four control bodies in their pressing position only on the unstable compression sleeve positively and non-positively in connection to bring are. The accuracy of the round pressing is not sufficient as a result.

Another significant disadvantage of such divisible press systems after The prior art is based on an insufficient pressing force. Due to the divisibility of the pressing tool and the requirement of Loading the press from the side, had a so-called "open Press design ", for example with a C-shaped press frame or press frame. This design causes a very high bending moment on the yoke of the "C", due to the pressing force and the Center distance H (see for example Figure 14). Only by a heavy and costly Construction can be countered by this disadvantage.

For cost reasons, therefore compromises were made, but severely limit the nominal diameter range of the presses. Such presses have only a pressing force of a maximum of 350 kN, while comparable Presses, e.g. are executed closed by lateral tie rods, Press forces up to 1,500 kN can muster. For complicated hose-tube combinations, as they are described at the beginning, this means that e.g. only such combinations up to the nominal diameter DN 16-4SP take place can be pressed up to DN 32-4SP. So here are the Demands for high pressing forces and the possibility of lateral Inserting the workpieces diametrically opposite.

One has avoided this problem so far by narrow Pipe bends with a bending angle of more than 90 degrees to the hose line screwed on. This installation method involves leakage risks and prepares additional costs. The laying techniques of hose-pipe combinations but they have made progress, and they are demanding that these pipe bends are over 90 degrees to 180 degrees. Partially Even fastening straps were welded to the pipe bends, the to hold the whole system.

The invention is based on the object, a radial press of the beginning described genus 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 the way Differences in the movements of the individual pressing surfaces are taken by the reaction forces of surface areas of the workpieces To support (hollow body), continue to be such a radial press also be able to form complex-shaped pipe elbows on both To press ends of the hose lines, continue to be such Press also be able to work without excessive design and Cost and large diameters of heavy hose types with the Workpieces (fittings) to press, and finally a radial press the genus described above are created, the requires lower driving forces, is simpler in construction and a lesser Number of high quality machined sliding surfaces, so that it is cheaper to produce, finally, the conditions be created for the fact that the pressing tool in special cases Also for inserting bulky hose fittings or other bulky Workpieces is divisible.

The solution of this task is carried out according to the invention by the characterizing features of claim 1.

This solution fully solves the task set.

Qer core of the invention, in simple terms, is that the Pressing tool with all pressing surfaces from the beginning to the end the Presshubes between the pressure hull and the rest, the pressing tool surrounding walls or sliding and supporting surfaces in the press yokes so included is that there is no alternative for unauthorized movements of the pressing surfaces by uncontrollable Reaction forces of the workpiece gives. Also the pressure body itself, the bridging the parting line, is exclusively from the movement of his Control or sliding surfaces in the press yokes dependent. In principle, it works it is about the rotation of the known press jaw sets with their Support and sliding surfaces in the press yokes by 45 degrees.

In the subject of the application, the center axis M moves while the pressing process laterally about halfway in the press-gap direction, while the pressure body to the entire path in the press-gap direction advanced. This entire way is just as big as that vertical path of the supporting body during the actual pressing process. This procedure ensures that the games or lots are between the press parts involved in the pressing process is minimized and despite the high pressing forces the fittings pressed on the hoses in cross-section stay circular. This result is in the prior art not achievable, because in this left and right of the press level Pressure bodies are arranged, while in the invention only on one Side a movable pressure body is present.

This reduction in possible games ensures compliance with the Roundness in the press result even with hoses for very high pressures, for example, over 1000 MP, where appropriate wall thicknesses of attached fittings are deformed on the high-pressure hoses.

Due to the arrangement of the pressure hull only on one side of the Pressing tool is given the opportunity to fittings on high-pressure hoses to form, as for example, a connection pipe with have a 180 ° elbow.

In the course of the further embodiment of the invention, it is additionally of Advantage. if the pressing tools are on one side of a press frame, consisting of two tie rods, are arranged and the centroids the wedge-shaped to each other standing second sliding surfaces in the Press yokes on the other side of the press frame or one plane defined by the axes of the tie rods. If that's it formed virtual mutual lever arms at least substantially are the same length, lift the opposing bending moments on the tie rods at least largely, whereby the frictional forces be reduced and the overall construction including the Drive can be performed more easily.

Further advantageous embodiments of the subject invention result itself - either individually or in combination - from the dependent claims.

1. Die Pressenkonstruktion ermöglicht einen seitlichen Freiraum für das seitliche Einlegen sehr eng gebogener komplexer Armaturen mit Biegewinkeln von über 90 Grad.

2. Das Presswerkzeug selbst füllt nur einen schmalen, scheibenförmigen Raum aus, der von vorn, von hinten und von der Seite her frei zugänglich ist.

3. Alle Pressflächen, sei es auf den Tragkörpern, sei es auf gesonderten Pressbacken, stehen während des Pressvorgangs form- und kraftschlüssig untereinander in Verbindung, so dass ein absolut rundes Pressergebnis erzielt wird.

4. Die vom Antrieb ausgeübte Presskraft bzw. deren Reaktionskraft kann ohne schädliche Biegemomente direkt in das Pressengestell bzw. das Presswerkzeug eingeleitet werden.

5. Das Presswerkzeug ist teilbar und beliebig weit zu öffnen.

6. Die Erfindung ermöglicht auch das Verpressen von Schläuchen mit handelsüblichen Rohrkrümmern bei denen R = d ist, wobei "R" der Biegeradius und "d" der Rohr-Aussendurchmesser ist.

7. Die ersten Gleit- und/oder Stützflächen für die Tragkörper bilden ein Steuerviereck, dessen Seiten parallel und senkrecht zur Kraftrichtung verlaufen und das nicht - bei einer senkrechten Anordnung - "auf der Spitze steht".

8. Das Presswerkzeug ist lageunabhängig einsetzbar.

There are the following advantages overall:

1. The press design allows a lateral clearance for the lateral insertion of very tight bent complex fittings with bending angles of over 90 degrees.

2. The pressing tool itself fills only a narrow, disk-shaped space, which is freely accessible from the front, from behind and from the side.

3. All pressing surfaces, be it on the supporting bodies or on separate pressing jaws, are positively and non-positively connected with each other during the pressing process, so that an absolutely round pressing result is achieved.

4. The force exerted by the drive pressing force or its reaction force can be introduced directly into the press frame or the pressing tool without harmful bending moments.

5. The pressing tool is divisible and open as wide as you like.

6. The invention also enables the compression of hoses with commercial pipe elbows where R = d, where "R" is the bending radius and "d" is the pipe outer diameter.

7. The first sliding and / or support surfaces for the support body form a control quadrilateral, whose sides are parallel and perpendicular to the direction of force and not - in a vertical arrangement - "on top".

8. The pressing tool can be used regardless of position.

Further advantages emerge from the following detailed description.

The mass of pamphlets and then executed in practice Disclose radial presses with press yokes and pressing tools Press jaws and / or support or control body for this, the virtual Envelope surfaces form a square whose area diagonal in the Parting line between the press yokes is or runs parallel to it. The square is sort of "on top". Now that is Length ratio of the surface diagonal to the edge length 1.41. This has the decisive disadvantage that - provided divisibility of the pressing tool - After inserting the side only U-shaped bent metal fittings or their pipes are pressed with high-pressure hoses can, where the radius of curvature because of the length of the surface diagonal is correspondingly large.

Completely formed tightly curved 180 degree manifold with more attached branch lines gain but increasingly important e.g. for construction machinery such as a shovel loader with numerous moving ones Components. The said fittings partly have the appearance of Deer antlers. If subsequent welding is not possible, then So far, we have been using further fittings, the high pressures and external loads due to bending forces.

Another major disadvantage is that the pressing jaws and / or the support or control body for this rest on control surfaces, which are predetermined by the said square and the sliding surfaces at the same time for the press jaws and / or their support or control body are. On these sliding surfaces, the pressing jaws and / or the Tragoder Control body for doing their own movements, the part wanted by the driving forces of the press, but partly also undesirable by the reaction forces of the workpieces are influenced. The problems grow disproportionately with the wall thickness of the workpieces in the Usually strong-walled sleeves made of high-strength free-cutting steel. The The result is unusable non-round or oval press results. The results are not predictable.

Embodiments of the subject invention and their modes of action will be explained in more detail with reference to Figures 1 to 13; FIG. 14 shows, for comparison, a radial press according to the state of the art Technology.

Figur 1

eine Ansicht zweier Pressenjoche mit einem Presswerkzeug mit vier Pressflächen und einem symmetrischen Druckkörper in der am weitesten geöffneten Stellung,

Figur 2

eine Ansicht analog Figur 1, jedoch nach Zurücklegen des linearen Leerhubes des Presswerkzeugs,

Figur 3

eine Ansicht analog Figur 2, jedoch mit geschlossenem Presswerkzeug am Ende der radialen Presswege der Pressflächen,

Figur 4

eine Ansicht analog Figur 1, jedoch mit einer Variante des Presswerkzeuges mit acht Pressflächen,

Figur 5

eine Ansicht des Gegenstandes nach Figur 4 nach Zurücklegen des linearen Leerhubes,

Figur 6

einen vergrösserten Ausschnitt aus der Mitte von Figur 5, jedoch mit geschlossenem Presswerkzeug am Ende der radialen Presswege der Pressflächen,

Figur 7

das Ende einer Hochdruck-Schlauchleitung mit aufgepresster Schlaucharmatur und einem 180-Grad Rohrkrümmer mit Anschlussnippel,

Figur 8

einen Ausschnitt aus Figur 6 in vergrössertem Massstab,

Figur 9

einen vergrösserten Ausschnitt aus der rechten Hälfte von Figur 6 mit vier auswechselbaren identischen Pressbacken,

Figur 10

eine Variante von Figur 9 mit acht auswechselbaren identischen Pressbacken,

Figur 11

eine Vorderansicht einer stehenden Radialpresse mit den Details gemäss Figur 4 und einem symmetrisch abgeschrägten Druckkörper,

Figur 12

eine Vorderansicht einer stehenden Radialpresse mit einem asymmetrisch abgeschrägten Druckkörper

Figur 13

eine Seitenansicht der Radialpressen nach den Figuren 11 und 12 mit zusätzlichen Details über den hydraulischen Antrieb und

Figur 14

eine Radialpresse nach dem Stande der Technik zu Vergleichszwecken.

Show it:

FIG. 1

a view of two press yokes with a pressing tool with four pressing surfaces and a symmetrical pressure body in the most open position,

FIG. 2

a view similar to Figure 1, but after covering the linear idle stroke of the pressing tool,

FIG. 3

a view similar to Figure 2, but with closed pressing tool at the end of the radial pressing paths of the pressing surfaces,

FIG. 4

1 shows a view similar to FIG. 1, but with a variant of the pressing tool with eight pressing surfaces,

FIG. 5

a view of the article of Figure 4 after covering the linear idle stroke,

FIG. 6

an enlarged detail from the middle of Figure 5, but with closed pressing tool at the end of the radial pressing paths of the pressing surfaces,

FIG. 7

the end of a high-pressure hose line with pressed-on hose fitting and a 180-degree elbow with connection nipple,

FIG. 8

a section of Figure 6 on an enlarged scale,

FIG. 9

an enlarged detail from the right half of FIG. 6 with four replaceable identical pressing jaws,

FIG. 10

a variant of FIG. 9 with eight replaceable identical pressing jaws,

FIG. 11

a front view of a stationary radial press with the details according to Figure 4 and a symmetrically bevelled pressure body,

FIG. 12

a front view of a stationary radial press with an asymmetrically bevelled pressure body

FIG. 13

a side view of the radial presses of Figures 11 and 12 with additional details about the hydraulic drive and

FIG. 14

a radial press according to the prior art for comparison purposes.

1 shows a radial press 1 with two press yokes 2 and 3, which are movable in the direction of a plane E-E relative to each other, in also the axes A1 and A2 of two in FIGS. 11, 12 and 13 shown tie rods lie. This plane is perpendicular to the drawing plane in Figure 1. By a drive shown later pressing forces P generated. The press yokes 2 and 3 have mirror-image recesses 4 and 5, which at least partially with self-lubricating lubricious Coverings 6 and 7 are occupied 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 E-E. Lie on these first sliding surfaces 6a and 7a. seen in the clockwise direction, four supporting bodies 8. 9, 10 and 11, the pressing surfaces 8a, 9a. 10a and 11a bear as sectors of a cylindrical surface are formed. that of the final surface of the to be pressed Workpieces corresponds. The said support body form a Pressbakkensatz 14th

On the inclined sliding surface 7b is a symmetrically shaped wedge-shaped pressure body 12 with two sliding surfaces 12a and 12b, whose opening angle "α" 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", Thus, the system first enters the position of Figure 2. This happens at least largely free of forces. A wedge slope 12c at Pressure element 12 prevents this from abutment of the support body 11 on Pressure body 12 during the closing movement. Also, the end face 12d of the Pressure body 12 is formed by a lubricious lining 12e.

If the described system from the position of Figure 2 in that moves according to Figure 3, the pressing forces P1 and P2 increase enormously, and the sliding surfaces 6b and 7b press the pressure body 12 with its plane End face 12d (Figure 1) in the direction of the parting line T against the support body 10 and 11, whereby a lateral force PQ is generated. The reaction forces PR (Figure 2) are of overlapping projections 2a and 3a to the Press yokes 2 and 3 generated. The on the circumference of the die set 14 distributed pressing and reaction forces are at least largely identical. The displacement paths of the support body 9/10 on the one hand and 8/11 on the other hand in the direction of the tie rods against each other due the choice of the angle "α" of 53 degrees and 8 minutes (rounded) with the Movement of the support body 10 and 11 against the support body 8 and 9 in the direction of the parting line T forcibly match, so that during pressing an absolutely synchronous movement of all supporting body takes place.

FIG. 3 shows the end position of all supporting bodies at the end of their radial Pressing paths, in which the supporting bodies abut each other without joints. It It is understood that in this case the workpiece axis "A" by half the pressing path in the direction of the parting line T is shifted, but what the press result has no influence. The center axis M of the pressing surfaces falls in the end position with the workpiece axis A together.

Back to Figure 1: The pressing forces P2 engage in so-called centroids S of the sliding surfaces 12a and 12b of the pressure body 12 at which is particularly clearly shown in Figures 1 and 2, but also for the embodiments according to the remaining figures applies. The centers the force attacks of the pressing forces P1 on the pressing jaw sets 14 and 16 have a distance "a" from the plane E-E, and the centroids S of the force attacks of the pressing forces P2 have from the level E-E on the opposite side a distance "b", with particular advantage a = b is selected. This eliminates - from minor changes apart from "a" and "b" during compression - all bending moments on the tie rods in the plane E-E, so that the tie rods 40 and 41 (Figures 11 to 13) slimmer and largely only on tensile forces can be interpreted towards. The frictional forces on the tie rods are thereby drastically reduced, and tilting of the support body against each other, resulting in a significant reduction of Total weight of the radial press 1 leads.

The support members 8 and 9 are bolted to the press yokes 2 and 3 (Figures 5, 11 and 12), but they can also with the press yokes. 2 and 3 are integrally formed so that the mutually parallel Sliding surfaces 6a and 7a can be kept shorter.

Particularly advantageous in this case is also at the end of the compression remaining V-shaped gap 15 between the projections 2a and 3a the press yokes 2 and 3. This gap 15 allows the insertion of tight bent hose connections, as shown in Figure 7. In Extension of the boundary surfaces of the gap 15 are also the Parting line T adjacent corners 13 of the plane E-E facing away from the supporting body 8 and 9 removed (see also Figure 3).

The essence of the invention is the support body and the with them connected pressing surfaces in a rectangular or square Enclose space so that it is under the action of the reaction forces the workpiece no uncontrolled evasive movements of the can perform exactly radial synchronous movement.

This also applies to the following further embodiments of the invention.

FIG. 4 shows - in an analogous representation to FIG. 1 - a pressing jaw set 16, the eight radially movable pressing surfaces 17 and 18 contains. First turn four support body 19, 20, 21 and 22 are present, however on each of its inner sides in the middle a molded projection 19a, 20a, 21a, and 22a, which includes an angle of 45 degrees and each one of four pressing surfaces 18 carries. On both sides of the projections All support bodies are in mirror-symmetrical arrangement (on the circumference) each have two sliding surfaces 23 and 24, an angle of 135 degrees. Lie on these sliding surfaces 23 and 24 between each two adjacent projections 19a, 20a, 21a and 22a four mutually uniform pressing jaws 25 in - on the circumference related - alternating arrangement to the projections. The distribution is doing so made that on press yoke 2 three pressing surfaces and At the press yoke 3 there are five pressing surfaces. Further details result from FIGS. 5, 6 and 8.

Figure 5 shows a position analogous to Figure 2, i. the die set 16 after covering the idle stroke. Are the press yokes 2 and 3 now further pushed together, the pressure body 12 is in Direction of the arrow 26 moves until the supporting body and the pressing jaws have reached the position of Figure 6. In extension of the boundary surfaces of the gap 15 are also the parting line T adjacent Corner 13 of the plane E-E facing away from the support body 19 and 20 removed (see Figures 3 and 6). FIG. 5 also shows in what way the gap 15 and the removed corners of the support body 19 and 20, the pressing of hose fittings with elbows 29 with tight bending radii allows, as shown in Figure 7. From Figure 5 goes further show that the support body 19 and 20 diagonal to the pressing tool 16 aligned tension screws 31 and 32 with the press yokes 2 and 3 are releasably bolted; However, they can also be integral with these Press yokes be formed, which also for the embodiment according to the figures 1, 2 and 3 applies.

FIG. 6 shows an enlarged detail from the middle of FIG. 5. but with closed die set 16 at the end of the radial Pressing paths of the pressing surfaces. The projections 19a, 20a, 21a and 22a and the alternately arranged pressing jaws 25 (see also Figure 4) abut radial joints, in which also the press axis lies, gap-free together. To a mechanical over-determination too avoid remaining between the press yokes 2 and 3 on the one hand and the support bodies 19, 20, 21 and 22 on the other hand column S1 and S2. Either These support bodies as well as the pressing jaws can be interchangeable Press jaw attachments 25b made of high-strength and hardened hollow cylinder sectors (see Figure 8) be provided, resulting in a closed Add ring. Thus, the pressing tool 16 after relieving the Press yokes 2 and 3 are automatically reopening, are in the said radial separating joints prestressed compression springs arranged in the Figures 4 and 5, however, are only indicated.

Figure 7 shows the end of a high-pressure hose 27 with pressed on Hose fitting 28 and a 180-degree elbow 29 with Connection nipple 30. The bending diameter D1 of the axis of the elbow 29 is relatively very small in relation to the pipe diameter D2.

FIG. 8 shows such a mirror-symmetrical pressing jaw 25 FIG. 6 enlarges the one base jaw 25a and one pressing jaw attachment 25b owns. The two common radial outer surfaces 33 enclose an angle of 45 degrees. Between these outer surfaces 33 are sliding surfaces 34, which on both sides of an axis-parallel Edge 35 enclose an angle of 135 degrees and with the Sliding surfaces 23 and 24 of the support body cooperate (see Figure 4).

According to Figure 6, these sliding surfaces 34 can be by means of the dot-dash line Lines to a uniform octagon with corner angles of each 135 degrees, which results solely from the drawing. Two opposite lying edges 35 of two pressing jaws 25 are in a first Symmetry plane E1, which is parallel to the pressing direction P; two in turn opposite edges of the two other pressing jaws 25th lie in a second symmetry plane E2, the beginning and the end of the pressing process coincides with the parting line T and perpendicular to Pressing direction P runs. The base jaw 25a and the press jaw attachment 25b are interchangeable by a locking pin 36 together held firmly connected to the pressing jaw attachment 25 b by a locking ring 37 is frictionally held in the base jaw 25a.

It is understood that the complete radial press 1 in remaining space layers is usable, i. the pressing direction P can be vertical or horizontal be aligned. The following figures show exemplary embodiments 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.

Figure 9 shows, in accordance with Figure 6, that both the support body 19, 20, 21 and 22 as well as the pressing jaws 25 (shown hatched) Press jaw attachments can carry, which are in closed position including their pressing surfaces to complete a ring on the Scope is shown alternately hatched.

FIG. 10 shows that the projections 19a, 20a, 21a and 22a according to FIG 4 can replace by pressing jaws 25 according to FIGS. 8 and 9, whereby on the circumference a wreath of eight identical pressing jaws 25th is formed according to FIG. This results in four mirror-symmetric angular support body 81, 82, 83 and 84 with four pairs of support surfaces 81a, 82a, 83a and 84a, which together form a regular octagon with edge angles of 135 degrees each. The four in the diagonal radial planes of symmetry SE lying pressing jaws rest stationary on the support surfaces arranged alternately between them Pressing jaws lead during the pressing stroke sliding on the Support surfaces off. By this construction principle, the manufacturing costs can be reduce.

FIG. 11 shows, in conjunction with FIG. 13, a completion of FIG of Figure 4: The upper movable press yoke 2 has both sides ever a boom 38, each with an internal thread 39 in the one vertical tie rods 40 and 41 is 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 rod 40 and 41 is moved vertically.

On both press yokes 2 and 3 are guide plates 44 and 45 on both sides screwed on, which enclose the recesses 4 and 5 between them, likewise the pressure body 12 in the closed position of Radial press 1. The upper guide plates 44 each have one after below open partial arc-shaped cutout 46, behind which the two upper support body 19 and 22 are arranged. The displaceability of the left support body 22 is by a screw 47 in a horizontal Slot 48 guaranteed.

The lower guide plates 45 each have one up open part-arc-shaped cutout 49, behind the two lower support body 20 and 21 are arranged. The displaceability of the left lower support body 21 is by a screw 50 in a horizontal Long hole 51 guaranteed. The pressure body 12 is on each side guided by a screw 52 in a slot 53, the longitudinal axis at the same angle as the sliding surface 12a of the pressure hull 12. This will cause an unwanted tilting or lifting of the pressure hull 12 prevented. On the respective lower support body 20 and 21 are two ring sectors 54 on both sides and mirror-symmetrical to plane E1 and 55 unscrewed, with an opening angle of 225 at the top Free degrees and prevent the jaws 25 from falling out.

For the closing and pressing movements, the comments on the Figures 1 to 10. However, it should be added that for the horizontal backward movements the support body 21 and 22 prestressed compression springs Serve 56 and 57, which run parallel to the parting line T and on each one vertical extension 58 and 59 act on the support bodies. Of the Expression "supporting body" excludes the wearing of own pressing surfaces and / or the wearing of pressing jaws.

The article of FIG. 12 differs from that of FIG FIG. 11 shows that an asymmetrical pressure body 60 is used here whose sliding surface 60a is inclined at an angle "α" of 45 degrees Parting line T or to the horizontal runs. The same applies to the Slot 61 under the screw 62. The upper sliding surface 60b of the pressure hull 60 also runs parallel to the parting line T as the sliding surface 63rd in the upper press yoke.

FIG. 13 applies to FIGS. 11 and 12, in each case viewed from the right to the left. Particular attention should be paid here to the press drive 64 and its control. Press against the lower fixed press yoke 3 a cylinder 65 with a piston 66, the piston rod 67 with a movable cross member 68 is bolted to the lower ends of the tie rods 40 and 41 interconnects. The lower press yoke 3 is open a substructure 69 attached. 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.

For limiting the vertical stroke of the upper press yoke 2 are an adjusting screw 74 and a limit switch 75 are provided. The final Press diameter is reached here, and the limit switch 75 is its signal via a control line 76 to a control valve 77 on. To the switching of this control valve 77, the oil flow of the high-pressure pump 71 of the underlying annular surface of the piston 66 fed to raise the crossbar 68. This lifting movement is achieved by the limit switch 78 terminated with the adjusting screw 79, the signal also is fed via a line 80 to the control valve 77. The radial press 1 is now in its initial position according to the figures 9, 10 and 11.

With reference to Figure 14, the prior art and its disadvantages compared to the invention explained as follows:

In contrast to the invention, the square or square with the Edge length K, in which the guide or sliding surfaces lie. to some extent "on top", i. the diagonal surfaces F1 and F2 of the pressing jaw insert run parallel and perpendicular to the plane E-E. in the Tie rods lie. The area diagonal F2 also falls with the parting line T together. This also causes the mass M1 and M2 to grow at least 1.4 times and therefore also the measure M3 for the minimum distance the axis of the elbow 29 from the center axis A of the Pressbackeneinsatzes, so that only pipe elbow with much larger Bending radius can be processed. Of particular disadvantage is but the corresponding large one-sided lever arm H between the pressing force P1 and the reaction force PR, the no counter torque can be set. This in turn leads to high bending moments, the be applied to the tie rods 41, so that their cross sections must be designed larger, which in turn leads to a higher Press weight leads. In addition, in a split press tool the lying in the parting line T supporting body along the diagonal surface F2 must be subdivided, resulting in the lifting of the positive connection and led to transverse shifts and non-round press results.

Despite all such measures was previously only the pressing of Hose fittings with a maximum nominal diameter of DN 16-4SP possible. Otherwise, had on the perimeter of the die set closed presses are used, but not the pressing of valves with complicated geometries and bending angles over Allow 90 degrees. Experience with such known, one-sided open, radial presses also have to uneven, in particular oval, press results led, since the press jaws or pressing surfaces due to the reaction forces of the workpiece superimposed proper movements can execute. This means a strong restriction of use the radial press. All the disadvantages were now at a stroke eliminated by the subject invention.

While in the figures 1 to 6 and 9 to 12 of the pressure body 12 and 60, respectively is shown as one piece, it is quite possible to make it out of several Parts to be put together, provided that it is guaranteed that these parts not relative to each other - especially not in the direction of the parting line "T" - can move.

LIST OF REFERENCE NUMBERS

1

radial press

2

press yoke

2a

head Start

3

press yoke

3a

head Start

4

recess

5

recess

6

covering

6a

first sliding surface

6b

second sliding surface

7

covering

7a

first sliding surface

7b

second sliding surface

8th

supporting body

8a

Press area

9

supporting body

9a

Press area

10

supporting body

10a

Press area

11

supporting body

11a

Press area

12

pressure vessels

12a

sliding surface

12b

sliding surface

12c

sloping face

12d

Surface

12e

covering

13

corners

14

Die set

15

gap

16

Die set

17

pressing surfaces

18

pressing surfaces

19

supporting body

19a

head Start

20

supporting body

20a

head Start

21

supporting body

21a

head Start

22

supporting body

22a

head Start

23

sliding surfaces

24

sliding surfaces

25

pressing jaws

25a

base jaws

25b

Press baking unit

26

arrow

27

High-pressure hose line

28

hose fitting

29

elbow

30

nipple

31

lag screw

32

lag screw

33

outer surfaces

34

sliding surfaces

35

edge

36

Steckbolzen

37

circlip

38

boom

39

inner thread

40

tie rods

41

tie rods

42

boom

43

drilling

44

guide plate

45

guide plate

46

neckline

47

screw

48

Long hole

49

neckline

50

screw

51

Long hole

52

screw

53

Long hole

54

ring sector

55

ring sector

56

compression spring

57

compression spring

58

extension

59

extension

60

pressure vessels

60a

sliding surface

60b

sliding surface

61

Long hole

62

screw

63

sliding surface

64

press drive

65

cylinder

66

piston

67

piston rod

68

traverse

69

substructure

70

hydraulic power unit

71

high pressure pump

72

pump motor

73

oil pan

74

adjustment

75

limit switch

76

control line

77

control valve

78

limit switch

79

adjustment

80

management

81

supporting body

81 a

support surface

82

supporting body

82a

support surface

83

supporting body

83a

support surface

84

supporting body

84a

support surface

α

aperture

A

Workpiece axis

A1

Axle of the tie rod

A2

Axle of the tie rod

a

distance

b

distance

D1

Bending diameter

D2

Pipe diameter

E-E

level

E1

plane of symmetry

E2

plane of symmetry

F1

diagonal surface

F2

diagonal surface

H

lever arm

K

edge length

L

idle stroke

M

Center axis of the pressing surfaces

M1

measure

M2

measure

M3

measure

P

pressing direction

P1

pressing force

P2

pressing force

PR

reaction forces

S

Centroids

S1

gap

S2

gap

SE

symmetry planes

T

parting line

Claims (22)

Radial press (1) for pressing hollow workpieces, in particular hose fittings (28), with a press frame with relatively movable press yokes (2, 3) and a press drive (64) with a predetermined press direction (P) and a press die set forming a press tool ( 14, 16) with at least four pressing surfaces (8a, 9a, 10a, 11a, 17, 18) including their supporting bodies (8, 9, 10, 11, 19, 20, 21, 22, 81, 82, 83, 84) relative to a workpiece axis (A) are arranged to be movable, wherein the press yokes (2, 3) on either side of a pressing direction (P) perpendicular parting line (T) each have a recess (4, 5) with first sliding surfaces (6a, 7a) on which at least two support bodies (8, 9, 10, 11, 19, 20, 21, 22, 81, 82, 83, 84) lying opposite one another relative to the parting line (T) are displaceably arranged,
characterized in that a) the first sliding surfaces (6a, 7a) for the displaceable supporting bodies (10, 11) are aligned parallel to one another and perpendicular to the pressing direction (P), the first sliding surfaces (6a, 7a) forming a control quadrangle, b) two of the mutually opposite, in the direction of the parallel sliding surfaces (6a, 7a) displaceable support body (10, 11) with a wedge-shaped, parallel to the parting line (T) movable, pressure body (12, 60) can be brought into operative connection, wherein the pressure body (12, 60) between two second sliding surfaces (6b, 7b) is mounted in the recesses (4, 5), which second sliding surfaces (6b, 7b) enclose an angle "α" between them, and that the angle "α "is chosen. that the path of the pressure body (12, 60) parallel to the parting line (T) is the same size as the pressing path of the press yokes (2, 3) perpendicular thereto. Radial press according to claim 1, characterized in that the angle "α" of the second sliding surfaces (6b, 7b) and the opening angle ("α") in a mirror-symmetrical wedge-shaped pressure body (12) is 53 degrees and 8 minutes. Radial press according to claim 1, characterized in that the angle "α" of the second sliding surfaces (60a, 63) in a single-sided wedge-shaped pressure body (60) is 45 degrees. A radial press according to claim 1, characterized in that the press yokes (2, 3) are arranged between two parallel tie rods (40, 41) to which one press yoke (2) is fixed, the other press yoke (3) being guides for the tie rods (40, 41), and in that the center axes (A1, A2) of the tie rods (40, 41) span a virtual plane (EE), on one side of which the pressing jaw set (14, 16) and on the other side the second sliding surfaces (6b, 7b, 6a, 63) and at least a partial length of the pressure body (12, 60) are arranged. Radial press according to claim 4, characterized in that the center axis (M) of the pressing jaw set (14, 16) runs parallel to the plane (EE) and in the closed position of the pressing jaw set (14, 16) a distance "a" from the plane (EE). and that the centroids (S) of the second sliding surfaces (6b, 7b, 60a, 63) in this case have a distance "b" from the plane (EE), wherein the distances "a" and "b" and thus on the Tie rod (40, 41) acting leverage moments are equal or almost equal. Radial press according to one of claims 1 to 5, characterized in that the support bodies (19, 20, 21, 22) each have on their inner sides in the middle a molded projection (19a, 20a, 21a, 22a), each one of four Press surfaces (18) carries and is bounded by two side surfaces which enclose an angle of 45 degrees, that on each side of the projection (19a, 20a, 21a, 22a) each have a control surface (23, 24) is arranged at an angle of 135 4 degrees, and that between these projections (19a, 20a, 21a, 22a) four further uniform pressing jaws (25) are accommodated in an alternating arrangement with the projections (19a, 20a, 21a, 22a) such that the pressing jaw set (16) has a total of eight identical radially and synchronously movable pressing surfaces. Radial press according to one of claims 1 to 5, characterized in that the support bodies (81, 82, 83, 84) are angularly shaped and have on their inner sides pairwise support surfaces (81 a, 82 a, 83 a, 84 a) which at an angle of 135 degrees to each other and lie in the closed state on the edges of a regular octagon and that eight uniform pressing jaws (25) are arranged on these support surfaces, such that the pressing jaw set (16) has a total of eight identical radially and synchronously movable pressing surfaces. A radial press according to claim 6, characterized in that the control surfaces (23, 24) of the support bodies (19, 20, 21, 22) are within a virtual octagonal prism surface with 135 degree edge angles, with two opposite edges (35) of a pair of Pressing jaws (25) lie in a first plane of symmetry (E1), which is parallel to the pressing direction (P), wherein two further opposite edges (35) of another pair of pressing jaws (25) in a second plane of symmetry (E2) are parallel to the parting line (T) runs. Radial press according to one of claims 1 to 8, characterized in that the radial press (1) has a split pressing jaw insert (14, 16). Radial press according to claim 9, characterized. that the press yokes (2, 3). starting from the pressing jaw insert (14, 16), opposite the parting line (T) recessed and outwardly diverging inclined sliding surfaces (6b, 7b) have. Radial press according to claim 9, characterized in that the pressing jaw set (14, 16) consists of two pressing jaw set parts, each having a group of pressing surfaces, of which one group consists of three pressing surfaces and the other group consists of five pressing surfaces. Radial press according to claim 11, characterized in that the pressing jaws (25) are held on the supporting bodies (19, 29, 21, 22; 81, 82, 83. 84) by annular sectors (54, 55) and in the radial direction to the workpiece axis (A ) are movably guided. Radial press according to claim 1, characterized in that the pressure body (12, 60) in the direction of the parting line (T) has a length which is greater than or equal to the diameter of the support body (8, 9, 10, 11, 19, 20 , 21, 22; 81, 82, 83, 84) surrounding virtual enveloping circle. Radial press according to claim 1, characterized in that the press has an upper movable press yoke (2) and a traverse (68), which are connected by tie rods (40, 41), that the press drive (64) in a substructure (69) is and acts on the tie rods (40, 41) on the upper movable yoke (2). Radial press according to claim 14, characterized in that the tie rods (40, 41) are displaceably guided through mutual arms (42) on the lower press yoke (3). Radial press according to Claim 4, characterized in that the virtual plane (EE) laid through the center axes of the tie rods (40, 41) is displaced at least as far in the direction of the pressure body (12, 60) that the outer surfaces of the tie rods (40, 41 ) lie outside a line of sight that passes through the opening between the pressing surfaces of the pressing jaw sets (14, 16). Radial press according to claim 1, characterized in that on the pressure body (12, 60) facing away from the pressing jaw sets (14, 16), a gap (15) is formed, which has a free space for the insertion of elbows (29) with a bending angle of more than 90 degrees. Radial press according to claim 17, characterized in that the gap (15) has an outwardly diverging wedge shape. Radial press according to claim 17, characterized in that the press yokes (2, 3) have projections (2a, 3a) which engage over the pressing die sets (14, 15) on the side facing away from the pressure body (12, 60) and for the purpose of forming the gap (FIG. 15) are tapered outwards diverging. Radial press according to claim 17, characterized in that the parting line (T) adjacent corners (13) of the pressure body (12, 60) facing away from the support body (8, 9) to form the gap (15) are removed, such that the gap (15) is formed by diverging to the outside. Radial press according to claim 1, characterized in that the pressure body (12, 60) is integrally formed. Radial press according to claim 1, characterized in that the pressure body (12, 60) is composed of several parts.

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