DE19814474C1 - Radial press tool for rotationally symmetrical workpieces - Google Patents

Abstract

The press has pressure cheeks (8a,b) with opposed press halves (1,2) having guides (5,6) with four radial guide ways (7) for the press cheeks. Control faces (9a,b) arranged inside the control bodies (3,4) for radial movement of the press cheeks. There can be eight control faces formed with sliding surfaces matching those on the cheeks.

Description

The invention relates to a radial press tool according to the preamble of Claim 1.

Under "rotationally symmetrical" are workpiece shapes with circular cross sections and understand cross sections of regular polygons as they do can be found, for example, in hexagonal or octagonal profiles. The Workpiece outer surfaces can be straight, conical in the axial direction, domed (barrel-shaped) or graded. Such Workpiece surfaces can be designed accordingly Press jaws are taken into account. A special application area for which the subject of the invention is particularly suitable is Connection of hose fittings made of metal with flexible Hose lines. The hose line consists essentially of one Hose piece is pushed over the ends of the press sleeves. In the Bores of the ends are inserted nipples, which with their Connectors z. B. with internal or external threads, flange plates,  Project elbows or the like from the end of the hose. The Inner parts, the nipples, support the hose walls during the Pressing process from the inside. For the outer parts, the compression sleeves, are whose shell diameter from the press jaws to the target Press diameter under sometimes very high radial force downsized. The pressing processes in small and Large-scale production with high dimensional and repeat accuracy take place because hose lines are very often safety-relevant Components, the failure and failure of which costs immense Damage to the environment and, not least, human life.

On radial press tools or radial presses for such applications extraordinarily high demands have to be made, some of them too lead diametrically opposed detailed solutions:

• 1. Extremely high closing and pressing forces,
• 2. self-contained power system,
• 3. exact geometrical guidance of all press jaws,
• 4. large linear displacement of the press jaws,
• 5. synchronous movement of all press jaws over the entire displacement,
• 6. Wear resistance, ie
  • 1. 6.1. small displacement distances between the inner sliding surfaces,
  • 2. 6.2. low internal surface pressures
• 7. easy interchangeability of the press jaw sets,
• 8. Large opening path of the press jaws for insertion complex shaped workpieces,
• 9. Clearances in front of and behind the press mouth, d. H. extreme shallow depth.

Radial presses with axially acting pressure medium drives and are known axially displaceable control bodies with closed on the circumference Truncated cone or truncated pyramidal surfaces that support the axial movement of the Convert the drive into radial movements of the press jaws. The production of hollow truncated pyramids is extremely expensive (DE 36 11 253 C2). The drive also blocks the space behind the press jaws and enforces a considerable depth, which is a multiple of the depth of the actual pressing tool.

In such a radial press according to DE 22 14 339 C3, the Opening path of the press jaws by manually adjusting one annular control body can be changed, the inside one Has a truncated cone surface. This is cumbersome and time consuming.

In such a radial press according to DE 28 44 475 C2, a larger one Opening path of the press jaws caused by a control body, the inside has two stepped frustoconical surfaces. This requires one particularly large axial depth and a large manufacturing effort.

For all radial presses with hollow truncated cone surfaces as control surfaces and outer control surfaces of the press jaws, which are sectors of one Truncated cone surface are formed, there is a flat contact only in a single position; in all other positions during the pressing process run through with full pressing force, there is only one touch along one or two lines, so that high surface pressures and high Wear are the result.

Such axial-radial presses can therefore be disregarded here. Large opening distances with a low construction depth can be achieved by so-called "divided pressing tools" with two sets of pressing jaws, which are arranged on both sides of a parting line. Such systems are disclosed in the following documents:

US-A-2 921 618
US-A-3 455 140
US-A-3 731 518
US-A-4 785 656 (= EP 0 263 614 B1)

So far, however, the displacement of the press jaws by plane Control surfaces takes place, which are arranged in pairs V-shaped and on act in groups of radially arranged press jaws The following problem: The pressing jaws closest to the parting line become because of their obtuse angular position to the drive direction always stronger and shifted with lower radial force components than the one in between lying press jaws, the longitudinal center axes of which are always more acute angles Have drive direction than that closest to the parting line Press jaws. The result is uneven displacement paths and Sliding speeds of the individual press jaws as well different shear forces resulting in different friction losses the press jaw guides and thus to different wear to lead.

If you want to create round pressings with it, the pressing surfaces of the Press jaws before the pressing process in an oval or elliptical position can be arranged, resulting in different deformation paths and Deformations result: Even an originally correctly shaped workpiece is first deformed elliptically and then finally pressed round - provided that all other pressing parameters are correct. Thereby eliminates a synchronous movement that is one of the The basic prerequisites for proper pressing are.

Fittings of high pressure hose lines do not leave asymmetrical  Deformation paths and no asynchronous deformation speeds too, otherwise the connections - with the known consequences - will leak.

Tolerances in the workpiece diameter and / or the processing of Workpieces with graded standard diameters cannot then be compensated, or there must be an adapted for each diameter Press jaw set are used, which means the scope of the equipment and increases the time required for the change process.

This also changes the generic solution according to US-A-3 731 518 nothing with the two V-shaped control surfaces in the area of their apex are rounded, i.e. have the shape of a parabola. Calculations have shown that with a press stroke of 10 mm an out-of-roundness of 1.58 mm, i.e. of about 16%, occurs, which at is absolutely inadmissible to today's requirements and test regulations.

The problems worsen as the number of press jaws decreases, so that also press tools with less than eight press jaws out of consideration can stay.

Regarding the above-mentioned writings and the further status of Technology, the following explanations are also made:

In the radial pressing tool known from US-A-2 921 618 not the required high pressing forces of the individual pressing jaws (up to 40 Mp) can be transferred because their sliding surfaces are spherical or round. in the further would be those press jaws that are at an obtuse angle to Press axis are exposed to very high transverse forces. These two Disadvantages leave the high wear of the sliding surfaces The pressing tool will soon be dimensionally accurate. This construction can be only for very light and small hose lines or other pressed parts apply, the area of application has a subordinate meaning.  

The radial pressing tools according to US-A-4 785 656 and EP 0 263 614 B1, are divisible and offer almost unlimited possibilities with regard to a complex variety of connection types to be processed Hose lines, on the other hand, have the same major disadvantage like US-A-2 921 618, in that the sliding surfaces of the press jaws are round are executed. It can not be the usually very high pressing forces transfer that easier to deform sleeves themselves Hydraulic hose lines are required. Because of the non-extensive Interventional conditions also cause rapid wear here. This Construction is therefore also only for subordinate pressing work suitable.

US-A-3 455 140 also shows a separable radial pressing tool. Here have the press jaws in contrast to the systems mentioned at the beginning areal control surfaces of all those involved in the pressing process Press parts. On the other hand, it is disadvantageous that only six instead of eight press jaws are used and that the press jaws are not guided in the pressing direction become. Rather, it tries to center them with compression springs, which is not can succeed. The consequence of this are unevenly wide ridges between the press jaws, which are on the outer jacket of the pressed Mark the hose sleeve (gaps between the press jaws). Such pressed hose lines are unsafe because of the unequal Press bars that tear the already pressed hose sleeves there.

US-A-3 731 518, already cited, addresses the same problem. Here, too, are those required for very high pressing forces Area intervention ratios insufficiently resolved. The inner, i.e. H. Press jaws closest to the press axis have rounded ones Sliding surfaces that are not in radius with the radius of the counter sliding surface can match because they are during the pressing process move concentrically while their counter control surface is parallel  emotional. The far greater disadvantage is the unfavorable pressure angles to see the outer press jaws. Here the pressing forces of the Drive deflected up to the pressing surface of the press jaws by about 67.5 degrees become. This, in turn, means that significant resulting opposing forces the centering ring in which the press jaws are guided and held, strain. High friction losses are the result in combination with one poorer efficiency. Assuming that individual press jaws up need to apply 40 Mp pressure force at these deflection angles resulting opposing forces to set just as high. Because of that this radial press tool is not suitable for high press forces.

EP 0 451 417 A2 shows a separable radial pressing tool with eight Press jaws. The press jaws have rollers on their outer ends that support the Transfer pressing forces. In view of the known high press jaw forces of up to 40 Mp when pressing valve connections for Hydraulic hose lines are a transfer of these forces through rollers not possible. This radial press tool is therefore only suitable for light ones Press work, e.g. B. for hose lines in the low pressure range.

The invention is therefore based on the object of a pressing tool specify the preamble of claim 1, the disadvantages of Avoids prior art and all specified at the beginning Requirements met at the same time.

The problem is solved in the pressing tool after Preamble of claim 1 according to the invention by the features in Characteristic of claim 1.

First of all, all of the above are thereby indicated Requirements met at the same time. Some aspects of the benefits will be added as follows:  

The pressure pieces have succeeded in creating additional control surfaces to set up. By a suitable choice of the angle of the pressure pieces opposite the counter sliding surfaces of the control body, it is ensured that synchronous with the control bodies also the pressure pieces in the closing and Move the press movement forward concentrically. The imaginary lines of the Control surfaces thus form during the pressing process continuously reducing square. In this way, eight in Circle evenly distributed, concentrically arranged press jaws into one to force radially acting press movement, although between the two Press tool halves only a parallel shift takes place.

The lateral wedge angles on each of the eight press jaws are uniform at 22.5 degrees and ensure an even flow of forces and thus high dimensional accuracy during the entire service life. The side Displacement of the press jaws against the counter sliding surfaces is only a fraction of the press jaw travel, which means that wear is minimal is. During the pressing process, depending on the press shear forces Size of hose connection to be pressed one Up to 40 Mp are not uncommon, the resulting effects Forces also on the guide body. In the inventive Subject the side forces of the press jaws, which to the Sides work. There are only components left that pass through Sliding friction within the guide grooves on the receiving segments in Press direction act.

By using two pressure pieces per press tool half this divided in the middle. This creates two mirror images Press tool halves that can be spaced as far apart as desired. Only when they meet does it unite to form a radial one Press tool. This creates the advantage that the free space between the press jaw halves of complicated shape Hose line ends, e.g. B. those with large flanges or large  Pipe elbow can be inserted and pressed. Second, need the press jaws only a relatively small way around the press path to drive. As a result, the pressing tool can be relatively small and be made compact.

Further advantageous configurations of the subject matter of the invention result itself from the subclaims and from the detailed description.

A very big advantage can be seen in the fact that with one handle each Press tool halves removed from the control bodies and against others can be exchanged. Only the index bolts have to be actuated become.

In known machines, each individual press jaw from the Extraction tool removed and another can be used for it. Here great care is needed to make press jaws different Press diameter must not be interchanged. Instead of eight press jaws here only two parts, the two press jaw halves, to be replaced. In practice, the exchange of press jaws is necessary because of a Press jaw set covers only a certain range of press diameters. in the The area below or above must be the appropriate one Press jaw set are inserted.

An embodiment of the subject matter of the invention and its function are explained in more detail below with reference to FIGS. 1 to 8.

Show it:

Fig. 1 is a partially sectioned front view of a Radialpreßwerkzeugs in the direction of the press axis A in a fully open state;

Fig. 2, the Radialpreßwerkzeug of FIG. 1 at the end of the closing operation of the die halves immediately prior to the pressing operation,

Fig. 3 shows the radial press tool of FIG. 1 at the end of the pressing process

Fig. 4 shows the upper right quadrant of FIG. 2, on an enlarged scale to illustrate the geometric and kinematic relationships

Fig. 5 is a perspective exploded view of one of the two semi-annular guide body having a pressing jaw,

Fig. 6, the two semi-annular guide body with the eight press jaws shortly before the end of the closing process,

Fig. 7 shows a section through the radial pressing tool in the fully open state along the line VII-VII in Fig. 1 on a reduced scale, and

Fig. 8 shows an axially parallel section through one of the pin fastenings for the two semi-ring-shaped guide bodies in the control bodies.

In Fig. 1 is a Radialpreßwerkzeug RP with a press axis A or A 'and eight radial thereto and mutually identical cheek plates 8 a, 8 b for the deformation of rotationally symmetrical workpieces W shown. The press jaws need not be made in one piece; they can be designed in several parts and, for example, each consist of a base jaw and a top jaw, which contains the pressing surface 24 mentioned later.

In the case shown, the workpiece W is the sleeve made of steel or sleeve of a hose fitting with a high pressure hose for Pressures up to 1000 bar should be pressed. Im - not particularly shown - hose is a piece of pipe that is firmly attached to a Flange plate F is connected to a large radial extension, which is the case here has created a solving problem.

The radial pressing tool RP has two pressing tool halves 1 and 2 which are arranged on both sides of a parting line T and are movable relative to one another, each of which has a control body 3 and 4 and an at least substantially semi-annular guide body 5 and 6 , each with four in radial guides 7 (see FIG. 5) Press jaws 8 a, 8 b. Of these, two outer press jaws 8 a are adjacent to the parting line T, and the other two inner press jaws 8 b are arranged between the outer press jaws 8 a.

In Fig. 1, the two press tool halves 1 and 2 are so far apart that the flange plate F can be easily pushed through and the workpiece W is with its axis - initially floating - in the press axis A. The two axes A 'of the press tool halves 1 and 2 have a corresponding distance D.

The control bodies 3 and 4 have on their inner sides control surfaces 9 a and 9 b, which together surround all the pressing jaws 8 a and 8 b. By means of these control surfaces 9 a and 9 b, in the moved-together position of the guide bodies 5 and 6 ( FIGS. 2 and 3), radial movements of the press jaws 8 a and 8 b can be brought about, the center axes MA of all press jaws 8 a and 8 b being equal angular distances from one another Include 45 degrees ( Fig. 4).

The two press tool halves 1 and 2 are connected to one another by two parallel guides 10 for the control bodies 3 and 4 , in which the guide bodies 5 and 6 are fastened interchangeably with the press jaws 8 a and 8 b. A total of eight control surfaces 9 a and 9 b are provided, of which the four outer control surfaces 9 a are adjacent to the parting line T in pairs and the four other inner control surfaces 9 b are arranged in pairs between the outer control surfaces 9 a.

The radial pressing tool RP can be used independently with a corresponding external drive, not shown, which works in the direction of the parallel guides 10 , but it can also be used in conventional presses with a press frame and a drive.

It is important that both the control surfaces 9 a and 9 b of the control bodies 3 and 4 and the outer ends of the press jaws 8 a and 8 b are formed as flat sliding surfaces, the sliding surfaces G of the pressing jaws 8 a and 8 b being perpendicular to whose center axes are MA (see FIGS . 5 and 6).

The essence of the invention is that four wedge-shaped thrust pieces 11 and 12 are arranged in the pressing tool halves 1 and 2 between the outer control surfaces 9 a of the control bodies 3 and 4 and the sliding surfaces G of the outer pressing jaws 8 a, which have paired abutting surfaces 13 . Furthermore, the pressure pieces 11 and 12 have outer flat sliding surfaces 14 , which cooperate with the outer control surfaces 9 a of the control bodies 3 and 4 , and inner sliding surfaces 15 , which cooperate with the sliding surfaces G of the outer pressing jaws 8 a.

As is apparent from a comparison of FIGS. 1 to 4, the angle of the sliding surfaces 14 and 15 of the plungers 11 and 12 are α and β (FIG. 4) is selected to the parting line T that fully when moving apart of the die halves 1 and 2 from the In the closed position ( FIG. 3), the pressure pieces 11 and 12 touching one another initially move radially outward in the direction of the abutting surfaces 13 (double arrow 30 in FIG. 4) and the outer press jaws 8 a are absolutely synchronous and tilt-free with the back inner cheek plates 8 b blank (double arrows 31 in Fig. 4) and the further moving apart of the die halves 1 and 2 from the position shown in Fig. 2 position by lifting off the abutting surfaces 13 of the movement of the die halves 1 and 2 in Fig. 1 shown Follow the fully open position (double arrow 32 in Fig. 4).

As also seen from a comparison of FIGS. 1 to 4, 1, the plungers 11 and 12 in the direction of movement of the die halves 1 and 2 are reversed at the moving together of the die halves 1 and 2 from the fully open position of FIG. Initially together with these to the coincidence of the abutting surfaces 13 ( FIG. 2), whereby the pressure pieces 11 and 12 each form a new movement unit in the form of a double wedge mirror-symmetrical to the parting line. Subsequently, during the pressing process from the position shown in Fig. 2 to the position shown in Fig. 3 position by further vertical moving together of the die halves 1 and 2 and by simultaneously against each other directed horizontal movement of the two moving units or pressure piece combinations 11/12 toward the Press axis A, the outer press jaws 8 a absolutely synchronously with the inner press jaws 8 b moved radially inwards.

In this "grow" the four plungers 11 and 12, so to speak temporarily to said two pressure pieces combinations 11/12 together, wherein centering takes place in that the pressure pieces 11 and 12 have in their abutting faces 13 centering. 16 and 17 16 is an index pin and 17 is a complementary index hole ( Fig. 1).

These processes are illustrated in more detail with reference to FIG. 4, in which one of the pressure pieces 11 is shown hatched for the sake of clarity, without being cut:

The control surfaces 9 b and 9 a extend - starting from a plane of symmetry SS, which is laid through both press tool halves 1 and 2 and parallel to the parallel guides 10 - relative to a first reference plane B1 perpendicular to this in the vicinity of the plane of symmetry SS at an angle of 22.5 Degrees and near the parting line T at an angle of 45 degrees to this reference plane B1. The inner sliding surfaces 15 of the pressure pieces 11 and 12 are at an angle of 22.5 degrees to a second reference plane B2, which runs parallel to the said plane of symmetry SS.

The effect of the pressing operation is that the vertical directions of movement of the control surfaces 9 b on the one hand and the horizontal displacement directions of the inner surfaces 15 of the pressure piece combinations 11/12 on the other hand all the press jaws identical with respect to the longitudinal center axis MA angle ∂ of 22.5 degrees include their (low ) mutually identical sine components act against one of the inner surfaces 7 a of the radial guides 7 , while the (substantially larger) and likewise identical cosine components run in the direction of the longitudinal center axes MA and thus in the pressing direction and thus act as identical pressing forces.

The plungers 11 and 12 and pressure member combinations 11/12 and thus the cause of the equalization of the compression forces and for the synchronization of the absolute Preßbackenbewegungen. It also follows that within the system all forces or force components cancel each other out, so that the half-ring-shaped guide bodies 5 and 6 do not move with respect to the press axis A and are self-centering in the idle state during the pressing process, so that no great demands are made on their suspensions are to be asked.

Through this self-centering, the press accuracy to which it is applied High pressure hose connections are crucial, optimized. The dashed or dash-dotted lines show the state at the end of the Pressing process; the diameter reduction has the dimension "ΔW".

In addition, the sliding or sliding paths on the sliding surfaces minimized so that wear is also minimized.

In the individual figures are provided between the pressing jaws 8 a and 8 b unnumbered compression springs shown, which are known per se, but produce in conjunction with the pressure pieces 11 and 12 and pressure pieces combinations 11/12 also same restoring forces.

The pressure pieces 11 and 12 and the spatial positions of their sliding surfaces 14 and 15 are therefore the prerequisite for an absolutely synchronous movement of the press jaws 8 a and 8 b during the pressing process and even beyond: it may be necessary for different diameters of the workpieces W due to Tolerances and different standard specifications to move the press paths or press strokes and / or their start and end points radially inwards or outwards without the guide bodies 5 and 6 with their press jaws 8 a and 8 b having to be exchanged for this. Rather, the same guide bodies 5 and 6 with their pressing jaws 8 a and 8 b can be used for a whole group of nominal dimensions of the workpieces W.

Referring to FIG. 4 11 and 12 have the pressure pieces against the control bodies 3 and 4 stops 18, which - cooperate with counter-stops 19, in such a way that the during an opening movement of the control body 3 and 4 in accordance with a lift-off - with the interposition of return springs 33 Buttocks 13 further relative movements between the pressure pieces 11 and 12 and the control bodies 3 and 4 are blocked. This position is shown in FIGS. 1 (bottom left) and 4 (right). These return springs 33 support the action of the remaining compression springs between the press jaws in a synergistic manner.

Referring to FIGS. 5 and 6, the semi-annular guide body 5 and 6 consist of five wedge pieces 20 and 21, of which the two outer wedge pieces 20 angle of 22.5 degrees, and the three inner wedge pieces include 21 angle of 45 degrees. These wedge pieces 20 and 21 are integrally connected by four smaller than the wedge pieces 20 and 21 in cross-section connectors 22 which form between the wedge pieces 20 and 21, the parallel-walled radial guides 7 for receiving the complementarily shaped pressing jaws 8 a and 8 b at their ends. In Fig. 5, only such an inner press jaw 8 b is shown with its partially cylindrical pressing surface 24 .

Referring to FIG. 5, the press jaws 8 a and 8 b at their, the press surfaces 24 ends remote from U-shaped with parallel legs 25 and fitted with a sufficient radial play astride the connecting pieces 22 of the guide body 5 and 6. As a result, the two sliding surfaces G lie on both sides of the connecting pieces 22 .

Referring to FIGS. 6, 7 and 8, 6 are semi-annular guide body 5, in the region of defined by both die halves 1 and 2, parallel to the parallel guides 10 symmetry plane SS waisted retaining pins 26 which inserted in radial bores 27 in the control bodies 3 and 4 and are held there by spring-loaded locking bolts 28 which are slidably inserted in axially parallel bores 3 a in the control bodies 3 and 4 against a prestressed spring 29 . The locking bolts 28 engage with an extended groove 29 in an annular groove 26 a of the holding pin 26 , but unlock when the spring 29 is compressed (force in the direction of arrow 29 a) by means of its own annular groove 28 a the holding pin 26 .

The holding pins 26 are displaceable in the radial bores 27 of the control bodies 3 and 4 by an amount which corresponds at least to the pressing path of the pressing jaws 8 a and 8 b.

In Fig. 7 is also shown in dashed lines in which spatial position the workpiece W, a press sleeve of a fitting with a flange plate F for a high-pressure hose 34 , lies in the press axis AA before the press tool halves 1 and 2 are moved together.

In Figs. 1 to 4 are shown parallel guides 10, which guide the control body 3 and 4 on the entire path, which is composed of a very large idle stroke and a power stroke (during the actual pressing operation). Parallel guidance is essential during the pressing process. During the idle stroke, however, it is possible to replace the guide on the long opening and closing path by other means, for example by a joint, the axis of which is spaced from and parallel to the press axis A, by two analog joints, or thereby, that one lifts the upper control body from one of the then shortened parallel guides 10 and swings out laterally about the axis of the other parallel guide 10 , resulting in an extremely wide open press jaw.

Reference list

1

Press tool half

2nd

Press tool half

3rd

Control body

3rd

aBore

4th

Control body

5

Guide body

6

Guide body

7

Radial guides

7

aInterior areas

8th

a,

8th

b Press jaws

9

a,

9

b Control areas

10th

Parallel guides

11

Thrust pieces

12th

Thrust pieces

13

Buttocks

14

outer sliding surfaces

15

inner sliding surfaces

16

Index pin

17th

Index hole

18th

attacks

19th

Counter-stops

20th

outer wedge pieces

21

inner wedge pieces

22

Connectors

24th

Pressing surface

25th

leg

26

Retaining pin

26

aRingnut

27

Holes

28

Locking bolt

28

aRingnut

29

feather

29

arrow

28

aRingnut

30th

Double arrow

31

Double arrow

32

Double arrow

33

Return springs

34

High pressure hose
A, A-APress axis
A 'tool half axes
B1, B2B reference level
Ddistance
F flange plate
Sliding surfaces (of the press jaws)
MAMen axes
RP radial press tool
S-SSymmetry plane
T separation joint
WWorkpiece

Claims (8)

1. Radial pressing tool with a press axis (A) and eight radial pressing jaws ( 8 a, 8 b) for the deformation of rotationally symmetrical workpieces (W), in particular for pressing hose fittings with high pressure hoses

• a) two pressing tool halves ( 1 , 2 ) arranged on both sides of a parting line (T) and movable relative to each other, each of which has a control body ( 3 , 4 ) and an at least substantially semi-ring-shaped guide body ( 5 , 6 ) with four radial guides ( 7 ) arranged press jaws ( 8 a, 8 b), of which two outer press jaws ( 8 a) adjacent to the parting line (T) and the other two press jaws ( 8 b) are arranged between the outer press jaws ( 8 a), and
• b) with control surfaces ( 9 a, 9 b), which surround all the pressing jaws ( 8 a, 9 a) on the inner sides of the control bodies ( 3 , 4 ) and, due to the moved together position of the guide bodies ( 5 , 6 ), radial movements the pressing jaws ( 8 a, 8 b) can be brought about, the center axes (MA) of all pressing jaws ( 8 a, 8 b) including angular distances of 45 degrees from one another,

characterized in that

• a) a total of eight control surfaces ( 9 a, 9 b) are provided, of which four outer control surfaces ( 9 a) are adjacent to the parting line (T) and the four other control surfaces ( 9 b) are arranged between the outer control surfaces ( 9 a),
• b) both the control surfaces ( 9 a, 9 b) of the control body ( 3 , 4 ) and the outer ends of the pressing jaws ( 8 a, 8 b) are designed as flat sliding surfaces, the sliding surfaces (G) of the pressing jaws ( 8 a , 8 b) are perpendicular to their central axes (MA), and that
• c) in the pressing tool halves ( 1 , 2 ) between the outer control surfaces ( 9 a) of the control body ( 3 , 4 ) and the sliding surfaces of the outer pressing jaws ( 8 a) four wedge-shaped thrust pieces ( 11 , 12 ) are arranged, the abutting surfaces interacting in pairs ( 13 ), as well as outer flat sliding surfaces ( 14 ), which cooperate with the outer control surfaces ( 9 a) of the control bodies ( 3 , 4 ), and inner sliding surfaces ( 15 ), which with the sliding surfaces (G) of the outer press jaws ( 8 a) cooperate flatly, the angle of attack (a, β) of the sliding surfaces ( 14 , 15 ) of the pressure pieces ( 11 , 12 ) to the parting line (T) are chosen so that
  • 1. When the pressing tool halves ( 1 , 2 ) move apart from the fully closed position, the contacting pressure pieces ( 11 , 12 ) first move radially outward by a limited amount and the outer pressing jaws ( 8 a) synchronously with the inner pressing jaws ( let go back 8 b) and follow the further moving apart of the die halves (1, 2) by lifting off the abutting surfaces (13) of the movement of the die halves (1, 2), and that
  • 2. When moving together the pressing tool halves ( 1 , 2 ) from the fully open position, the pressure pieces ( 11 , 12 ) in the direction of movement of the pressing tool halves ( 1 , 2 ) are moved with them until the abutting surfaces ( 13 ) meet and then by further moving together the pressing tool halves ( 1 , 2 ) are displaced during the pressing process in the direction of the press axis (A) and in doing so move the outer pressing jaws ( 8 a) synchronously with the inner pressing jaws ( 8 b) radially inwards.

2. Radial pressing tool according to claim 1, characterized in that the pressure pieces ( 11 , 12 ) in their abutting surfaces ( 13 ) have centering means ( 16 , 17 ). 3. Radial pressing tool according to claim 1, characterized in that the control surfaces ( 9 b, 9 a), starting from an apex line between two inner control surfaces ( 9 b) with respect to a reference plane (B1) parallel to the parting line (T) in the vicinity this apex line at an angle of 22.5 degrees and in the vicinity of the parting line (T) at an angle of 45 degrees, and that the inner sliding surfaces ( 15 ) of the pressure pieces ( 11 , 12 ) to the parting line (T) at an angle of 67.5 degrees. 4. Radial pressing tool according to claim 1, characterized in that the pressure pieces ( 11 , 12 ) with respect to the control bodies ( 3 , 4 ) have stops ( 18 ) which cooperate with counter-stops ( 19 ), such that the control body ( 3 , 4 ) after lifting off the abutting surfaces ( 13 ) further relative movements between the pressure pieces ( 11 , 12 ) and the control bodies ( 3 , 4 ) are blocked. 5. Radial pressing tool according to claim 1, characterized in that the semi-annular guide body ( 5 , 6 )

• a) consist of five wedge pieces ( 20 , 21 ), of which the two outer wedge pieces ( 20 ) include angles of 22.5 degrees and the three inner wedge pieces ( 21 ) angles of 45 degrees, and
• b) consist of four compared to the wedge pieces ( 20 , 21 ) reduced in cross-section connecting pieces ( 22 ) between the wedge pieces ( 20 , 21 ) parallel-walled radial guides ( 7 ) for receiving complementarily shaped press jaws ( 8 a, 8 b) form.

6. Radial pressing tool according to claim 5, characterized in that the pressing jaws ( 8 a, 8 b) at their, the pressing surfaces ( 24 ) ends U-shaped with parallel legs ( 25 ) and astride the connecting pieces ( 22 ) of the guide body ( 5 , 6 ) are attached. 7. Radial pressing tool according to claim 5, characterized in that the semi-ring-shaped guide bodies ( 5 , 6 ) in the area of a through both pressing tool halves ( 1 , 2 ), parallel to the parallel guides ( 10 ) parallel plane of symmetry (SS) have waisted holding pins ( 26 ), which are inserted into radial bores ( 27 ) in the control bodies ( 3 , 4 ) and are held there by spring-loaded locking bolts ( 28 ) which can be displaced against a preloaded spring ( 29 ) in axially parallel bores ( 30 ) in the control bodies ( 3 , 4 ) are used, in stretched spring (29) in an annular groove (31) of the holding pins (26) engage, disengage the holding pin (26) in compressed spring (29) by means of an own annular groove (32). 8. Radial pressing tool according to claim 7, characterized in that the holding pin ( 26 ) in the radial bores ( 27 ) of the control body ( 3 , 4 ) are displaceable by an amount which corresponds at least to the pressing path of the pressing jaws ( 8 a, 8 b) .