EP0298017B1 - Radial press - Google Patents

Abstract

A radial press is described for workpieces with an essentially cylindrical outer surface, with a plurality of pressing jaws which are arranged in a circle around the axis of the outer surface of the workpiece, are guided on an axial abutment, are movable radially to this axis and the outer surfaces of which each have at least one control surface formed obliquely to the axis, and with a pressure ring which can be displaced axially relative to the pressing jaws by a hydraulic or pneumatic drive and the inner surfaces of which have control surfaces which come into engagement with the control surfaces of the pressing jaws when the pressure ring is displaced axially to close the pressing jaws, the pressing jaws moving radially inwards, initially with a rapid idle stroke and then with a slow power stroke. To avoid damage to the control surfaces, the pressing jaws are guided on the pressure ring with the control surfaces of the pressure ring and pressing jaws lifted clear in the range of the idle-stroke motion of the pressure ring.

Description

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

Such a radial press, which is used, for example, for the production of high-pressure hose lines with connection fittings is already known from GB-A-2 033 281. In this radial press, the pressing jaws slide with their control surfaces along the control surfaces at the end with a steeper pitch angle during a closing movement during the idle stroke and then pass into the power stroke, which leads to high friction losses and signs of wear on the control surfaces. In the known radial press, the known use of slide bearings and that of dirt wipers, which are provided to protect the control surfaces of the pressure ring against dirt and damage, lead to a shorter service life of the radial press.

The invention has for its object to provide a radial press of the type mentioned, with a short overall length and simple construction as possible a tilting moment-free and low-maintenance guidance of the press jaws on the pressure ring, even with a large axial stroke of the press jaws, through the pressure ring.

This object is achieved by the features of claim 1.

It is thereby achieved that during the critical idle stroke movement of the pressure ring, the control surfaces provided for the power stroke with a front face and transition edge to the control surface of the pressure ring and press jaws disengage, so that these control surfaces formed as plain bearings are not stressed, especially along the end face of the press jaws, and so that they are not subject to wear.

Only after the end of the empty stroke do the control surfaces come into operative position again in order to close the press jaws during the power stroke that then begins. Due to the bevels provided on the side of the control surfaces for the power stroke, an abrupt placement of the control surfaces of the pressing jaws and pressure ring and contact of the transition edges to the control surfaces of the pressing jaws with the pressure ring are avoided. Due to the bevels provided on both sides, the press jaws are guided largely without tilting moment even during the feed movement of the pressure ring. The radial press according to the invention is characterized by a long service life of the slide bearings and is particularly suitable for presses in which the control surfaces of the pressure ring are equipped with slide bearing surfaces.

In order to significantly improve the service life of the dirt wipers protecting the control surfaces and thus the service life of the radial press, according to one embodiment of the invention, the bevels of the pressure ring are designed in such a way that the control surfaces of the pressure ring and press jaws provided for the power stroke during the idle stroke movement thereof by one of the preload of a respective dirt wiper arranged on a press jaw are raised, which is in engagement with the respective control surface of the pressure ring during the power stroke movement.

In order to reliably absorb the reaction forces occurring during the power stroke from the control surfaces of the pressure ring, it is provided according to the invention that the bevels of the pressure ring are out of contact with the press jaws during the power stroke movement thereof.

The demand for the highest possible radial pressing forces in connection with the lowest possible maximum pressure of the hydraulic system and low-wear radial stroke of the press jaws is achieved according to a further embodiment of the invention in that the press jaws each have two parallel offset control surfaces for the power stroke in the axial direction and that the pressure ring has essentially complementary to the control surfaces of the press jaws designed control surfaces for the power stroke.

The elevation slopes of the pressure ring are expediently formed on side guides for the press jaws.

According to a further embodiment of the invention, it is provided that the elevation slopes change in the closing direction of the pressure ring into axially adjoining slopes with a small angle of inclination with respect to the axis. As a result, an abrupt placement of the control surfaces of the pressing jaws and pressure ring at the beginning of the power stroke is avoided in a particularly advantageous manner, since the control surfaces only gradually come into engagement with one another due to the inclined slopes. These measures also protect the dirt wipers particularly effectively.

In terms of construction and production technology, it is particularly favorable if adjacent lifting bevels of the pressure ring, which may change into inclination bevels, are designed as flat back parts, between which the control surfaces of the pressure ring provided for the power stroke are formed in a recessed manner.

The lifting bevels of the press jaws can be designed according to the invention as lateral pins, bolts or the like. Sliding elements which slide on the lifting bevels and possibly inclined bevels of the pressure ring during an idle stroke movement.

According to a further embodiment of the invention, it is provided that the control surfaces of the pressure ring provided for the power stroke are designed as slide bearing surfaces, preferably made of PTFE. By lifting off the control surfaces of the pressing jaws and pressure ring during the idle stroke according to the invention, the advantageous properties of these maintenance-free and only minimal friction losses bearing bearings come into their own.

So that the control surfaces of the pressure ring are protected from damage by the control edges of the press jaws, according to the invention on the flanks of the parallel offset control surfaces of the pressure ring provided for the power stroke, end-face sliders are provided, along which the press jaws slide along during the idle stroke movement of the pressure ring. In addition, the sliders can be used to fasten the slide bearing surfaces at the same time.

In order to avoid an abrupt placement of the control surfaces of the press jaw on the control surfaces of the pressure ring during the transition between the idle stroke and the power stroke movement in this embodiment as well, it is provided according to the invention that the sliders have steep bevels at which the press jaws preferably adhere to their outer surfaces their front ends formed, possibly rounded control edges, and / or that the sliders have a preferably rounded raised edge on which the press jaws with control edges formed on their outer surfaces with adjoining control bevels slide during the idle stroke movement.

In particular in the case of large radial presses, it is provided according to the invention that two axially opposite pressure rings are provided which axially move towards one another by means of pressure medium drives in order to close the press jaws arranged between them are displaceable, and that the axially opposing press jaws are supported against each other. The arrangement of two axially opposite pressure rings can advantageously dispense with the counter bearings required for the press jaws in the case of a single design.

In addition to individual control of the two pressure rings for the axial feed movement, the pressure medium drives provided for the axial displacement of the pressure rings can also be connected in parallel and / or the axially opposite press jaws can be formed in one piece. The parallel connection of the pressure medium drives results in a uniform axial movement of the pressure rings axially towards one another, radial tolerances being compensated for with an additional one-piece design of axially opposite pressing jaws.

In a further development of this embodiment of the invention it is provided that the pressing jaws are provided on their outer sides with devices for holding, centering and for tolerance compensation of an intermediate jaw, which is designed to receive pressing jaws with a smaller nominal width. The radial presses according to the invention can thus be converted easily and conveniently for the production of hose lines with small diameter connection fittings.

It is expediently provided that the pressure ring or rings are designed as spring-loaded ring or hollow pistons of the pressure medium drive, which are guided on a radially outer cylinder jacket and a cylinder base arranged in a recess in the pressure ring. This configuration with a pressure ring designed as a ring or hollow piston results in an extremely short axial construction, combined with great freedom of movement on the back of the pressure ring, so that workpieces with a complicated shape and in particular hose lines with pipe bends arranged on both sides can be pressed. In this embodiment, the axial length of the pressure ring is advantageously used to form a pressure chamber, which is delimited by the cylinder base which axially guides the pressure ring and the outer cylinder jacket.

With a single pressure ring, it can be particularly favorable with regard to a compact design if the cylinder jacket is connected to the counter bearing and serves as a connecting element for transmitting the reaction forces.

In a particular embodiment of the invention, the pressure medium drive has an annular piston guided between an outer surface of the pressure ring and an outer cylinder, to the piston rod, which is preferably designed as a tie rod, the counter bearing which bears against the pressing jaws is fastened and which axially together with the pressing jaws when the annular piston is pressurized moved in the direction of the stationary arranged with respect to the housing pressure ring. In this radial press, which has an axially short overall length, when the annular piston is pressurized, for example in a recess in the pressure ring, the counter bearing together with the press jaws is pulled axially against the pressure ring, as a result of which a radial movement of the press jaws relative to the counter bearing or of the stationary arrangement with respect to the housing is arranged Pressure ring takes place. In addition, the piston rod designed as a tie rod for the counterbearing leads to an open construction, at least in the open position of the press jaws, so that, during the insertion process of a high-pressure hose, possibly detachable fitting parts can fall out or be removed without damage to the press is coming.

It is also within the scope of the invention that the pressure medium drive (s) are designed as double-acting piston-cylinder arrangements for a closing and opening movement of the press jaws.

Further features, advantages and possible applications of the invention result from the following description of exemplary embodiments, which are shown in the drawing.

Fig. 1

einen vertikalen Axialschnitt durch eine erfindungsgemäßen Radialpresse,

Fig. 2

eine perspektivische Teildarstellung eines erfindungsgemäßen Druckrings mit Preßbacken,

Fig. 3

den Preßbacken gemäß Fig. 2,

Fig. 4

einen vertikalen Axialschnitt durch den in Fig. 2 dargestellten Druckring mit Preßbacken,

Fig. 5

eine Fig. 4 entsprechende Darstellung des Druckrings mit Preßbacken, jedoch in Schließstellung des Preßbackens,

Fig. 6

einen Axialschnitt durch eine Radialpresse mit zwei Druckringen,

Fig. 7

eine Teilansicht einer weiteren Ausführungsform einer erfindungsgemäßen Radialpresse,

Fig. 8

eine Teilansicht einer wiederum anderen Ausführungsform einer Radialpresse,

Fig. 9

eine Teilansicht einer noch anderen Ausführungsform einer Radialpresse und

Fig. 10

eine Vorder- oder Rückansicht einer Radialpresse gemäß Fig. 1 und 5 bis 8.

Show it:

Fig. 1

a vertical axial section through a radial press according to the invention,

Fig. 2

2 shows a perspective partial illustration of a pressure ring according to the invention with press jaws,

Fig. 3

the press jaws according to FIG. 2,

Fig. 4

3 shows a vertical axial section through the pressure ring with press jaws shown in FIG. 2,

Fig. 5

4 corresponding representation of the pressure ring with press jaws, but in the closed position of the press jaw,

Fig. 6

an axial section through a radial press with two pressure rings,

Fig. 7

2 shows a partial view of a further embodiment of a radial press according to the invention,

Fig. 8

2 shows a partial view of yet another embodiment of a radial press,

Fig. 9

a partial view of yet another embodiment of a radial press and

Fig. 10

a front or rear view of a radial press according to FIGS. 1 and 5 to 8.

1 shows a cylindrical radial press with a hydraulic feed unit, which has a cylinder jacket 16 and a cylinder base 3. The annular cylinder base 3 and the cylinder jacket 16 are connected to one another by screws 8. A counter bearing 5 is fastened on the end face opposite the cylinder base 3.

In the interior of the cylinder there is a rotationally symmetrical pressure ring 2, the outer surface of which consists of two cylinder surfaces of different diameters, between which an annular surface is arranged, which represents the actual active surface of a hollow piston which is formed by the pressure ring 2. The cylinder space formed within the cylinder is sealed to the outside by ring seals and by a further ring seal 7 arranged between the cylinder base 3 and the cylinder jacket 16. The cylinder space is connected via a bore and line connections 50, 51 to a pressure medium source, not shown. The cylinder base 3 has a flattened area 49 in the area of the bore, which favors the pressurization of the hollow piston in its open position shown in FIG. 1.

In the counter bearing 5 designed as a plate, spring bearings 10 are inserted, in which compression springs 15 for returning the pressure ring 2 into the starting position shown in FIG. 1 are accommodated. The compression springs 15 simultaneously prevent the pressure ring 2 from rotating.

The pressure ring 2 has an inner surface which is formed by the control surfaces 30, 32, which are offset parallel to one another. The control surfaces 30, 32 are inclined with respect to the axis X-X of the cylindrical outer surface of a workpiece, not shown, which coincides with the axis of the radial press. With the control surfaces 30, 32, distributed uniformly over the circumference, eight press jaws 4 work together, the outer surfaces of which are composed of complementary control surfaces 31, 33. The press jaws 4 are, as indicated in FIGS. 2 and 3, via T-slots on the Counter bearing 5 attached.

As can be seen from FIGS. 2 to 5, the pressure ring 2 on its side guides 40 for the pressing jaws 4 has two bevels 34, 34a arranged offset parallel to one another in the axial direction, of which the first 34a on the end face of the pressure ring 2 and the second 34 in Area of the flank between the two control surfaces 30, 32 arranged in parallel offset is provided. The elevation slopes 34, 34a change in the closing direction of the pressure ring 2 into axially adjoining slope slopes 37, 37a with a small angle of inclination with respect to the axis XX. As can be seen from Fig. 2, adjacent elevation slopes 34, 34a of the pressure ring with the corresponding inclination slopes 37, 37a, which are each assigned to the pressure ring 2 pressing jaws 4, are formed as flat back parts 9, between which the control surfaces 30, 32 are recessed. These control surfaces 30, 32 of the pressure ring 2 are designed as slide bearing surfaces and consist of the low-friction material PTFE.

The elevation bevels 34, 34a and the incline bevels 37, 37a of the pressure ring 2 complementary to each other are formed on the side surfaces of the press jaws 4, elevation bevels 64, 64a or corresponding incline bevels 11, 11a.

As can be seen from FIG. 3, the pressing jaw 4 has a dirt wiper 41 on its front end face, which comes into engagement with the respective control surface 30 of the pressure ring 2.

The radial press described works as follows:
First, the pressure ring 2 is in the position shown in FIG. 1, namely under the action of the compression springs 15 in the stop in the cylinder bottom 3. The press jaws 4 are in their maximum outer position in which they are under the action of the compression spring 14 are kept as far apart as possible. In this position, a pressure hose with a fitting of complicated shape can be inserted into the cylindrical space with the opening diameter 61 (see FIG. 10).

As soon as pressure is generated in the bore, it acts on the circular surface of the hollow piston and begins to move the pressure ring 2 to the left. Here, the press jaws 4 slide with their bevels 64, 64a on the bevels 34, 34a of the pressure ring 2. The control surfaces 30 and 32, of the pressure ring 2 are lifted from the control surfaces 31 and 33 of the press jaw 4, namely by a preload of on the press jaws 4 arranged dirt wipers 41 corresponding dimension. As a result, the pressing jaws 4 move inward in this idle stroke movement of the pressure ring 2 practically without force at high speed.

At the end point 36 of the bevels 34, 34a, the inclination surfaces 11, 11a of the pressing jaws 4 engage with the complementary inclining surfaces 37, 37a of the pressure ring, the pressing jaws 4 with their control surfaces 31, 33 having the complementary control surfaces 30, 32 of the pressure ring 2 Plant. At the beginning of touching these surfaces or shortly thereafter, the actual power stroke occurs, i.e. a relatively large path of the pressure ring 2 is required in order to move the press jaws 4 radially inward by an amount corresponding to the deformation path 63 (cf. FIG. 9). The end position of the pressure ring 2 and the press jaw 4 can be seen from FIG. 5. From Fig. 10 it can be seen that the end faces of the press jaws 4 bsw. enclose a practically closed cylinder with the press diameter 62 of press jaws 57 with smaller nominal widths.

A limit switch 47 connected to the housing 48 of the radial press via a mounting bracket 46 is pressed against an adjusting screw 45 when the end position of the pressure ring 2 is reached, as a result of which the pressure is reduced and the pressure ring 2 under the action of the pressure springs 15 into the position shown in FIG. Fig. 4 shown position returns. The press jaws 4 follow this return movement, the control surfaces 30, 32 and 31, 33 of the pressure ring 2 and press jaws 4 by the interaction of the inclined bevels 64, 64a and 11, 11a and subsequently the elevation bevels 34, 34a and 64, 64a by a bias of the Dirt scraper 41 corresponding size are lifted.

The radial presses shown in FIGS. 5 to 8 have the same or similar functional sequence as the radial press according to FIGS. 1 to 4, the corresponding components being provided with the same reference numbers.

The radial press shown in FIG. 6 has two axially opposite pressure rings 2, 2.1, which can be axially displaced towards one another by means of pressure medium drives, between the pressure jaws 4 arranged between the pressure rings 2, 2.1. The pressure rings 2, 2.1 designed as hollow pistons slide with their radially outer ring surface on a cylinder jacket 18, which is provided with connection options for the supply of pressure medium. To seal the pressure chambers formed by the cylinder jacket 10 and the cylinder bottoms 3 arranged on both sides, ring seals 7 are provided. The pressure medium drives for the pressure rings 2, 2.1 or the application of their hollow pistons with pressure medium can take place in a parallel connection, which results in a uniform axial movement of the pressure rings 2, 2.1.

In the cylinder bottoms 3 pressure chambers provided with annular pistons 22 are formed, the front end of which is formed by annular disks 6 with connections for a pressure supply. At the end of each pressure ring 2, 2.1, at least three pressure rods 21 are arranged at a uniform distance along the circumference of the annular piston 22. The pressure rods 21, which are respectively fastened to the one end of the one pressure ring 2, 2.1, are guided through the respectively opposite pressure ring 2 or 2.1 into the respectively adjacent pressure chambers against the end face of the respective annular piston 22, ring seals 24 being provided for sealing. The axial movement of the pressure rings 2, 2.1 into their end position moves the ring pistons 22 in the direction of the ring disk 6. By switching the pressure direction and introducing a pressure medium via the connection to the ring disk 6, the opposing ring pistons 22 move axially towards one another, as a result of which the pressure rings 2, 2.1 are brought into their starting position via the pressure rods 21.

The pressing jaws 4, which are supported against one another in pairs, are raised during the idle stroke of the pressure rings 2, 2.1 in the manner described above.

In addition to the parallel action on the pressure medium drives for the pressure rings 2, 2.1, the embodiment shown in FIG. 6 also gives the possibility of individually controlling the pressure rings 2, 2.1 for the axial feed movement. In this case, only half of the deformation path 63 (see FIG. 10) that is available per se can be used for any workpieces, possibly also those with a smaller diameter. For this purpose, it is provided that one pressure ring 2 remains extended up to a limit 19 of its axial feed path, while the other pressure ring 2.1 is brought into its end position.

As can further be seen from FIG. 6, devices 54 for holding, centering and for tolerance compensation of an intermediate jaw are provided on the pressing jaws 4 on their outer sides, which are designed for receiving pressing jaws 57 with a smaller nominal width. For this purpose, the devices 54 are designed as holding plates arranged axially on the pressing jaws 4, each of which is tensioned by at least one compression spring 53 against a centering pin 55 which is formed by an opening in the holding plate. The holding plate has in the middle of its diagonals an elongated hole slightly offset from a bore 66, which runs parallel to the axis XX of the press jaws 4. The holding plate is guided by means of dovetail guides on both long sides of the press jaws 4. An intermediate jaw for receiving the pressing jaws 57 of smaller nominal width is inserted through an oblong retaining bolt with an annular groove through the elongated hole of the retaining plate into the bore 66 and axially aligned with the centering pin 55. By means of the compression spring 53, the holding plate is moved back into its starting position, with a portion of the peripheral edge of the elongated hole engages in the annular groove of the retaining bolt arranged on the underside of the intermediate jaw and locks the intermediate jaws. To compensate for tolerances, a resilient pressure piece 56 is arranged in the lower half of the bore 66. that pushes against the lower end of the retaining bolt. This prevents the pressing jaws 57 from wobbling until it lies against the outer surface of the respective workpiece to be pressed.

FIG. 7 shows a radial press with a pressure ring 2 designed as a double-acting hollow piston. An outer annular chamber 23 is provided, which is formed by a recess on the radially outer circumference of the pressure ring 2 and a cylinder jacket. When pressure is applied to the annular chamber 23, the pressure ring 2 is automatically returned to the starting position. The connection between the cylinder base 3 and the counter bearing 5 is made by screws 20. The distance between the end face of the pressure ring 2 and the counter bearing 5 is determined by means of spacer sleeves pushed onto the screws 20. At the same time, this leads to an open design in the area between the pressure ring 2 and the counter bearing 5, which facilitates cleaning of the press.

The latter also applies in the same way to the radial press shown in FIG. 8. As a further special feature, this has a pressure chamber formed by an outer surface of the pressure ring 29, an outer cylinder and an end-side cylinder base 28 with a return piston 25 for the pressure medium drive. The annular piston 25 is connected to the counter bearing via tension rods 17. The ring piston 25 is moved in the direction of the cylinder base 28 by introducing pressure medium. The abutment on the press jaws 4 together with these is axially against the pressure ring 29 pulled, whereby the press jaws 4 are brought into the closed position. The reverse direction of movement takes place by supplying pressure medium through the supply opening provided between the cylinder surface and the pressure ring 28.

The pressure medium drive of the radial press shown in FIG. 9 is also designed as a double-acting piston-cylinder arrangement for a closing and opening movement of the press jaws. For this purpose, a full ring 27 is screwed in at the front end of the pressure ring 2 as a piston with an external thread and sealed with a ring seal.

As can be seen from FIG. 9, in this radial press on the flanks of the parallel arranged control surfaces 30, 32 of the pressure ring 2, end-face sliders 38, 39 are provided, on which the press jaws 4 during the idle stroke movement of the pressure ring 2 while lifting the control surfaces 30 , 31, 32, 33 slide along. The on the flanks between the parallel offset control surfaces 30, 32 of the pressure ring 2 arranged sliding pieces 38 are provided with steep bevels on which the press jaws 4 are guided with rounded control edges 43 formed on their outer surfaces during the idle stroke. The sliding pieces 39 arranged on the end face of the pressure ring 2 have a rounded raised edge, on which the pressing jaws 4 are guided with control edges 43.1 formed on their outer surfaces with adjoining control bevels 42. During the idle stroke movement of the pressure ring 2, the press jaws simultaneously slide up with their rounded control edges 43 on the steep elevation slopes of the slide pieces 38, and the control edges 43.1 with the control bevels 42 of the press jaws 4 thereafter, on the rounded lift edges of the slide pieces 39. As a result, the press jaws are raised radially steep and quickly reduce the opening diameter 61 (see FIG. 10).

Subsequently and simultaneously, the control surfaces 30, 31 and 32, 33 of the pressure ring 2 and press jaws 4 come into engagement. This is associated with a slow axial forward movement of the pressure ring 2 with a radially powerful stroke of the pressing jaws 4 inwards in the direction of the axis XX. This embodiment of a radial press also reveals the short axial overall length, which is advantageous for great freedom of movement on the back of the pressure ring.

Reference symbol list:

2nd

Pressure ring

2.1

Pressure ring

3rd

Cylinder bottom

4th

Press jaws

5

Counter bearing

6

Washer

7

Ring seal

8th

Screws

9

Back parts

10th

Spring bearing

11

Incline

11a

Incline

14

Compression springs

15

Compression springs

16

Cylinder jacket

17th

Tension rods

18th

Cylinder jacket

19th

Limitation

20th

Screws

21

Pressure bars

22

Ring piston

23

Ring chamber

24th

Ring seal

25th

Ring piston

26

Sealing ring

27

Full ring

28

Cylinder bottom

29

Pressure ring

30th

Control surface

31

Control surface

32

Control surface

33

Control surface

34

Elevation slope

34a

Elevation slope

35

Control edge

36

Endpoint

37

Incline

37a

Incline

38

Slider

39

Slider

40

Side guide

41

Dirt scraper

42

Elevation slope

42a

Elevation slope

43

Control edge

43.1

Control edge

44

Micrometer

45

Adjusting screw

47

Limit switch

48

casing

49

Flattening

50

Line connection

51

Line connection

53

Compression spring

54

Press jaw holder

55

Centering

56

Pressure piece

57

Press jaws

61

Opening diameter

62

Press diameter

63

Deformation path

64

Elevation slope

64a

Elevation slope

66

drilling

Claims (18)

1. Radial press for workpieces having a substantially cylindrical outer surface, comprising a plurality of pressure clamps (4) arranged circularly around the axis (X-X) of the radial press, which are guided along an axial counter support (5) radially movable with respect to the axis (X-X) and the outer surfaces of which each comprise control surfaces (31, 33, 64, 64a) differently inclined relative to the axis (X-X) and axially displaced relative to each other as well as a pressure ring (2) axially displaceable by means of a pressure means drive relative to the pressure clamps (4), the inner surface of the pressure ring (2) comprising control surfaces (30, 32, 34, 34a) differently inclined and axially displaced relative to each other, coming into engagement with the corresponding control surfaces (31, 33, 64, 64a) of the pressure clamps (4) when the pressure ring (2) is axially displaced to close the pressure clamps (4), whereby as a consequence of the different inclinations of the control surfaces displaced axially the pressure clamps (4) first move radially inward in fast idle stroke and then in slow power stroke and whereby the pressure clamps (4) in the region of their idle stroke movement are guided along the pressure ring (2) while lifting the control surfaces (30, 31, 32, 33) of the pressure ring (2) - or respectively - the pressure clamps (4) provided for the power stroke, characterized in that the control surfaces (34, 34a) of the pressure ring (2) provided for the idle stroke are each formed as two lifting inclinations being arranged as seen in circumferential direction of the pressure ring (2) at both sides of each of the control surfaces (30, 32) of the pressure ring (2) provided for the power stroke and that the control surfaces (64, 64a) of the pressure clamps (4) provided for the idle stroke are arranged complementary to the lifting inclinations (34, 34a) of the pressure ring (2) as lifting inclinations which are arranged at the side surfaces of each pressure clamp (4) being substantially transverse to the circumferential direction.
2. Radial press according to claim 1, characterized in that the lifting inclinations (34, 34a) of the pressure ring (2) are formed to lift the control surfaces (30, 31, 32, 33) of the pressure ring (2) and the pressure clamps (4) provided for the power stroke during their idle stroke movement to an extent appropriate to the pretension of a dirt stripper (41) arranged at each pressure clamp (4) which during power stroke movement is in engagement with the respective control surface (30, 32) of the pressure ring (2).
3. Radial press according to claim 1 or 2, characterized in that the lifting inclinations (34, 34a) of the pressure ring (2) are out of touch with the pressure clamps (4) during power stroke movement.
4. Radial press according to claims 2 or 3, characterized in that in axial direction the pressure clamps (4) each comprise two control surfaces (31, 33) for the power stroke displaced relative to each other in parallel and that the pressure ring (2) comprises control surfaces (30, 32) for the power stroke substantially complementary to the control surfaces (31, 33) of the pressure clamps (4).
5. Radial press according to one of claims 2 to 3, characterized in that the lifting inclinations (34, 34a) of the pressure ring (2) are arranged at side guides (40) for the pressure clamps (4).
6. Radial press according to one of claims 2 to 5, characterized in that in closing direction of the pressure ring (2) the lifting inclinations (34, 34a) merge into downward inclinations (37, 37a) adjoining axially with a small inclination angle relative to the axis (X-X).
7. Radial press according to one of claims 2 to 6, characterized in that adjacent lifting inclinations (34, 34a) of the pressure ring (2) which may merge into downward inclinations (37, 37a) are formed as flat back parts (9) between which the control surfaces (30, 32) of the pressure ring (2) provided for the power stroke are depressedly formed (Fig. 2).
8. Radial press according to one of claims 2 to 7, characterized in that the lifting inclinations of the pressure clamps (4) are provided as sideward pins, bolts or similar gliding elements gliding at the lifting inclinations (34, 34a) and possibly at the downward inclinations (37, 37a) of the pressure ring (2) during an idle stroke movement.
9. Radial press according to one of claims 1 to 8, characterized in that the control surfaces (30, 32) of the pressure ring (2) provided for the power stroke are formed as glide bearing surfaces preferably made of PTFE.
10. Radial press according to one of claims 1 to 9, characterized in that facial gliding pieces (38, 39) are provided at the flanks of the control surfaces (30, 32) of the pressure ring (2) displaced relative to each other in parallel and provided for the power stroke, along which the pressure clamps (4) glide during the idle stroke movement of the pressure ring (2).
11. Radial press according to claim 10, characterized in that the gliding pieces (38) have steep lifting inclinations along which the pressure clamps (4) are guided with control edges (43) which may be rounded and provided at their outer surfaces, preferably at their front ends, and/or that the gliding pieces (39) have a preferably rounded lifting inclination along which the pressure clamps (4) glide with their control edges (43.1) formed at their outer surfaces together with adjacent control inclinations (42) during the idle stroke movement.
12. Radial press according to one of claims 1 to 11, characterized in that two pressure rings (2, 2.1) axially facing each other are provided being axially displaceable towards each other to close the pressure clamps (4) arranged between them by means of pressure means drives and that the respective pressure clamps (4) axially facing each other support each other.
13. Radial press according to claim 12, characterized in that the pressure means drives provided for the axial displacement of the pressure rings (2, 2.1) are placed in parallel, and/or that the respective opposite pressure clamps (4) are made of a one-piece structure.
14. Radial press according to claim 12 or 13, characterized in that the pressure clamps (4) at their outer surfaces comprise devices for holding, centering and tolerance-balancing an intermediate clamp which is adapted to receive pressure clamps (57) of a minor nominal width.
15. Radial press according to one of claims 1 to 14, characterized in that the pressure ring/s (2, 2.1) is/are provided as spring-loaded ring/s or hollow piston/s of the pressure means drive being guided along a radial outer cylinder wall (16, 18) and a cylinder bottom (3) located in a recess of the pressure ring (2, 2.1).
16. Radial press according to claim 15, characterized in that the cylinder wall (16) is connected to the counter support and serves as a connecting member for the transfer of the reaction forces.
17. Radial press according to one of claims 1 to 12, characterized in that the pressure means drive comprises a ring piston (25) guided between an outer surface of the pressure ring (29) and an outer cylinder, the counter support (5) abutting the pressure clamps (4) being fastened to the piston rod of the ring piston which is preferably formed as a tension rod (17) which counter support (5) when a pressure is applied is dosplaced axially with the pressure clamps (4) in the direction of the pressure ring (29) fixedly arranged with reference to the housing (48) (Fig. 8).
18. Radial press according to one of claims 1 to 17, characterized in that the pressure means drive/s is/are provided as double-effective piston-cylinder arrangements for a closing and an opening movement of the pressure clamps (4).

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