radial press

Abstract

The invention relates to a radial press of the toggle press construction type, comprising a fixed toggle (1), a movable toggle (2), a press drive (3) which effects the closing movement of the movable toggle (2) relative to the fixed toggle (1), and an integral ring-shaped closed frame (9) which encloses the aforementioned components. Here, the fixed toggle (1) and the movable toggle (2) together define a tool mounting space in which a pressing tool (5) is accommodated, the pressing tool (5) having a plurality of press jaws (6) which are arranged around the press axis. The press drive (3) comprises at least two hydraulically operated cylinder-piston units (10) which are oriented parallel to one another and are spaced apart from one another transversely to the press axis. A drive bracket (12) is provided, against which the frame (9) is wrapped at least 160° against an arcuate support surface (16) of the drive bracket. The drive bracket (12) has a number of receptacles (38) corresponding to the number of cylinder-piston units (10), into which the pistons (39) of the cylinder-piston units (10) sink.

Description

[0001] This invention relates to a radial press of a yoke press structure, comprising a fixed yoke, a movable yoke, a press drive, and an integral annular closed frame. The press drive enables the movable yoke to close relative to the fixed yoke. The frame surrounds the aforementioned components. The fixed yoke and the movable yoke together define a tool mounting space, in which a pressing tool is accommodated. The pressing tool has multiple pressing claws arranged around the press axis.

[0002] Radial presses with a yoke press structure have been known for decades and have been proven in practical use. For relevant prior art, see, for example, DE 41 35 465 A1. Yoke presses with a housing or frame structure having a lateral supply port (see DE 199 40 744 A1 and DE 198 17 882 A1) facilitate operation for various applications or are even essential for certain applications, through which the workpiece can be inserted from the side into the open pressing tool. However, under very high pressures, these radial presses reach their limits due to the risk of deformation (due to the asymmetrical housing or frame structure). Here, a radial press designed with a yoke press structure is advantageous, having tie rods coupled to the movable yoke on both sides of the tool mounting space (see DE 41 35 465 A1, as above), or a closed, surrounding frame structure coupled to a fixed yoke. The radial presses mentioned later, such as those corresponding to the radial presses of the same structural form given above, are known in particular by US 8 266968 B2, DE 199 12 976 A1, CA 2 005 264 A and DE 10 2016 102 275 A1.

[0003] Against the backdrop of a growing demand for radial pressing performed at very high pressures, the objective of this invention is to provide a radial press of the same type, characterized by a particularly advantageous power-to-weight ratio. In other words, the goal is to provide a radial press of the same type with a high power-to-weight ratio (in the sense of maximum pressure). This advantageous power-to-weight ratio is particularly important for radial presses designed for particularly high pressures (e.g., greater than 15,000 kN), as it keeps manufacturing costs (which largely depend on the amount of material used) on an acceptable order of magnitude.

[0004] The aforementioned task is achieved in the following way: in radial presses of the same type The press drive device includes at least two parallel-oriented hydraulic cylinder-piston units, which are spaced apart from each other transversely to the press axis. - A drive bracket is provided, and the frame abuts against the arched support surface of the drive bracket to surround the drive bracket at least 160°, and - The drive bracket has a number of receiving portions corresponding to the number of hydraulic cylinder-piston units, and the pistons of the hydraulic cylinder-piston units sink into the receiving portions.

[0005] The outstanding feature of the radial press according to the invention, through the synergistic interaction of its various structural features, is its ability to achieve a very uniform stress distribution while having only minimal local stress peaks. Thus, even the reaction forces generated under very high pressures can be controlled by structures—measured by the performance of the radial press and compared to radial presses with structures known to date—that can be manufactured with lower material consumption and thus lower cost; and similarly—measured by the performance of the radial press—the low weight of the radial press is also a significant advantage of the invention. Another highly practical advantage associated with the structure of the radial press according to the invention is that the radial press can be optimized in terms of particularly simple replacement of components of the yoke and press drive without sacrificing performance.

[0006] According to a first preferred embodiment of the invention, the drive bracket support surface presents a cylindrical section. This not only directly and advantageously affects the stress distribution established within the frame, but more precisely, another advantage of this design is the particularly simple possibility of achieving a defined, desired sliding between the frame and the drive bracket during the pressing process, even if elongation of the frame is intentionally taken into account. Furthermore, it is even more advantageous in this case if the frame and drive bracket are only partially fixed to each other, particularly at the apex of the frame, while the frame slidably rests against the drive bracket support surface for the remainder. These advantages are particularly pronounced if the frame rests against the arched support surface of the drive bracket, wrapping around the drive bracket at 180°.

[0007] Another highly advantageous improvement of the invention is characterized in that the cylinder body of the hydraulic cylinder-piston unit is an integrated part of the drive bracket, such that the receiving portion of the drive bracket forms the cylinder body of the hydraulic cylinder-piston unit. Therefore, the static mechanical strength requirements for the cylinder body of the hydraulic cylinder-piston unit are met by the receiving portion integrally formed on the drive bracket with the drive bracket, but this does not preclude the use of separate cylinder liners for the internal lining of the cylinder body of the hydraulic cylinder-piston unit, especially when the drive bracket is manufactured using casting processes (e.g., particularly from gray cast iron). This improvement exhibits particular advantages if the press drive includes exactly two hydraulic cylinder-piston units. Furthermore, it is desirable that there exists—for example, through a sliding surface mating pair—transverse mobility to the axis of the respective hydraulic cylinder-piston unit between the piston and the movable yoke of the hydraulic cylinder-piston unit; in this way, possible lateral forces on the piston are minimized, which helps to mechanically protect the hydraulic cylinder-piston unit, thereby extending its service life.

[0008] In particular, when the press drive includes a greater number of hydraulic cylinder-piston units, it proves advantageous to integrate the press drive into other designs of the drive bracket, where the hydraulic cylinder-piston units are independent components with their cylinder bodies inserted into the receptacles of the drive bracket. Here, commercially available cylinder-piston units can even be used, ideally supported on the drive bracket without torque. The design describes how the pistons of the hydraulic cylinder-piston units are recessed into corresponding receptacles of the drive bracket. As indicated in the preceding description of a preferred embodiment of the invention, the phrase "the pistons of the hydraulic cylinder-piston units are recessed into corresponding receptacles of the drive bracket" should not be (erroneously) interpreted as meaning that the pistons functionally cooperate with the receptacles; in this respect, it relates more to geometric relationships.

[0009] Depending on the specific design of the radial press according to the invention, at least one hydraulic booster is provided to the hydraulic cylinder-piston unit of the press drive. In common applications of the invention, preferably, the hydraulic booster is structurally integrated into the drive bracket, such that the hydraulic booster has a housing integrally formed with the rest of the drive bracket. However, in some cases, although typically at the cost of a higher overall weight for the radial press, it has proven advantageous to have the hydraulic booster as a separate component mounted on the drive bracket.

[0010] Depending on another preferred improvement according to the invention, corresponding to the support of the drive bracket on the frame according to the invention, it is advantageous if the frame abuts against the arched support surface of the fixed yoke and surrounds the fixed yoke at least 160°, particularly preferably 180°, wherein, in particular, the yoke support surface may also present a cylindrical section. The advantages set forth and described above are applied here in a corresponding manner.

[0011] Regarding the arrangement of the two yokes, according to another preferred improvement of the invention, the fixed yoke forms the lower yoke, and the movable yoke forms the upper yoke. This is particularly suitable for workpieces of particularly large size (e.g., Radial presses designed for applications such as >500mm and particularly high pressures (e.g., >10000 kN) to be applied to workpieces; because in such cases, each yoke has a large mass, which acts to increase the pressure when the movable yoke is set as the upper yoke.

[0012] According to yet another preferred improvement of the invention, the frame has two arc segments and two tension segments, each arc segment describing a 180° arc, and the two tension segments connecting these two arc segments, the two tension segments being parallel to each other and parallel to the orientation of the hydraulic cylinder-piston unit. This orientation of the tension segments ensures that they are not subjected to shear stress, i.e., only tensile loads. This also contributes to optimal stress distribution and thus optimal utilization of the materials used. It is particularly advantageous that the extension dimension of the frame parallel to the press axis is smaller, at least in a portion of the arc segments, than in the tension segments. The larger extension dimension of the frame parallel to the press axis relative to the arc segments in the two tension segment regions ensures that the frame has enhanced resistance to deformation that could lead to limited radial pressing quality (e.g., pressing taper). Also contributing to this is if, according to yet another preferred improvement of the invention, a guide structure for the movable yoke is provided in the region of the tension segment of the frame. It is particularly advantageous if the guide element fixed to the movable yoke engages with a corresponding groove in the tension segment of the frame and is movably guided therein. This implementation of the guide structure for the movable yoke does not impede the expected, definite elongation of the tension section during pressing. For this form of guide structure for the movable yoke, the above-described embodiment of the frame has proven particularly advantageous, i.e., the tension section is designed, at least locally—in the direction parallel to the press axis—to be wider than the arc segment. However, in individual cases, it may also prove advantageous if the frame has the same extension dimension parallel to the press axis in all locations, i.e., in both its tension section and its arc segment, and the tension section is even narrower than the arc segment.

[0013] According to yet another preferred improvement of the invention, in a radial press having a press drive comprising exactly two hydraulic cylinder-piston units, at least one rapid advance and return stroke adjuster acting on the movable yoke is provided on the drive bracket between the cylinder bodies of the hydraulic cylinder-piston units. Particularly preferred is the provision of two (or more) rapid advance and return stroke adjusters in the form of hydraulic cylinder-piston units spaced apart from each other in a parallel orientation along the press axis. Preferably, a reinforcing web of the drive bracket, oriented transversely to the press axis, extends between the two rapid advance and return stroke adjusters, the reinforcing web transitioning at its end to its receiving portion, and if necessary, to the cylinder body of the two hydraulic cylinder-piston units of the press drive formed by the receiving portion. Particularly preferred is that the at least one rapid advance and return stroke adjuster can be replaced without additional disassembly work; this allows the radial press to be adapted to different requirements or tasks without the significant associated overhead.

[0014] Furthermore, it is particularly advantageous if at least two displacement measuring sensors, preferably four, act between the fixed yoke and the movable yoke, and the signals from these sensors are transmitted to the press controller. This allows for the early detection of potential pressing asymmetries before irreversible damage occurs to the workpiece, which in turn allows for correction of the pressing. In particular, this is a decisive factor in the fact that the radial press according to the invention, due to its structural type, is preferably used for radially deforming particularly large, complex, and expensive workpieces; by identifying potential erroneous strokes of radial deformation early and fully utilizing the possibility of corrective intervention, scrap can be avoided, which constitutes a very direct cost aspect.

[0015] The invention will now be described in more detail with reference to two preferred embodiments shown in the accompanying drawings. Wherein: Figure 1 A radial press according to the first embodiment is shown in a perspective view. Figure 2 Showing according to Figure 1 Front view of the radial press. Figure 3 The left side shows the basis Figure 1 and Figure 2 Side view of the radial press. Figure 4 Showing according to Figures 1 to 3 radial press along Figure 2 Vertical sectional view of line IV-IV in the middle. Figure 5 Showing according to Figures 1 to 4 A top view of the radial press. Figure 6 Showing according to Figures 1 to 5 radial press along Figure 2 The horizontal sectional view of line VI-VI in the middle, and Figure 7 Showing according to Figures 1 to 6 radial press along Figure 2 A horizontal sectional view along line VII-VII. Conversely, Figure 8 A partially sectional front view of the upper region of the radial press according to the invention, based on a second embodiment, is shown.

[0016] In the attached diagram Figures 1 to 7 The radial press shown, implemented using a yoke press structure, includes a fixed yoke 1, a movable yoke 2, and a press drive 3 that enables the movable yoke 2 to close relative to the fixed yoke 1. The fixed yoke 1 and the movable yoke 2 together define a tool mounting space 4, in which a pressing tool 5 is housed, and has multiple pressure claws 6 arranged around the press axis X. Through the support and control surfaces of the two yokes 1 and 2 and the pressure claws 6 interacting in a known manner, the closing motion of the movable yoke 2 (arrow A) is converted into a radially inward movement of the pressure claws 6 oriented towards the press axis X. This design, which essentially constitutes a yoke press, and its structural implementation are fully described in the prior art and therefore need not be repeated here.

[0017] In the radial press shown, the fixed yoke 1 forms the lower yoke 7, and the movable yoke 2 forms the upper yoke 8. The press drive 3 is positioned above the upper yoke 8 and acts directly on it. Force transmission (between the lower yoke 7 and the press drive 3) is achieved through an integral (i.e., a casting designed for rework) frame 9, which circumferentially surrounds the lower yoke 7, the upper yoke 8, and the press drive 3.

[0018] The press drive unit 3 includes two hydraulic cylinder-piston units 10 oriented parallel to each other, each hydraulic cylinder-piston unit 10 having a vertical axis parallel to the closed motion A of the upper yoke 8. These two cylinder-piston units 10 are arranged side-by-side, and specifically transverse to the press axis X, i.e., spaced apart from each other in a plane perpendicular to the press axis X. The two cylinder bodies 11 of each hydraulic cylinder-piston unit 10 are formed by integrally constructed, downward-opening sleeve-like receiving portions 38 on the drive bracket 12; in this way, the receiving portions 38 are integrated parts of the drive bracket 12, which also has webs and ribs that reinforce the structure, particularly a reinforcing web 13 that extends transversely to the press axis X between the two receiving portions 38 or between the cylinder bodies 11 formed through the receiving portions 38, transitioning at the end to the receiving portions 38. The drive bracket 12 is defined upward by an end arch 14, which widens in the orientation of the press axis X. The outer surface 15 of the end arch 14 forms an arched support surface 16 for the frame 9. The end arch 14 has two widened foot sections 17 that transition to the bottom 18 of the cylinder body 11 of the two hydraulic cylinder-piston units 10. The arched support surface 16 formed on the end arch 14 transitions to a support surface section 19 formed on the cylinder body 11 of the hydraulic cylinder-piston unit 10. The entire drive bracket support surface 20 (i.e., the arched support surface 16 formed on the end arch 14 together with the two support surface sections 19) is located in a 180° section of the cylinder, and the two support surface sections 19 respectively form extensions on the cylinder body 11. The frame 9 has an upper arc segment 21 in this manner, which is described as a 180° arc and abuts against the drive bracket support surface 16 to wrap around the drive bracket 12 at a 180° angle.

[0019] The fixed yoke 1 (i.e., the lower yoke 7 in the current case) faces away from the outer surface 22 of the tool mounting space 4, and the yoke support surface 23 is described in a manner similar to that of the previously described drive bracket 12, which is also located in the 180° section of the cylinder. The frame 9 has a lower arc segment 24, described as a 180° arc, which abuts against the arched yoke support surface 23 and wraps around the lower yoke 7 at a 180° angle. It should be noted that the two arc segments 21 and 24 of the frame 9 are planarly abutted against the drive bracket support surface 16 or the yoke support surface 23; however, these two arc segments 21 and 24 are not fixed to the drive bracket 12 or the lower yoke 7 in such a way that, in the event of sliding on the support surfaces 16 and 23 of the drive bracket 12 or the lower yoke 7, this arrangement would impede or even prevent the relevant arc segments 21 and 24 from elongating under load. In this regard, the positions of the drive bracket 12 and the lower yoke 7 on the frame 9 are fixed only at the upper apex of the upper arc segment 21 or the lower apex of the lower arc segment 24, and are achieved solely by clamping using the upper jaw pair 25 or the lower jaw pair 26, with the upper jaw pair 25 fixed to the drive bracket 12 and the lower jaw pair 26 fixed to the lower yoke 7. This avoids the need for holes, especially threaded holes, in the arc segments 21 and 24 of the frame 9.

[0020] Furthermore, the frame 9 also has two tension sections 27 that connect the two arc segments 21 and 24 to each other. The two tension sections 27 are parallel to each other and parallel to the orientation of the hydraulic cylinder-piston unit 10. These two tension sections 27 are designed to be wider relative to the arc segments 21 and 24, such that the extension dimension of the frame 9 parallel to the press axis X is smaller than that of the tension sections 27 at least in a portion of the arc segments 21 and 24. This increases the stiffness of the frame 9 about a horizontal axis oriented transverse to the press axis X and transverse to the direction of movement A of the upper yoke 8, thereby preventing the lower yoke 7 and the drive bracket 12 from tilting relative to each other. Furthermore, the corresponding widened areas of the two tension sections 27 are also designed to guide the (movable) upper yoke 8. For this purpose, the tension section 27 of the frame 9 has a groove 28 that extends parallel to the direction of movement A of the upper yoke 8. A guide element 29 is in the form of a guide plate 30 fixed to the upper yoke 8 and (movably) embedded in the groove 28. Therefore, it is not necessary to provide threaded holes or other holes in frame 9 to guide the yoke 8. This is beneficial to the integrity of the frame and thus promotes optimal, undisturbed force transmission.

[0021] The hydraulic cylinder-piston unit 10 of the press drive unit 3 is designed as a single-acting hydraulic cylinder. The lifting of the upper yoke 8 to open the radial press is achieved by two separate return stroke adjusters 31 acting on the upper yoke 8. The return stroke adjusters 31 are located between the cylinder bodies 11 of the two hydraulic cylinder-piston units 10. The return stroke adjusters 31 are arranged parallel to the hydraulic cylinder-piston units 32 and spaced apart from each other along the press axis X. The cylinder bodies 33 of the two return stroke adjusters 31 are connected here to the drive bracket 12, i.e., to the rib 34, which extends laterally from the reinforcing web 13 in the manner of an inverted T-shaped profile between the two cylinder bodies 11 of the hydraulic cylinder-piston unit 10 of the press drive unit 3.

[0022] Here, the return stroke adjuster 31, designed as a combined rapid advance and return stroke adjuster, is also responsible for achieving the initial, high-speed closing motion of the upper yoke 8 at this stage, until the pressing claw 6 of the pressing tool 5 abuts against the workpiece placed in the pressing tool 5. At this stage, the hydraulic cylinder-piston unit 10 of the press drive device 3 switches to supplementary suction operation, in which hydraulic fluid flows from two upper supplementary suction tanks 36 into the enlarged working chamber of the hydraulic cylinder-piston unit 10. These supplementary suction tanks 36 are respectively connected to the drive bracket 12 via valve block 35 flanges.

[0023] Two electrical displacement sensors 37 operate between the lower yoke 7 and the upper yoke 8, and the signals of the displacement sensors 37 are connected to the machine controller. Two additional displacement sensors 37 may be arranged mirror-symmetrically on the other end of the radial press.

[0024] For the radial press according to the second embodiment, see the accompanying drawings. Figure 8 The upper region is shown in a partially sectional front view, which, except for the following differences relative to the first embodiment, is directly described from the front. Figures 1 to 7 The description of the first embodiment shown in the figure illustrates this radial press.

[0025] Here, the press drive unit 3' includes three hydraulic cylinder-piston units 10', each having a cylinder body 11' and a piston 39'. These cylinder-piston units 10' constitute independent components, i.e., physically independent of the drive bracket 12'. These components are respectively fitted into receiving portions 38' integrated on the drive bracket 12', i.e., partially accommodated within the free space 41 formed by the respective receiving portions 38'. The load-transmitting end support of the cylinder body 11' on the drive bracket 12' is achieved in a torque-free manner, i.e., through mutually abutting sliding surfaces having a ball-and-socket geometry.

[0026] In this embodiment, the two return stroke adjusters 31' are diagonally offset outward from the center of the radial press; that is, the return stroke adjuster located on the side away from the observer (which is located on...) Figure 8 The piston rod 40 is shown to be offset to the left into a plane between the left-side cylinder-piston unit 10'a and the middle cylinder-piston unit 10'b, while the piston rod 40'a is positioned on the side facing the observer. Figure 8 The invisible return stroke adjuster is shifted to the right into a plane located between the middle cylinder-piston unit 10'b and the right cylinder-piston unit 10'c.

[0027] It should be pointed out that, in Figures 1 to 7 The details shown, such as in particular valve block 35 and replenishment tank 36, are in Figure 8 For simplicity, and for better overview and display, it is not shown. Obviously, similar components can also be found in... Figure 8 It is implemented in a radial press.

[0028] according to Figure 8 In a modified variant of the implementation, it is possible that the three hydraulic cylinder-piston units 10'a, 10'b, and 10'c of the press drive may not be arranged in a single plane, but rather the middle cylinder-piston unit 10'b may be offset along the press axis relative to the plane defined by the left cylinder-piston unit 10'a and the right cylinder-piston unit 10'c. In this way, by applying targeted and controlled individual loading to the different hydraulic cylinder-piston units, the center of the resultant force applied by the press drive 3' to the movable yoke 2 can be moved along the press axis. During the pressing process, and thus without correcting the position of the workpiece in the pressing tool, this allows for the influence of the pressure state, particularly for compensating for possible asymmetries, such as those arising from asymmetrical workpiece geometry and / or eccentric positions of the workpiece in the pressing tool, and can be achieved by displacement sensors 37 (see [link to relevant documentation]) located on the radial front and back of the press. Figure 2 The asymmetry is detected by measuring the different results from each other. Of course, this modification can also be used in radial presses according to the invention having at least three hydraulic cylinder-piston units, such as in… Figures 1 to 7 As shown in the first embodiment, the cylinder body of the hydraulic cylinder-piston unit is an integrated component of the drive bracket.

Claims

1. A radial press with a yoke-type press structure, comprising a fixed yoke (1), a movable yoke (2), a press drive device (3, 3'), and an integral annular closed frame (9), wherein the press drive device (3, 3') realizes the closing movement of the movable yoke (2) relative to the fixed yoke (1), the frame (9) surrounds the above components, the fixed yoke (1) and the movable yoke (2) together define a tool mounting space (4), in which a pressing tool (5) is accommodated, the pressing tool (5) having a plurality of pressing claws (6) arranged around the press axis (X), characterized in that: – The press drive device (3, 3') includes at least two hydraulic cylinder-piston units (10, 10') oriented in parallel, the at least two hydraulic cylinder-piston units (10, 10') being spaced apart from each other transversely to the press axis (X); – A drive bracket (12, 12') is provided, and the frame (9) is attached to the arched support surface (16) of the drive bracket (12, 12') to surround the drive bracket (12, 12') at least 160°. – The drive bracket (12, 12') has a number of receptacles (38, 38') corresponding to the number of hydraulic cylinder-piston units (10, 10'), and the pistons (39, 39') of the hydraulic cylinder-piston units (10, 10') sink into the receptacles (38, 38').

2. The radial press according to claim 1, characterized in that, The drive bracket support surface (16) is a cylindrical section.

3. The radial press according to claim 1 or claim 2, characterized in that, The cylinder body (11) of the hydraulic cylinder-piston unit (10) is an integrated part of the drive bracket (12) in such a way that the receiving part (38) of the drive bracket (12) forms the cylinder body (11) of the hydraulic cylinder-piston unit (10).

4. The radial press according to claim 3, characterized in that, There is a transverse mobility between the piston (39) of the hydraulic cylinder-piston unit (10) and the movable yoke (2) of the hydraulic cylinder-piston unit (10).

5. The radial press according to claim 3 or claim 4, characterized in that, The cylinder body (11) of the hydraulic cylinder-piston unit (10) is lined with a separate cylinder liner inside.

6. The radial press according to any one of claims 3 to 5, characterized in that, The press drive device (3) includes exactly two hydraulic cylinder-piston units (10).

7. The radial press according to claim 1 or claim 2, characterized in that, The hydraulic cylinder-piston unit (10') is an independent component, and the cylinder body (11') of the hydraulic cylinder-piston unit is inserted into the receiving portion (38') of the drive bracket (12').

8. The radial press according to claim 7, characterized in that, The cylinder body (11') of the hydraulic cylinder-piston unit (10') is torque-free supported on the drive bracket (12').

9. The radial press according to any one of claims 1 to 8, characterized in that, The drive unit (3, 3') has a hydraulic booster.

10. The radial press according to claim 9, characterized in that, The hydraulic booster is structurally integrated into the drive bracket (12, 12').

11. The radial press according to any one of claims 1 to 10, characterized in that, The frame (9) is attached to the arched support surface (23) of the fixed yoke (1) and wraps around the fixed yoke by at least 160°.

12. The radial press according to claim 11, characterized in that, The yoke support surface (23) presents a cylindrical section.

13. The radial press according to any one of claims 1 to 12, characterized in that, The fixed yoke (1) forms the lower yoke (7), and the movable yoke (2) forms the upper yoke (8).

14. The radial press according to any one of claims 1 to 13, characterized in that, The frame (9) has two arc segments (21, 24) and two tension segments (27), the arc segments (21, 24) respectively describing 180° arcs, the two tension segments (27) connecting the two arc segments to each other, the two tension segments (27) being parallel to each other and parallel to the orientation of the hydraulic cylinder-piston unit.

15. The radial press according to claim 14, characterized in that, The extension dimension of the frame (9) parallel to the press axis (X) is smaller at least in a portion of the arc segment (21, 24) than in the tension segment (27).

16. The radial press according to claim 14 or claim 15, characterized in that, A guide structure for the movable yoke (2) is provided in the region of the tension section (27) of the frame.

17. The radial press according to claim 16, characterized in that, The guide element (29) fixed to the movable yoke (29) engages with the corresponding groove (28) of the tension section (27) of the frame (9).

18. The radial press according to any one of claims 1 to 17, characterized in that, At least one fast advance and return stroke adjuster (31) is provided between the two cylinders (11, 11') of the hydraulic cylinder-piston unit (10, 10'), and the at least one fast advance and return stroke adjuster (31) acts between the drive bracket (12, 12') and the movable yoke (2).

19. The radial press according to claim 18, characterized in that, At least two fast-forward and return stroke adjusters (31) in the form of hydraulic cylinder-piston units (32) are provided, the hydraulic cylinder-piston units (32) being spaced apart from each other in a parallel orientation along the direction of the press axis (X), and the cylinder body (33) of each hydraulic cylinder-piston unit (32) is provided on the drive bracket (12, 12').

20. The radial press according to claim 18 or claim 19, characterized in that, The at least one fast forward and return stroke adjuster (31) can be replaced without additional disassembly work.

21. The radial press according to any one of claims 1 to 20, characterized in that, At least two displacement measuring sensors (37), preferably four displacement measuring sensors (37), act between the fixed yoke (1) and the movable yoke (2).

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