RADIAL PRESS

Abstract

A radial press is provided having a first and a second ring structure extending about a press axis. Multiple press bodies are arranged about the press axis between the ring structures and are movably supported on support surfaces paired with the ring structures. The axial distance between the two ring structures can be changed using a drive system having a plurality of actuators oriented parallel to the press axis and distributed about the press axis. The support surfaces paired with one of the two ring structures are inclined relative to the press axis, and the press bodies are guided in a forced manner relative to the two ring structures in that the press bodies are equipped with guide grooves into which guide bodies engage.

Claims

1. A radial press (1) with a first and a second ring structure (2; 3) extending around a press axis (X) and, disposed between them around the press axis (X), several pressing elements (8) displaceably braced at bracing faces (11; 12) associated with the ring structure (2; 3), wherein the axial distance of the two ring structures (2, 3) from one another can be varied by means of a drive system, which comprises a multiplicity of actuators (C) oriented parallel to the press axis (X) and disposed in distributed manner around it, of which respectively a first component is coupled with a first of the two ring structures and a second component, actively movable relative to the first component, is coupled with the second ring structure, and wherein furthermore at least the bracing faces (11) associated with one of the two ring structures (3) are oriented at an inclination to the press axis (X) and the pressing elements (8) are guided compulsorily relative to the two ring structures (2, 3), wherein the compulsory guidance (18, 19) takes place respectively via the pressing elements (8) and pairs, associated with the ring structure (2, 3) in question, of guide slots (20, 24) made in the pressing elements (8) and guide elements (21), comprising guide rollers (23, 26), engaging in these.

2. The radial press of claim 1, wherein the guide rollers (23, 26) are respectively mounted on a bolt constructed as a positioning cam.

3. The radial press of claim 1, wherein the pressing elements (8) comprise base jaws (16) and pressing jaws (17) that can be fastened exchangeably to these.

4. The radial press of claim 3, wherein the extent of the base jaws (16) parallel to the press axis (X) is at least twice as large as transversely relative thereto and/or in that a hydraulically actuatable interlock system acts between the base jaws (16) and the pressing jaws (17).

5. The radial press of claim 1, wherein only the bracing faces (11) associated with one of the two ring structures (2, 3) are inclined relative to the press axis (X), whereas the bracing faces (12) associated with the other ring structure (2) are oriented perpendicular to the press axis (X).

6. The radial press of claim 5, wherein the ring structure (2) having bracing faces (12) oriented perpendicular to the press axis (X) is constructed as a stationary ring structure (40).

7. The radial press of claim 6, wherein a displacement-measuring device (29) with radially oriented measuring direction acts between the stationary ring structure (40) and at least one of the pressing elements (8).

8. The radial press of claim 1, wherein the press axis (X) is vertically oriented, wherein one of the ring structures forms a lower ring structure (2) and the other ring structure forms an upper ring structure (3), wherein preferably the lower ring structure (2) is braced via a load-bearing structure (4) on the foundation but is spaced apart from it.

9. The radial press of claim 8, wherein the upper ring structure (3) is braced on the lower ring structure (2) at least in the scope of a substantial part of its own mass as well as of that of the components, associated with it, of the actuators via spring elements (70), wherein preferably spring elements (70) constructed as gas springs (71) act between the lower ring structure (2) and the components, associated with the upper ring structure (3), of the actuators.

10. The radial press of claim 1, wherein a hydraulic drive system is provided wherein the actuators (C) are constructed as hydraulic cylinder-piston units (33), of which respectively the cylinder (35) forms the first component and the piston rod (39) forms the second component of the actuator (C) in question.

11. The radial press of claim 10, wherein the cylinder-piston units (33) are constructed as synchronizing cylinders (34), wherein preferably a valve unit (45) permitting a direct hydraulic short circuit of the two working chambers (A, B) of the synchronizing cylinder (34) in question is associated with each synchronizing cylinder (34).

12. The radial press of claim 11, wherein the valve units (45) are disposed respectively at the end of the associated piston rod (39), provided with supply ducts (46, 47).

13. The radial press of claim 1, wherein an electromechanical rapid positioning drive (51) comprising several positioners (53) is provided.

14. The radial press of claim 13, wherein the rapid positioning drive (51) comprises a common servo motor (64) acting on all positioners (53).

15. The radial press of claim 13, wherein the positioners (53) act respectively between the components, actively positionable relative to one another, of an actuator, especially between the cylinder (35) and the piston rod (39) of a hydraulic cylinder-piston unit (33).

Description

BRIEF DESCRIPTION OF THE DRAWING

[0027] The present invention will be explained in more detail in the following on the basis of a preferred exemplary embodiment, illustrated in the drawing, wherein

[0028] FIG. 1 shows the radial press in question in perspective view obliquely from above,

[0029] FIG. 2 shows, in an angled view similar to that of FIG. 1, the radial press shown therein in cutaway representation,

[0030] FIG. 3 shows a section from FIG. 2 on an enlarged scale,

[0031] FIG. 4 shows, in perspective view obliquely from above, one of the eight hydraulic cylinder-piston units of the radial press shown in FIGS. 1-3 and

[0032] FIG. 5 shows one of the eight pressing elements of the radial press according to FIGS. 1-3 without the associated panel.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0033] Radial press 1, illustrated in the drawing, designed for operation with vertical press axis X, comprises a first, lower ring structure 2 and a second, upper ring structure 3. Both ring structures 2, 3 extend around press axis X. This lower ring structure 2 is constructed as a stationary ring structure and is braced via beams 4 on the foundation. The second, upper ring structure 3 can be raised and lowered by means of a drive system, which comprises eight actuators C disposed around the press axis and oriented parallel thereto, i.e. the spacing of upper ring structure 3 relative to lower ring structure 2 can be decreased and increased by means of the drive system. The lower ring structure has a pot-like basic shape (with an open region at the center!), by the fact that it has a bottom ring 6 and a substantially cylindrical wall 7 towering from it; it is so dimensioned that lowered upper ring structure 3 is inserted into lower ring structure 2 in the sense that it and cylindrical wall 7 of lower ring structure 2 overlap one another.

[0034] Furthermore, the radial press comprises, disposed uniformly around press axis X, eight pressing elements 8, which - via associated upper mating faces 9 and lower mating faces 10 - are respectively braced in slidingly displaceable manner on an upper plane bracing face 11 associated with upper ring structure 3 as well as on a lower plane bracing face 12 associated with lower ring structure 2. These upper bracing faces 11 are respectively constructed on the surface of an exchangeable upper sliding plate 13, and the lower bracing faces 12 are respectively constructed on the surface of an exchangeable lower sliding plate 14. Whereas lower bracing faces 12 (as well as associated lower mating faces 10) stand perpendicular to press axis X, upper bracing faces 11 (as well as associated upper mating faces 9) are oriented at an inclination to press axis X. Thus upper bracing faces 11 represent “control faces”, via which an axial movement of upper ring structure 3 is transformed into a radial movement of pressing elements 8. Upper ring structure 3 thus forms a “control ring” 15.

[0035] Pressing elements 8 comprise base jaws 16, on which upper and lower mating faces 9 and 10 are constructed, and pressing jaws 17 that can be attached exchangeably to base jaws 16. Each of the base jaws 16 - the extent of which parallel to press axis X is approximately twice as large as transversely relative thereto - is guided on upper ring structure 3 via an upper compulsory guide 18 and on lower ring structure 2 via a lower compulsory guide 19 in such a way that it is held (at least substantially) without clearance on the two associated bracing faces 11 and 12, i.e. it cannot be raised from them. Upper compulsory guide 18 then comprises two guide slots 20 machined laterally in base jaws 16 in question and extending parallel to upper mating face 9 and, engaging therein and disposed on upper ring structure 3, guide elements 21 in the form of roller arrangements 23 attached to an (upper) roller carrier 22. Correspondingly, lower compulsory guide 19 has its guide slots 24 and roller arrangements 26 attached to (lower) roller carriers 25. The individual rollers are then respectively mounted on a bolt constructed as a positioning cam. For guidance of base jaws 16 in circumferential direction, sliding plates 27, which respectively define a bracing face and on which base jaws 16 are braced via associated mating faces 28, are attached to upper roller carriers 22.

[0036] Respectively one displacement-measuring device 29 (with measuring direction parallel to lower compulsory guides 19, i.e. oriented radially), by means of which respectively the relative position of the base jaw 16 in question relative to lower ring structure 2 can be indicated, is associated with at least one part of pressing elements 8. Displacement-measuring device 29 in question comprises a pin 30 connected with the base jaw 16 in question and projecting downward from this with a transducer 31, which is disposed on its end and which cooperates with an associated ruler 32 fixed on lower ring structure 2 and extending radially.

[0037] The drive system used for relative movement of the two ring structures 2 and 3 relative to one another is hydraulically constructed; it comprises - as actuators C -eight hydraulic cylinder-piston units 33 oriented parallel to press axis X and a pressure-supply unit (not illustrated but of customary construction) having a tank, a motor-pump unit and a controller. Hydraulic cylinder-piston units 33 - respectively disposed with gaps on pressing elements 8 - are constructed as synchronizing cylinders 34. Via an associated flange 37 formed on cylinder bottom 36, cylinder 35 is respectively joined securely with upper ring structure 3 (control ring 15). Lower end 38 of the respective piston rod 39 extending through cylinder 35 is accordingly joined securely with lower ring structure 2 (“bracing ring” 40).

[0038] Two hydraulic working chambers A and B, bounded off from one another by piston 42, which is securely joined with piston rod 39, are defined in each hydraulic cylinder-piston unit 33, within the respective cylinder 35, which is closed at the top by a cover 41 with through-bore. These are supplied through piston rod 39 with through-bore. A valve unit 45 is built onto upper end 43 of piston rod 39 passing through through-bore 44 of cover 41 - or possibly on an assembly plate (see below) joined to it. This respectively has four ports a, b, c, d; via two of these (ports a and b), it communicates with the pressure-supply unit, whereas the two other ports c and d communicate with supply ducts 46 and 47 extending within piston rod 39 and supplying the two working chambers A and B. The two switching valves 49 integrated in the respective valve unit 45 and actuatable via an electrical actuator 48 permit changeover between on the one hand fluidic communication of the two working chambers A and B with the pressure-supply unit (via respectively a passing connection of port a with port c and of port b with port d) and on the other hand a direct hydraulic short circuit of the two working chambers A and B via an internal bypass 50, via which ports c and d communicate fluidically with one another. In the said second switched position, the two working chambers A and B are shut off from the pressure-supply unit by means of switching valve 49.

[0039] The said bypasses 50 are opened when rapid positioning of the two ring structures 2 and 3 toward one another is taking place by means of a rapid positioning drive 51. This is electromechanically constructed and comprises a drive unit 52, four positioners 53 and one drive train 56 provided with drive unit 52 with shafts 54 and angle gear mechanisms 55 joining the four positioners 53. A hydraulic cylinder-piston unit 33 -acting between cylinder 35 and piston rod 39 - is associated with each of the four positioners 53 (constructed as rack-and-pinion units 57). For this purpose, a toothed gear, which is mounted rotatably in a toothed pinion housing 59, is engaged with a toothed rack 58 fixed on the cover 41 of the respectively associated hydraulic cylinder-piston unit 33. This toothed-pinion housing 59 is built onto an assembly plate 60, which in turn is securely joined with the end portion, projecting from cover 41, of piston rod 39 of the hydraulic cylinder-piston unit 33 in question. Four displacement-measuring systems 61, having respectively one ruler 62 fixed on cover 41 of the associated hydraulic cylinder-piston unit 33 and one transducer 63 fixed on the assembly plate 60 in question are provided functionally in parallel with the four positioners 53.

[0040] Drive unit 52, which is likewise joined (at least indirectly) in positionally invariable relationship to piston rod 39 of the hydraulic cylinder-piston unit 33, in question and in particular is built onto valve unit 45 associated with this, comprises a servo motor 64 with a flange-connected, self-locking planetary gear mechanism 65, an electromechanical separating clutch 66, an input 67 used for manual actuation and a distributing gear mechanism 68 with two outputs 69, to which associated shafts 54 of drive train 56 are connected.

[0041] The unit consisting of upper ring structure 3 and the eight cylinders 35, joined thereto, of hydraulic cylinder-piston units 33, is braced at least in the scope of a substantial part of its mass via spring elements 70 on lower ring structure 2. For this purpose, gas struts 71 extend between respectively a lower link point 72 associated with lower ring structure 2 and an upper link point 73 associated with cover 41 of a hydraulic cylinder-piston unit 33.

[0042] As regards the fixation, on base jaws 16, of the pressing jaws 17 that can be attached exchangeably to base jaws 16, hydraulically actuatable interlocks, which permit automated fitting of the eight base jaws 16 with a set of pressing jaws, are provided for the purpose - respectively protected by a panel 74 in ready-to-operate condition of radial press 1. The interlocks comprise respectively one clamping unit 76, which is attached to base body 75 of the base jaw and has a pivotably driven claw, which pulls the respective pressing jaw 17 - bearing on reinforcing rail 77 of base body 75 of the base jaw - radially outward to its interlocking position defined by stops 78. Furthermore, the interlock respectively comprises, disposed in pairs on base body 75 of the base jaw, two hydraulic cylinders 79 having, attached to the respective piston rod, interlocking heads 80, which press the pressing jaw 17 in question into the associated seat of base body 75 of the base jaw. A mechanical spring 81 then supports respectively the hydraulic cylinder 79 in question and ensures that the pressing jaw 17 in question is also held without external energy on the respective base jaw 16, i.e. does not tilt due to its own weight. The position of interlocking heads 80 is detected by means of sensors 82, which are attached via angle pieces 83 to base body 75 of the base jaw.