WO1995033595A1

WO1995033595A1 - Finishing machine

Info

Publication number: WO1995033595A1
Application number: PCT/EP1994/003191
Authority: WO
Inventors: Otmar Fahrion
Original assignee: Otmar Fahrion
Priority date: 1994-06-03
Filing date: 1994-09-24
Publication date: 1995-12-14
Also published as: KR100355405B1; DE4419366A1; JPH10500631A; AU7698494A

Abstract

For finishing round surface sections of very heavy workpieces, for example the main pin and crank pin of crankshafts (12) for marine diesel engines, the invention proposes that the finishing belt and the pressure bodies (76) over which it passes be mounted on a rotary support ring (52) driven by a motor (74), while the workpiece remains stationary in the direction of rotation during the finish machining. The support ring (52) and a rotationally fixed head frame (44) of the finish machining head (34) are each split along a vertical contact plane running through the axis of the support ring, so that one half (42) of the machining head can be moved away from the other half (40) to allow the workpiece section for machining to be inserted into and removed again from the machining head.

Description

Finishing machine

The invention relates to a finishing machine for processing round surface sections of workpieces according to the preamble of claim 1.

In such known finishing machines, the workpieces are rotatably mounted on tailstocks. A machining means is guided over fixed pressure bodies, and by the workpiece surface running past the machining means, material is removed from its surface and smoothed.

Particularly in the case of heavy and large workpieces, such as crankshafts for ship diesel, the use of such finishing machines requires a high degree of attention and a relatively large amount of time, since the tailstocks must have a possibility of the bearing axis being movable in the horizontal and vertical directions, so that the axis of the respective axis can machining surface section, e.g. a crank pin on which the axis of the machining head, which is predetermined by the arrangement of the pressure element, is correctly aligned. In addition, heavy workpieces of this type can bend differently depending on the current angle of rotation, and since such workpieces can only be stored at a few geometrically equivalent locations (for example axially aligned crank or main journals) during machining, there are additional machining difficulties which can lead to inaccuracies in the machining.

The present invention is therefore intended to provide a finishing machine according to the preamble of claim 1. are formed so that they can also process surface sections on very heavy workpieces without the workpiece having to be rotated.

This object is achieved according to the invention by a finishing machine with the features specified in claim 1.

In the finishing machine according to the invention, the pressure bodies and the processing means are arranged on a support ring, which in turn is rotatably mounted in a holding part of the processing head. It is thus possible to rotate these parts, which have a small mass compared to the workpiece, for machining, while the workpiece itself remains spatially fixed.

In the finishing machine according to the invention, there is also freedom to adjust the relative speed between the machining means and the workpiece surface, since no large masses are moved. For this reason, the adjustment of the machining head to the desired target axis of the round surface section to be machined is easier than the adjustment of the workpiece to the axis of the machining head. Finally, a bearing device for the workpiece, which is considerably simplified compared to the prior art, is also sufficient for the finishing machine according to the invention. You can e.g. simply use tailstocks and the machine bed of a large lathe.

Advantageous developments of the invention are specified in the subclaims.

The development of the invention according to claim 2 enables the machining head to be easily completely moved away from a round surface to be machined. Section to another round surface section of the workpiece to be machined, since the support ring is segmented and easy to open.

In the case of a finishing machine according to claim 3, the support ring need only have two segments, which is advantageous in terms of simple manufacture and simple handling.

In the case of a finishing machine according to claim 4, the machining head can simply be moved away from the workpiece in a horizontal direction after the support ring has been opened, when the processing of a surface section has ended, and can be moved towards the side in order to process the next surface section. You do not need to move the processing head or only slightly in the vertical direction.

With the development of the invention according to claim 5 it is ensured that the two head frame segments and the support ring segments carried by them can be closed again without expensive adjustment work.

With the development of the invention according to claim 6, a quick and reliable locking of the two head frame segments is ensured.

In a finishing machine according to claim 7, that support ring segment which is carried by the movable head frame segment is automatically captively connected to the movable head frame segment after opening this head frame segment.

The development of the invention according to claim 8 also allows the machining head to be simply moved away from a surface section to be machined and a subsequent approach to a next round surface section of the workpiece to be machined. In the case of the finishing machine according to claim 8, no parts of the machining head are to be adjusted or released.

With such a finishing machine, a continuous drive in the circumferential direction of the support ring interrupted at one point can be ensured in a particularly simple manner.

The development of the invention according to claim 10 allows a plurality of machining operations to be carried out without changing the machining means between them.

The development of the invention according to claim 11 ensures that sections of the processing means are each guided tightly over the pressure element.

In a finishing machine according to claim 12, the processing means can be exchanged easily and quickly.

It is particularly advantageous here if the pressure bodies themselves are also attached to the interchangeable frame, since it is then also possible to thread the processing means in advance before changing the processing means cassette. You can also provide different print bodies together with different processing tapes as ready-prepared replacement cassettes.

The development of the invention according to claim 14 makes it possible to apply differently strong contact pressure to the surface section of the workpiece to be machined at successive locations in the circumferential direction. to remove different amounts of material. In this way, systematic out-of-roundness of a specific workpiece type can be eliminated in a particularly short time.

The development of the invention according to claim 15 is advantageous with regard to a flexible and rapid adaptation of the contour of the cam surface working on the pressure body.

The further development of the invention allows

Claim 16 combining cam ring segments of different contours without formation of steps at the joint.

In a finishing machine according to claim 17, the portions of the cam surface can be easily shifted in the circumferential direction.

The development of the invention according to claim 18 is advantageous with regard to the adjustment of the axis of the machining head to the axis of the surface section of the workpiece to be machined.

The development of the invention according to claim 19 enables simple adjustment of the machining head from a round surface section to be machined to an axially spaced further surface section to be machined.

Furthermore, the movability of the head frame and thus the machining head also allows the machining head to be moved back and forth with a small stroke, as stated in claim 20. In this way, a cross-section microstructure of the workpiece surface is obtained, which is desirable in view of the good running properties of a bearing surface is. In addition, a higher material removal is achieved by such an additional axial reciprocating movement of the machining means.

The development of the invention according to claim 21 enables rapid machining of workpieces which have a larger number of surface sections to be machined.

In the case of a finishing machine according to claim 22, it is also possible to simultaneously process those axially successive surface sections of a workpiece which are not axially aligned.

A finishing machine, as specified in claim 23, also allows the actual contour of the surface section currently being machined to be measured continuously.

In a finishing machine according to claim 24, starting from the output signals of these position sensors, it is continuously calculated how an ideal cylindrical shape of the workpiece surface section being processed can be obtained most quickly and with the lowest machining performance. In accordance with the respective out-of-roundness of the workpiece surface section, the desired axis is shifted accordingly by shifting the support ring axis.

In the case of a finishing machine according to claim 25, no cable or hose connections are necessary between the peripheral parts of the processing head and the fixed parts thereof.

The development of the invention according to claim 26 results in terms of favorable running properties Grinding pattern and advantageous in terms of high material removal.

With the development of the invention according to claim 27 it is achieved that the curved end face of the

Can adjust the pressure body to the workpiece surface to be machined even with slight misalignment of the pressure body movement axis.

The development of the invention according to claim 28 is also advantageous in terms of adapting the pressure body end face to the workpiece surface. The extent of the adaptation can be varied via the bending stiffness of the spring plate forming the pressure body end face.

In the case of a finishing machine, as specified in claim 29, the deflection rollers located between the pressure body simultaneously ensure that the processing means are entrained axially, which is particularly advantageous in terms of impressing the processing means with a predetermined axial back and forth movement.

With the development of the invention according to claim 30 it is achieved that the pressure bodies can adjust to larger eccentricities, so that one can easily obtain a circular shape taking these eccentricities into account with minimal material removal, if desired.

It can be switched off with the development of the invention according to claim 31, this automatic self-adjustment of the partial circle predetermined by the pressure element by locking the hydraulic cylinders in a predetermined position. With the development of the invention according to claim 32, a spring effect for receiving symmetrical positional deviations of the actual surface is obtained in a simple manner, which would otherwise lead to hard impacts on the pressure body end faces.

The development of the invention according to claim 33 also serves to cushion the pressure body end faces. The invention is explained in more detail below on the basis of exemplary embodiments with reference to the drawing. In this show:

Figure 1: an axial plan view of a finishing machine for machining crankshafts;

FIG. 2: a side view of a processing head of the finishing machine shown in FIG. 2;

FIG. 3: an axial plan view of a part of the machining head shown in FIGS. 1 and 2 on an enlarged scale;

Figure 4: a radial section along the section line IV-IV of Figure 3, in which details

Storage and cam actuation of pressure bodies of the machining head are reproduced;

Figure 5 is an enlarged vertical section through the joint between a movable part of the machining head and a fixed part of the machining head on an enlarged scale, with parts broken away;

Figure 6: a section through a locking unit for connecting the movable part of the machining head with its fixed part;

FIG. 7: an axial top view of a modified finish processing head with rewindable processing tape;

Figure 8: an axial section through a finish unit of the machining head shown in Figure 7 together with an electronic-mechanical

Readjustment unit for the target axis of the workpiece surface section to be machined;

FIG. 9: a section through a modified pressure body;

FIG. 10: a section through a pressure body modified again;

FIG. 11: a view of a deflection roller for guiding a processing belt of the finishing machine; and

Figure 12: a view similar to Figure 7, in which a modified finish machining head is shown with coupled floating pressure bodies. 1 and 2, 10 denotes a machine bed which, for example, Can be part of a large lathe, such as that used for machining ship crank parts.

Such a crankshaft, which can typically have a length of up to 10 m (blank up to 10.6 m) and can have a finished length of up to about 20 t (blank 45 t), is designated by a total of 12 in the drawing. She has on the Main pin 14 lying on the shaft axis, on which the shaft is later mounted in the motor housing, as well as crank pins 18 connected to the crank cheeks 16. The crank shaft 12 is on the machine bed 10 above and behind the plane of the drawing, not shown tailstocks stored. In order to prevent deflections of the heavy crankshaft and to facilitate its adjustment, a total of 20 bearing units are provided, which are laterally movable in the horizontal direction on carriages 22 which are perpendicular to the plane of the drawing, ie parallel to the shaft axis on wheels 24 and rails 26 are movable. The bearing units 20 each have three rollers 28 which are offset in the angular direction and can act on the surface of a main pin 14. The outer rollers 28 are arranged on pivotable arms 30 so that a bearing unit 20 can be used for different pin diameters.

On a further slide 32, which can also be moved perpendicular to the plane of the drawing in FIG. 1, there is a machining head, designated 34 as a whole, for finishing both the main pin 14 and the crank pin 18.

The processing head 34 is arranged on the carriage 32 in the drawing plane of FIG. 1 so as to be movable in the horizontal direction. For adjustment, a threaded spindle 36 is provided, on which an electric motor 38 works. This and other electric motors used in the finishing machine under consideration can be a speed-controllable AC motor or a stepper motor which ensures rapid and precise adjustment of the part moved by it. Although not shown in the drawing, it goes without saying that each such drive motor is assigned a position transmitter, either in the form of a resolver coupled to the motor shaft or in the form of a linear position transmitter cooperating with the moving part.

The machining head 34 has a first machining head part 40 which cooperates with the slide 32 and which (apart from the adjustment possibilities mentioned above is parallel to the shaft axis and perpendicular to the shaft axis) and is therefore shortened in the present description and the claims as fixed machining head part is addressed. A second, pivotable machining head part, generally designated 42, is carried by the fixed machining head part 40. This is shown in FIG. 1 with solid lines in the open state, by dash-dotted lines in the closed state adjacent to the first machining head part.

Where below and in the drawing, comparable components of the two machining head parts 40 and 42 are highlighted, they are identified by the same basic reference signs, to which an "A" or "B" is appended for differentiation, wherever such Differentiation is important. If these reference numerals are used without such an addition, they should apply equally to the components of both processing heads 40 and 42.

The machining head parts each have a frame part 44, which consists of two spaced frame plates 46, 48, which are firmly connected by bolts 50. The

Frame plates each hold a support ring segment 52 which extends over 180 ° and which (see FIGS. 3 and 4) is provided with a radially outer guide ring 54. As FIG. 4 shows in more detail, upper and lower race ring segments 56, 58 are fixedly inserted into the end faces of the support ring segments 52, which are supported by a rotating ball arrangement 60 of fixed upper and lower guide shoes 62, 64, each of which two the race ring segments 56, 58 of have cheeks 66, 68 spanning inside and outside. Due to the arrangement of the balls and shoulders shown on the races, both a radial bearing and an axial bearing of the support ring segment 52 are obtained.

A drive gear 70 (see FIGS. 1 and 3) meshes with the ring gear 54 of the support ring segments 52 and is driven by an electric motor 74 via a chain 72.

The support ring segments 52 each carry pressure bodies 76 which protrude radially inward beyond the inner surface of the support ring segment and which are only shown schematically in FIG. 1 and more precisely in FIGS. 3 and 4.

The pressure bodies 76 each have a head 78, which is made of Vulkolan or a comparable dimensionally stable, but slightly elastic material. The end face 80 of the head 78 is selected in accordance with the desired nominal diameter of the spigot to be machined.

The head 78 is seated on a head support 82, which in turn is mounted on a hollow rod 84. This passes through a radial bore 86 in a cassette frame 88. The bore 86 is provided at the radially outer end with a counterbore 90 in which an arm part 92 carried by the rod 84 runs. The arm part 92 carries a cam follower roller 94, which closes with cam ring segments 96 extending over an angle of 45 °. work together. The latter are connected by screws 98 to an adjusting ring 100, which in turn is connected by screws 102 (see FIG. 4) to the upper fixed race 62, which in turn is connected by screws 104 to the frame plate 46.

As FIG. 3 shows, the setting ring 100 is provided with an angle scale 106.

As can be seen from FIGS. 1 and 4, the rods 84 are guided through slide bearing bushes 108 inserted into the bore 86, and the radially outer end faces of the head carriers 82 are supported on the cassette frame 88 via a plate spring assembly 110. The entire arrangement of the pressure body support, rod 84 and arm part 92 is held together by a bolt 112 which is passed through these parts.

In the exemplary embodiment shown in FIGS. 1 to 3, two pressure elements 76 are provided on a cassette frame 88 offset from one another by an angle of 90 °. A processing belt 114 is guided over the two pressure bodies 76 and consists of a flexible base and fine abrasive particles attached to it. The processing belt 114 is drawn off from a supply roll 116, which is fastened via a holder 118 at the end of the cassette frame 88 which is at the top in FIG. 3, and is wound onto a take-up roll 120 which is at the bottom in FIG. 3 via a further holder 122 - Lying end of the cassette frame 88 is attached.

The position of the two brackets 118 and 122 is selected so that the processing belt 114 runs at an angle of approximately 20 to 30 ° to the end face 80 of the head 78 and inclines on the latter and at approximately the same angle from in Direction of rotation seen rear pressure body 76 expires.

In order to create comparable discharge geometry or overrun geometry for the front or rear pressure element, between the two pressure elements there is a roller unit, generally designated 124, which has three deflection rollers 126, 128 and 130, each behind the through the end faces 80 of the two pressure elements 76 predetermined circle 132 lie.

The cassette frame 88, together with the components carried by it, can be removed as a unit of support bolts 134 of the support ring segment 52 under consideration after loosening screws (not shown). In this way, the processing belt 114 can be easily replaced after it has been completely used up. Complete units with different pressure bodies / processing belt combinations can also be kept ready ready for rapid replacement in a warehouse.

A locking device 136, shown in more detail in FIG. 5, is provided so that the support ring segment 52B contained in the pivotable head part 42B remains securely held in this when the machining head part is pivoted away. This includes a locking lever 138, which is designed as an angle lever and is accommodated in a pocket 140 of the machining head part 42. It is pivotally supported at the end of one arm via a pin 142, and the outside of the end of its other arm is provided with a nose 144 which can engage between two teeth of the ring gear 54. A spring 146 engages on the rear side of the locking lever 138, by means of which the locking lever 138 is pretensioned into a position engaging in the toothed crane 54. As Figure 5 shows, the location of the pin 142 and the

The width of the locking lever 138 is selected such that the vertical arm of the locking lever 138 on the left in FIG. 5 can protrude with its left edge beyond the boundary surface of the head part 42. This position of the locking lever 138, which is assumed under the force of the spring 146, is indicated by dash-dotted lines in FIG. 5.

If the machining head part 42 is moved against the machining head part 40, the arm of the locking lever 38, which is vertical in FIG. 5, is gripped by the end face of the latter, so that the locking lever 138 pivots clockwise against the force of the spring 146 and his nose 144 comes free from the ring gear 54.

Under these conditions, the two support ring segments 52 can run freely in the bearing formed by the frame plates 46, 48 and the components 56 to 68 carried by them, whereby they are axially and radially supported.

To securely connect the two machining head parts 40, 42 in this closed working position, a locking unit designated overall by 148 is provided, which is shown only schematically in FIG. 1 and offset by 90 ° with respect to the head axis and in FIG. 6 by 90 ° with respect to it the plane of the processing head is shown tilted.

The locking unit 148 includes a locking pin 150 which is carried by the machining head part 42 and is provided at its free end with a frustoconical end section 152. The locking pin 150 runs in one Locking sleeve 154, which is fixedly connected to the machining head part 40.

In the section on the left in FIG. 6, the locking pin 150 is provided with a conical latch bore 156, into which a conical end section 158 of a latch pin 160 can be inserted. The latter is guided so as to be displaceable perpendicular to the axis of the locking sleeve 154 in a sleeve 162 which is supported by a locking housing designated overall by 164. The latter receives a compressed air-actuated double-acting working cylinder 166, the piston rod 168 of which is connected to the latch pin 160.

It can be seen that when the latch pin 160 is moved downward in FIG. 6, the latch pin 150 can be moved into and out of the latch sleeve 154, while the latch pin 150, which is essentially retracted into the latch sleeve 154, by means of cooperating conical surfaces of the latch bore 156 and the end section 158 in the closed position is pulled when the piston rod 168 is extended.

Alternatively, the pivotable head part 42 can be held by spring force on the fixed head part 40, in which case a compressed air cylinder or another servo motor is provided in order to fold the head part 42 away from the fixed head part 40 against the spring force acting in the closing direction.

In the modified machining head shown in FIG. 7, components which functionally correspond to components already described with reference to the preceding figures are again provided with the same reference numerals, even if they differ from them in details of their geometry. In this machining head, only a single support ring segment 52 is provided, which extends over an angle of approximately 300 °. On the two end faces of the support ring segment 52, two axially projecting guide ribs 170 are provided, which slide in grooves 172 which are provided on the inner sides of the frame plates 46, 48. The frame plates 46, 48 now have a shaft receiving opening 174, which is open in the drawing to the right to the edge of the frame plates 46, 48.

To drive the support ring segment 52 via its ring gear 54, four drive gear wheels 70 are now provided, which have an angular distance of 90 ° and are each rigidly connected to a chain wheel 176. The drive chain 72 runs over the various sprockets 176, the return run of which runs within the edges of the shaft receiving opening 174, for which purpose two free-running sprockets 178 are provided, as can be seen from the drawing. The drive chain 72 is guided via further free-running chain wheels 180 via a chain wheel 182 carried by the shaft of the electric motor 74.

Two processing units, designated overall by 184, each having a pressure body 76 with an associated head 78 and a processing belt 114 and a supply roll 116 and a take-up roll 120, are mounted on the support ring segment 52 at an angular distance of approximately 140 °, so that a journal to be machined of the crankshaft 12 can simply be moved from the right in FIG. 7 against the end faces 80 of the pressure element 76.

The internal structure of the pressure body units 184, as it results from the section shown in FIG. 8, is Similar to that shown in FIG. 3, except that the pressure bodies 76 rest exclusively on the workpiece surface under the force of the associated disk spring pact 110.

The arm part 92, which also serves as a spring seat, works together with the input part of a position transmitter 186. Its output signal is routed via a cable-free data transmission path, which comprises a first modem part 188 integrated in the pressure body unit 184 and a frame-fixed modem part 190. The latter is connected to one of the inputs of a multiplexer 192, the second input of which is connected to the modem part 190 belonging to the second pressure body unit, wherein in modified exemplary embodiments additional inputs of the multiplexer 192 can be provided for further pressure body units. In a modification of this, however, only one of the pressure body units 184 can be equipped with a position transmitter, in which case the multiplexer 192 can then be omitted.

The output of the multiplexer 192 is connected to a signal shaping circuit 194 which, in the event that the position transmitter 186 and the modem part 188 have not already digitized the position signal, also accomplishes an analog / digital conversion. With the output signal of the waveform circuit 194, a digital characteristic circuit 196 is driven, which serves to compensate for non-linearities of the measuring system formed by the pressure element 76, the rod 84, the plate spring assembly 110 and the position transmitter 186.

The multiplexer 192, the signal form circuit 194 and the characteristic curve circuit 196 are activated by the output signal of a free-running clock generator 198, the operating frequency of which is large compared to the rotational frequency. frequency of the support ring segment 52 (typically about 20 U / min to 160 U / min).

A read / write memory 200 is connected to the output of the characteristic curve circuit 196, the address signal of which is obtained by combining the output signal of the clock 198 and the output signal of an A / D converter, the input of which receives the output signal of a resolver 204 which, for example, corresponds to the output shaft of the Electric motor 38 is coupled, as indicated in Figure 7.

The digitized output signals of the various position transmitters 186 are thus stored in the read / write memory as a function of the angular position of the support ring segment 52. This stored data can be called up as whole blocks from a freely programmable computer 206, which uses this data to calculate the center point and radius of a circle, which can be achieved most quickly on the basis of the actual state, taking into account the given requirements for out-of-roundness and surface roughness. If you ask e.g. 100% roundness, the circle calculated by the computer 206 is the one which has the largest diameter and lies completely within the current actual contour. If smaller out-of-roundnesses are permissible, the target contour circle calculated by the computer 206 with sections can also protrude slightly beyond the actual contour.

Depending on the calculated position of the center point of the target contour circle, the computer 206 controls via power units 208, 210 servomotors 212, 214, by means of which the machining head can be moved overall in the horizontal direction or vertical direction.

In both of the above-described embodiments a pendulum drive acting perpendicular to the drawing plane of FIG. 1 or FIG. 7 (shown schematically at 216 in FIG. 1) is provided in order to move the processing head 34 perpendicular to the drawing plane by a small distance of 0.5 to 5 mm, so that the machined Surfaces are given a cross-section.

In a further modification, several machining heads 34 can be provided on the carriage 32 on the machine bed 10 in order to be able to machine different main and / or crank pins at the same time. If one additionally provides that the machining heads on the carriage 32 can be adjusted in the vertical direction, such a finishing machine can simultaneously machine pins which are not axially aligned.

In the modified pressure element 76 according to FIG. 9, a ball socket 218 is provided in the rear side opposite the end face 80, in which a joint ball 220 is held, which is provided at the front end of a pressure element holding rod 222. In this way, the end face of the pressure body can be angularly adapted to the workpiece surface.

In the pressure body 76 shown in FIG. 10, a spring plate 226 is placed on a cup-shaped pressure body main part 224 that is open toward the workpiece, and in the unloaded state has a slightly larger radius of curvature than the radius of the surface to be machined would choose for an end face carried by a rigid pressure body. In this way, the pressure element 76 can adapt to the workpiece surface with slight elastic deformation, with slits that may be open in the walls of the pressure element main part 224 toward the end face of the pressure element main part 224 228 can be provided to facilitate the elastic deformation of the spring plate 226.

As FIG. 11 shows, the deflection rollers 126 to 130 of the roller unit 124 each have lateral collars 230, 232, the spacing of which is selected such that the processing belt 114 is guided on the deflection rollers 126 to 130 with a small transverse play. If the entire machining head 34 is embossed with an axial back and forth movement in addition to the circulating movement in order to improve the material removal and to achieve a cross-grind structure on the workpiece surface, the deflection rollers 126 to 130 ensure a clean axial entrainment of the machining belt.

In the exemplary embodiment according to FIG. 12, the head carriers 82 are each supported via a plate spring 234 on the driven part of a single-acting hydraulic cylinder 236, which in turn is supported on the box frame 88 and thus on the support ring segment 52. The hydraulic cylinders 236 are each connected via a switching valve 238 to a compensating line 240, to which a pressurized compensating tank is additionally connected, as is also used as a hydraulic pressure accumulator.

If the switching valves 238 are all open, the hydraulic cylinders 236 can adjust themselves freely, which means that the pressure elements 76 adjust to the actual pitch circle of the workpiece surface to be machined.

Such a setting can then be frozen by closing the switching valves 238. The end faces of the pressure bodies 76 are then still cushioned by the plate spring 234. For special tasks, the switching valves 238 can also be left open or partially opened during processing, so that throttling the hydraulic oil obstructs the self-alignment of the pressure body end faces on the pitch circle which can be obtained with the least machining.

Claims

1. Finishing machine for processing round surface sections of workpieces, with a device for storing the workpiece and with at least one machining head (34), which has: a fixed head frame (44), at least one pressure body (76), at least a processing means (114) guided via a pressure body (76) and a drive device which generates a relative movement between the workpiece surface and the processing means, characterized in that the pressure bodies (76) are arranged on a support ring (52) , which is rotatably supported by the head frame (40) and is rotated or moved back and forth by a drive motor (74).

2. Finishing machine according to claim 1, characterized in that the support ring (52) consists of at least two Tragring¬ segments (52A, 52B) and the head frame (44) two in a predetermined angular position of the support ring (42) each one of the support ring segments (52A , 52B) receiving head frame parts (44A, 44B).

3. Finishing machine according to claim 2, characterized in that the support ring segments (52A, 52B) each have one

Have an angle of 180 °.

4. finishing machine according to claim 2 or 3, characterized gekenn¬ characterized in that the abutting plane between the two Trag¬ ring segments (52A, 52B) and the head frame parts (44A, 44B) extends vertically.

5. Finishing machine according to one of claims 2 to 4, characterized in that the head frame parts (44A, 44B) are connected via a joint.

6. Finishing machine according to one of claims 2 to 5, character- ized by a servo lock (148) for the two head frame parts (44A, 44B).

7. Finishing machine according to one of claims 2 to 6, characterized by a supporting ring segment locking device (136) which is provided on the movable head frame part (44B) and is activated when this head frame part (44B) is moved away from the fixed head frame part (44A) .

8. finishing machine according to claim 1, characterized in that the support ring (52) has an angular extent of less than 360 °, but preferably more than 180 ° and in at least one circular groove (172) of the frame part (44) and that Head frame (44) has a receiving opening (174) open to one of its edges for the workpiece (12) to be machined.

9. finishing machine according to claim 8, wherein the support ring (52) is provided with a ring gear (54), characterized in that along the path of the support ring (52) a plurality of in the ring gear (54) engaging drive gears (70) is provided , whose angular distance is smaller than the angular extent of the support ring (52).

10. Finishing machine according to one of claims 1 to 9, da¬ characterized in that the support ring (52) carries at least one supply roll (116) and a take-up roll (120) for band-shaped processing means (114), which seen in the direction of rotation in front or behind a pressure body (76) or a group of pressure elements (76) are arranged.

11. Finishing machine according to claim 10, characterized in that between adjacent pressure bodies (76) of a pressure body group, over which a common band-shaped processing means (114) is guided, each one the processing means (114) radially outwards over the path of the pressure body end faces ( 80) steering deflection roller arrangement (124) is provided.

12. Finishing machine according to one of claims 9 to 11, characterized in that in each case a supply roll

(116) and the associated take-up reel (120) and the deflection roller arrangement (124) lying between them are arranged on a common cassette frame (88).

13. finishing machine according to claim 12, characterized gekennzeich¬ net that the pressure body (76) from the cassette frame

(88) are worn.

14. Finishing machine according to one of claims l to 13, characterized in that the pressure body (76) is radially displaceable (84, 86) on the support ring (52) and are provided with a cam follower part (94) which is on an axis of the Support ring (52) runs essentially coaxial cam surface of a cam ring (96).

15. finishing machine according to claim 14, characterized gekennzeich¬ net that the cam ring (56) is made up of interchangeable cam ring segments, preferably the pitch of the cam ring segments equal to the pitch of the support ring segments (52) or an integral multiple thereof.

16. Finishing machine according to claim 15, characterized in net that in the case of cam ring segments (96) with different cam surfaces, the start section and end section of the cam surface run exactly in the circumferential direction and have the same distance from the axis of the support ring (52).

17. Finishing machine according to one of claims 14 to 16, characterized in that the cam ring (96) can be fixed in different angular positions on the fixed head frame (44).

18. Finishing machine according to one of claims 1 to 17, characterized in that the fixed head frame (44) can be moved in the horizontal direction in the supporting ring plane (36, 38).

19. Finishing machine according to one of claims 1 to 18, characterized in that the fixed head frame (44) can be moved in a horizontal direction parallel to the support ring axis.

20. Finishing machine according to claim 19, characterized by a drive (216) for axially moving the head frame (44) which is fixed in the direction of rotation with a small stroke of preferably 0.5 to 5 mm.

21. Finishing machine according to one of claims 1 to 20, characterized in that it has a plurality of processing heads (34) which process axially spaced surface sections of the workpiece (12).

22. Finishing machine according to claim 21, characterized gekennzeich¬ net that the fixed in the direction of rotation head frame (44) of the various machining heads (34) are each adjustable in the support ring plane in the vertical direction.

23. Finishing machine according to one of claims 1 to 22, characterized in that in one of pressure bodies

(76) and processing belt (114) free area of the support ring (52) at least one position transmitter is provided, which cooperates with the surface portion of the workpiece (12) being machined, or at least one movable in the radial direction against spring force (110) (84, 86) pressure body (76) is assigned a position transmitter (186).

24. Finishing machine according to claim 23, characterized by a read / write memory (200) which stores the output signals of the position transmitter (186) for a full rotation of the support ring (52), and by a computer (206) which is operated by the various Measuring points a compensation circle, for example according to the method of the smallest square error, and an error signal assigned to the offset between the center of the equalizing circle and the support ring axis, and by a feed circuit (208, 210) for servo drives (212, 214) which are directed to the head frame which is fixed in the direction of rotation (44) work, the entire arrangement being such that the head frame (44) is adjusted so that the center point of the compensating circle is placed on the support ring axis.

25. finishing machine according to claim 23 or 24, characterized ge indicates that the outputs of the position transmitter (186) via wireless modems (188, 190) with the read / write memory (200) are connected.

26. Finishing machine according to one of claims 1 to 25, characterized in that the drive motor (74) is controlled for an oscillating movement, the angular amplitude is smaller than half the angular distance between adjacent pressure bodies.

27. Finishing machine according to one of claims 1 to 26, characterized in that the pressure bodies (76) are each connected via a hinge connection (218, 220) to a pressure body holding means (222).

28. Finishing machine according to one of claims 1 to 27, characterized in that at least one of the pressure bodies (76) has a hollow main pressure body part (224) which on the workpiece side carries an essentially circular arc-shaped spring plate (226), its radius of curvature preferably is chosen somewhat larger than the radius of the workpiece surface to be machined, and preferably the main pressure part (224) is also slightly resilient.

29. Finishing machine according to one of claims 11 to 28, characterized in that at least one of the Umlenk¬ rollers of the deflection roller assembly (124) is provided with side collars (230, 232) through which the edges of the processing belt (114) positio in the axial direction ¬ are niert.

30. Finishing machine according to one of claims l to 29, characterized in that the pressure bodies (76) are each supported by a hydraulic cylinder (236) on the support ring (52) and these hydraulic cylinders (236) are connected in parallel in terms of flow (240) are.

31. Finishing machine according to claim 30, characterized by means (switching valves 238) for optionally locking the hydraulic cylinders (236).

32. finishing machine according to claim 30 or 31, characterized ge indicates that a hydraulic line (236) connecting compensation line (240) is connected to a pressurized expansion tank (242).

33. Finishing machine according to one of claims 30 to 32, characterized in that in each case at least one spring (234) is inserted into the force transmission path leading from the support ring (52) to the end faces of the pressure elements (76) via the hydraulic cylinder (236) is.