Patent Application
20250018478
Clamping systems with a hollow shaft and a complementary shaped centering mount, for example according to ISO 12164 or ISO 26623, have proven themselves on the market for many years.
Among other things, they are used in driven or fixed tool holders. Then, the centering mount and the clamping system are integrated in the spindle of the driven tool holder or in the housing of the tool holder. In the following, the term “spindle” is used for rotating and non-rotating receptacles of the clamping system and centering receptacle. The hollow shaft is part of an adapter that for example carries a drill, a milling cutter, a turning tool or another tool.
To be able to transmit the required torque between the spindle and the adapter and to achieve a defined position of the tool with repeated accuracy, centering receptacles have been used for decades with a truncated cone which has a polygonal cross-section (hereinafter also referred to as an inner polygon). The hollow shaft of the adapter has a complementary outer contour (hereinafter also referred to as an outer polygon).
The known clamping systems for clamping such a polygonal hollow shaft comprise a collet consisting of multiple clamping segments. The clamping segments are arranged around a tension bolt. An axial movement of the tension bolt relative to the clamping segments presses them radially outward into a groove of the hollow shaft. This initially results in a positive-locking fit with the hollow shaft at the front ends of the clamping segments. A further movement of the tension bolt creates an axial clamping force, which the clamping segments exert on the hollow shaft of the adapter, such that the adapter is pulled into the centering mount. An example of such a clamping system is known from EP 2 164 662.
Similar clamping systems are known from EP 1 924 379 B1 and DE 196 18 610 A1.
The forces required for clamping and releasing are provided for example by a cylinder structure in automatic systems. This cylinder structure, which is actuated fluidically (e.g., pneumatically or hydraulically), must also be integrated into the spindle. It is obvious that the installation space available for the clamping system and the cylinder structure in a, for example, driven spindle is very limited both in the radial and in the axial direction. Even in the case of standing tool holders, the available space for the clamping system is becoming increasingly smaller due to increasingly smaller installation spaces. The available installation space must therefore be optimally utilized here as well.
The mounting of the clamping system and the optional cylinder structure into the spindle must in most cases be accomplished by the centering receptacle (the inner polygon) in order to achieve a very compact radial design.
The invention is based on the object of providing a clamping system which makes it possible to best exploit the installation space available in a rotatably mounted or a fixed spindle. In addition, the mounting of the clamping system and cylinder structure should be easy and time-saving. In the event of an overhaul or repair, the clamping system and the cylinder structure should be easily removable.
According to the invention, this object is achieved by a rotatably mounted or fixed spindle, wherein the spindle has a recess which comprises a centering receptacle, an annular groove, and a receiving bore for a clamping system, and an optional cylinder structure for actuating the clamping system, wherein the centering receptacle, which is designed as a polygonal inner cone and accommodates an adapter with a polygonal outer contour and hollow shaft, wherein the centering system comprises a collar, wherein the clamping system comprises a collar, wherein the collar has a polygonal outer contour, or the outer contour is formed by a plurality of lugs distributed over the circumference, wherein the collar fits through the centering receptacle in at least one rotational position, and a positive-locking fit is established in at least one axial direction between the collar and the annular groove by rotating the collar relative to the spindle into at least one locking position.
As a result of this type of locking mechanism of the housing or the collar in the annular groove in the manner of a bayonet closure, the diameter of the receiving bore and consequently also the diameter of the installable housing or of the clamping system can be maximized. It can be the same size or only slightly smaller than the inscribed circle of the smallest inner polygon of the centering receptacle.
For the actual axial securing of the collar in the spindle, the space directly behind the centering receptacle is formed as an annular groove. There, the centering receptacle has its smallest diameter at the transition between the centering receptacle and the receiving bore. The installation space requirement for the locking mechanism according to the invention is therefore minimal.
It is particularly advantageous that the outer diameter of the clamping system and a cylinder structure possibly arranged behind the clamping system can be maximized. This gives the designer of the clamping system and cylinder structure degrees of freedom in the design, and furthermore also increases the actuating forces that the cylinder structure can provide in order to clamp or release the clamping system, since a cylinder structure with a larger piston diameter can be installed.
A further advantage is that the number of components is reduced. The collar and the annular groove can be controlled well in production. Furthermore, due to this small number of components and their structure, the axial transmission of force by the clamping system to the spindle is extremely rigid.
Because the axial securing of the clamping system can also take place in both directions at one location, namely the collar or the annular groove, very narrow tolerances can be selected here so that a very precise axial positioning of the clamping system and the cylinder structure can be realized without increased manufacturing effort.
In an advantageous development of the invention, a diameter of the annular groove is equal to or somewhat larger than a circumference of the outer contour of the collar.
In order to secure the positive-locking fit according to the invention against unintentional release, a recess is formed in the collar. A securing pin which dips into the recess is inserted into a bore (with or without a thread) in the spindle. In this way, a positive-locking fit and releasable anti-rotation lock of the collar and therefore also of the clamping system relative to the spindle is created.
The securing pin can be designed, for example, as a threaded pin. Other one or two-part designs can be realized at any time, as long as the basic function of the positive-locking fit and releasable anti-rotation lock is maintained.
In a preferred development, the recess is arranged at a high point of the polygonal collar or a lug of the collar.
Furthermore, it is advantageous if a width of the annular groove is equal to or slightly greater than a width of the collar. The difference between the width of the annular groove and the width of the collar results in the axial play with which the clamping system is positioned in the spindle. A very low axial play of less than 0.1 mm can easily be realized. An axial play of 0.05 mm can also be realized. If the annular groove is 0.02 mm to 0.05 mm wider than the collar, then this is considered “equivalent.” The play prevents a clamping of the collar in the annular groove and facilitates assembly.
The receiving bore in the spindle can be designed as a polygon at least sectionally. Even more installation space in the interior of the spindle is then available for the clamping system and an optional cylinder structure. The piston or pistons of the cylinder structure can also be designed as a polygon.
If the receiving bore in the spindle is designed at least sectionally as a polygon, then the collar is or the collar and the housing are rotatable relative to the rest of the clamping system (4) or the cylinder structure (6). The collar then functions like a locking ring and forms an axial stop in the clamping direction. The piston and the rest of the system can then rest on the entire surface of the polygonal contour of the bore and use the full cross-sectional surface of the polygonal receiving bore.
In another advantageous embodiment of the invention, the optional cylinder structure comprises a piston rod, wherein the piston rod has a central bore for supplying a tool clamped in the clamping system with cooling lubricant, and wherein the piston rod penetrates a seal support and ends in a supply space of the spindle.
This seal support separates the supply space in which cooling lubricant is located from the cylinder structure so that the fluidic working medium of the cylinder construction (such as for example compressed air or hydraulic fluid) and the cooling lubricant in the supply space do not come into contact with one another. Even if cooling lubricant is used in the cylinder structure, it should not be mixed with the cooling lubricant in the supply space, since greater purity requirements are placed on the cooling lubricant used in the cylinder structure.
A particularly advantageous embodiment of the invention provides that the seal support comprises a flange and a threaded section with an external thread, wherein an annular groove is formed between the flange and the threaded section. In the region of the threaded section, a gap is formed between the piston rod and the sealing support, and at least one bore connects the annular groove and the gap to one another. In this way, it is possible in a very easy and space-saving manner to convey cooling lubricant from the outside, i.e. from the spindle into the annular groove, through the at least one bore and the gap into the supply space.
According to the invention, at least one bore is provided in the spindle and opens into a space delimited by the annular groove and the spindle. Cooling lubricant is conveyed to the sealing support or the annular groove through this bore.
In order to hydraulically separate the supply space from the cylinder structure, at least one seal is arranged in the flange of the seal support. This seal seals the piston rod relative to the supply space. In addition, in an advantageous development of the invention, a stationary seal can be arranged in the flange, which seal seals the flange of the seal support relative to the spindle.
Further advantages and advantageous embodiments of the invention can be found in the following drawings, the descriptions and the claims. All features disclosed in the drawings, their descriptions and the patent claims can be essential to the invention, both individually and in any combination with one another.
In the drawings:
In the context of the invention, the term “adapter” is used as a generic term for all components or assemblies that can be clamped in a polygonal centering receptacle 7 of a spindle 1 with the aid of the clamping system according to the invention. This can be a tool (e. g., drill, milling cutter, turning tool), an adapter (drill chuck, collet holder, cutting chuck for receiving indexable inserts), a device and more.
As already mentioned several times, the invention is described with reference to a rotatably mounted spindle 1. However, the spindle 1 can also be a fixed spindle.
At its end facing the centering receptacle 7, the adapter 2 has a conical polygonal outer contour, which is also referred to below as an outer polygon. The centering receptacle 7 is shaped complementarily to the outer polygon of the adapter 2. The shape of the centering receptacle 7 is therefore also referred to as an inner polygon. This polygon connection has been established on the market for many years and is standardized, for example, in ISO 26623.
The adapter 2 comprises a profiled hollow shaft 102 which interacts with a clamping system 4 in the spindle 1. These hollow shaft clamping systems have also been known to a person skilled in the art for many years, for example from the documents mentioned in the introduction to the description.
Therefore, the polygon connection of adapter 2 and centering receptacle 7, the clamping system 4 and the cylinder structure 6 are assumed to be known, and only the aspects relevant to the invention are explained.
The spindle 1 can, for example, be part of a driven tool holder. That is to say, the spindle 1 has to be designed relatively compact in order to fit into the limited installation space of the tool holder. Therefore, the potentially available installation space in the interior of the spindle 1 is limited in the radial direction by the outer diameter and the length of the spindle 1.
Nevertheless, the clamping system 4 arranged in the spindle 1 has to fix an adapter 2 with a hollow shaft in the centering receptacle 7 in such a way that very good concentricity and axial run-out of the adapter 2 or the tool attached thereto is ensured at all times. In addition, the torque required for machining and the arising radial and axial forces must be reliably transmitted from the adapter 2 to the spindle 1. High clamping forces are therefore required in the axial direction; the adapters 2 and spindle 1 are clamped relative to one another in order to transmit the resulting forces, torsion and bending moments.
The clamping system 4 is generally clamped and released by a cylinder structure 6, which is actuated fluidically (e.g., pneumatically or hydraulically) and which is also integrated into the spindle 1. It is arranged behind the clamping system 4 in a stepped receiving bore 9 of the spindle 1. Any other systems for applying high axial forces can alternatively be used.
The cylinder structure 6 and the clamping system 4 are mounted from the front, i.e. by a centering receptacle 7 (inner polygon) of the spindle 1. As a result, the maximum diameter of the clamping system 4 and the cylinder structure 6 and the maximum diameter of the receiving bore 9 cannot be greater than the smallest inscribed circle of the centering receptacle 7.
The cylinder structure 6 comprises a piston rod 3 which transitions into a tension bolt 5 of the clamping system 4 or is connected thereto. The cylinder structure 6 must provide comparatively large actuating forces on the piston rod 3. An effective means for increasing the actuating forces is to increase the diameter of the pistons of the cylinder structure 6. However, the maximum diameter is predetermined by the diameter of the receiving bore 9. The diameter of the receiving bore 9 should therefore be as large as possible.
From the comparison of the two positions of the tension bolt 5 in
In order for the clamping process to be carried out reliably both manually and automatically, the front end of the tension bolt 5 serves as a stop for the adapter 2.
The centering receptacle 7 is designed as an inner polygon. It can be an integral part of the spindle 1. However, it can also be a separate component which is inserted into the spindle 1.
A section of the receiving bore 9 adjoining the centering receptacle 7 receives the clamping system 4. A further adjoining section of the receiving bore 9 receives the cylinder structure 6.
Where the receiving bore 9 receives the clamping system 4 and the cylinder structure 6, it is designed as a cylindrical bore with a shoulder 13. In the shown exemplary embodiment, the receiving bore 9 is designed as a blind hole on the right-hand side in
In
The exemplary embodiments of spindles 1 according to the invention shown in
As already mentioned, the centering receptacle 7 is designed as a polygon (e.g. according to ISO 26623). This can be seen, for example, upon more precise examination of
A shoulder 60 arranged concentrically to the central line is denoted by 60 on the end face of the spindle 1. The line 7.1 marked a high point of the inner polygon of the centering receptacle 7. Therefore, the distance in the radial direction between the shoulder 60 and the line 7.1 is small compared to the distance in the radial direction between the shoulder 60 and the line 7.2, which marks a low point of the polygon. The points belonging to the lines 7.1 and 7.2 are marked in
An annular groove 65 is formed in the spindle 1 following the polygonal centering receptacle 7. This circular annular groove 65 is arranged concentrically with respect to the central line. It has a diameter which is equal to or greater than the circumference of the smallest inner polygon of the centering receptacle 7.
In the shown exemplary embodiment, the diameter of the annular groove 65 is approximately as large as the diameter of the “high point” of the inner polygon designated 7.1 in
If the polygonal shape of the collar 67 is “cut” at the outer diameter (for example by twisting off the high points), then the diameter of the annular groove 65 can be smaller than the circumference of the high point 7.1 of the polygon at the transition between the centering receptacle 7 and the annular groove 65. In any case, the diameter of the annular groove 65 has to be somewhat larger than the inner diameter of the smallest polygon, but the axial forces that can be transmitted in the axial direction between the collar 67 and the annular groove 65 are then smaller. It is therefore desirable to use the whole polygonal shape and to select the diameter of the annular groove 65 to be as large as shown in
Due to the polygonal cross section of the centering receptacle 7, a shoulder at the transition between the centering receptacle 7 and the annular groove 65 in the region of the lowest point 7.2 is significantly greater than at the high point 7.1. It can also be seen from the comparison of the distances between the lines 7.1 and 7.2 in the radial direction to the annular groove 65 that the centering receptacle 7 is an inner polygon.
In this exemplary embodiment, the clamping system 4 comprises a spring housing 19. A collar 67 is formed at the front end (left in
Because the outer contour of the collar 67 is somewhat smaller than the smallest inner polygon of the centering receptacle 7, the spring housing 19 can be inserted with its cylindrical part in a certain rotational position through the centering receptacle 7 into the part of the receiving bore 9 located behind the annular groove 65. In this rotational position, the collar 67 fits through the polygonal centering receptacle 7. This situation is shown in
By subsequently rotating the collar 67 relative to the spindle 1, the high points of the collar 67 move into the annular groove 65. A positive-locking fit acting in at least one axial direction is thereby created by the collar 67 between the spring housing 19 and the spindle 1. As a result, the clamping system 4 and the cylinder structure 6 arranged behind the clamping system 4 are axially fixed in the receiving bore 9 in the direction of the centering receptacle 7. In the exemplary embodiment shown in
The insertion of the clamping system 4 and cylinder structure 6 into the spindle 1 and the subsequent production of a positive-locking fit is illustrated in three steps in
These figures represent a plan view of the polygonal centering receptacle 7. The lines belonging to the centering receptacle 7 are designed as dash-dot-dot lines. The lines belonging to the collar 67 are solid.
In
When the collar 67 is rotated relative to the spindle 1 in this axial position, then the high points of the collar 67 dip into the annular groove 65. This results in a positive-locking fit acting in at least an axial direction between the collar 67 and the spindle 1. This situation is shown in
In the shown example, the angle of rotation is 60° between the rotational positions shown in
In the shown exemplary embodiment in
In the embodiment according to
In the exemplary embodiments shown in
For dismantling the clamping system 4 and the cylinder structure 6, the collar 67 is simply rotated counterclockwise by 60° from the rotational position shown in
In order to secure this positive-locking fit generated by rotation and formed in at least one axial direction, a recess 69 is provided at a high point of the collar 67. The recess 69 is located in
In the position of the collar 67 shown in
The securing pin 71 is accessible from the end face of the spindle 1. The threaded bore (without reference sign) in the spindle 1 runs approximately parallel to the centering receptacle 7 and ends in the annular groove 65 (see
The screwing-in or insertion of the securing pin 71 from the end or front side of the spindle 1 has several advantages:
With driven tool holders, no cooling lubricant from the centering receptacle 7 can pass through the threaded bore to the rolling bearings (not shown) with which the spindle 1 is held. If this case should occur, the rolling bearings are damaged.
In addition, the securing pin 71 is easily accessible and can be reached without removing the tool holder, which simplifies maintenance or repair of the clamping system.
A special weight advantage of the type of axial locking mechanism according to the invention and explained with reference to
If the line 7.2 (left of the annular groove 65) in the lower part of
In other words: the locking mechanism according to the invention in the axial direction of the collar 67, here connected to the spring housing 19, does not require any additional space in the radial direction in the spindle 1. It also requires only very little installation space in the axial direction. The required installation space corresponds approximately to the width of the annular groove 65.
A direct positive consequence of maximizing the diameter of the cylindrical part of the receiving bore 9 is that the installation space available for the cylinder structure 6 becomes greater. That is to say that the diameter of the pistons 27 and 31 can be increased and, as a result, greater actuating forces can be provided by the cylinder structure 6 under otherwise identical boundary conditions. In addition, the radial installation space for the clamping system is also maximized, which allows it to be built more “robustly”.
A further advantage of the locking mechanism according to the invention via the collar 67 on the spring housing 19 in the spindle 1 is that the number of components is reduced.
The cylinder structure 6 is described briefly below in
In addition to the cylinder sleeve 17, a spring housing 19 is provided in the receiving bore 9. The spring housing 19 belongs to the clamping system 4. The intermediate floor 15 and the cylinder sleeve 17 of the cylinder structure 6 are accordingly axially fixed in the axial direction by the shoulder 13 and the spring housing 19 in the receiving bore 9. The cylinder sleeve 17 also delimits a pressure chamber 37 of the cylinder structure 6.
There is an opening 21 in the inner diameter of the intermediate floor 15. The piston rod 3 projects through the opening 21. A seal 23, which surrounds the piston rod 3, is formed on the opening 21.
In this exemplary embodiment, the piston rod 3 has a shoulder 25. Starting at the shoulder 25, a piston 27, a piston rod sleeve 29, and a piston 31 are lined up on the piston rod 3.
The piston 31 is screwed onto the piston rod 3 at the right end of the piston rod 3 in
The intermediate floor 15 divides the space delimited by the cylinder sleeve 17 and the receiving bore 9 into two partial chambers. A piston 27, 31 is located in both partial chambers. The pistons 27 or 31 in turn divide a partial chamber into a first pressure chamber 35 and a second pressure chamber 37. Because
In the position of the piston rod 3 shown above the central line in
Due to the movement of the piston rod 3 and the pistons 27, 31, the volumes of the second pressure chambers 37 decrease. The intermediate floor 15 limits the path of the piston 31 to the left in
In both end positions (above or below the central line of
Because two pistons 27 and 31 are attached to the piston rod 3, and these pistons are supplied with a hydraulic or pneumatic force FHydr by the pressurized fluid located in two first pressure chambers 35, the forces of the pistons 27 and 31 add up. The two pistons are connected in parallel. As a result, the cylinder structure 6 can provide relatively large actuating forces relative to the diameter of the piston 27 that is possible in terms of installation space.
If more installation space is present in the axial direction, three or more pistons can of course also be arranged one behind the other on the piston rod 3 and, as a result, the actuating force available on the tension bolt 5 can be further increased, or the fluid pressure required to generate the required clamping force can be reduced.
If the second pressure chambers 37 are now pressurized with pressurized fluid, the piston rod 3 and with it the tension bolt 5 move from the left end position (below the central line) to the right. Here too, an addition of the forces exerted by the pistons 27 or 31 onto the piston rod 3 takes place again. Due to the movement of the tension bolt 5 from the released position into the clamped position, the adapter 2 is pulled into the centering receptacle 7. For reasons of clarity, the adapter 2 is shown in
The pressure chambers 35 and 37 are supplied via control lines 39, 41. In
via this first pressure chamber 35 of the piston 27, the fluid is guided into the first pressure chamber 35 of the piston 31 via a channel between the piston rod 3 and the piston rod sleeve 29 or piston 31. As a result, the radial installation space of the spindle 1 on the right-hand side can be reduced, and space is provided for the seal support 59 which, if coolant is required within the spindle 1, can transfer the coolant into the spindle 1.
The second pressure chambers 37 are supplied with pressurized fluid as required via a second control line 41 (above in
Depending on which of the two control lines 39, 41 is supplied with pressurized fluid, the first pressure chambers 35 or the second pressure chambers 37 are pressurized and accordingly a force directed to the left or right in
Releasable check valves (not shown) can be present in the control lines 39, 41. Like the control lines 39 and 41, the check valves are preferably arranged opposite one another, i.e. offset by 180° in the circumferential direction. In this way, the spindle 1, despite the control lines 39 and 41 and the check valves, is balanced very well. Only a relatively small dynamic imbalance arises even at high rotational speeds. This can also be compensated relatively easily by bores in the circumference of the spindle 1.
The optionally present releasable check valves ensure that the fluid located in the first pressure chambers 35 and the second pressure chambers 37 is held there, also against centrifugal forces which arise when the spindle 1 rotates, and with it the cylinder structure 6. In addition, the piston rod 3 and the tension bolt 5 coupled thereto are thereby held in their positions. This means an additional securing for the clamping system 4 against unintentional release.
In the shown exemplary embodiment in
At the right end of the piston rod 3 in
In this exemplary embodiment, the seal support 59 is screwed into the spindle 1. The seal support 59 comprises a flange 75 and a threaded section 77 with an external thread.
An annular groove 79 is formed between the seal support 75 and the threaded section 77. In the region of the threaded section 77, a gap is formed between the piston rod 3 and the seal support 59 so that cooling lubricant can flow through one or more bores 81 from the annular groove 79 through the gap into the supply space 53. From there, the cooling lubricant passes through the through-bore or central bore 47 into the region of the centering receptacle 7 or into the hollow shaft of the adapter 2.
A movement seal 51 is provided in the seal support 75 and interacts with a sealing section of the piston rod 3 and prevents the undesired escape of cooling lubricant from the supply space 53 in the direction of the cylinder structure 6 and of the clamping system 4, and at the same time also prevents fluid from escaping from the first pressure chamber 35 into the supply space 53.
Furthermore, a stationary seal between the seal support 75 and the spindle 1 is also provided. Both seals seal the first pressure chamber 35 against the supply space 53. They separate the fluid of the cylinder structure 6 from the cooling lubricant.
This design of the seal support 59 has several advantages:
It is built very compactly (especially in the axial direction) because a movement seal and a stationary seal are required only in the seal support 75, and because the gap present in the threaded section 77 between the seal support 59 and the piston rod 3 is used for transporting the cooling lubricant into the supply space 53.
The seal support 59 is also very advantageous from a manufacturing point of view; it can be mounted and removed very easily. The sealing support 59 is screwed in via a pin wrench whose pins enter into complementary bores in the end face of the seal support 59.
Because the exemplary embodiment shown in
Two advantages essential to the invention can be explained well with reference to
The diameter DAB of the receiving bore 9 is marked in
In the solutions known from the prior art, the diameter of the receiving bore is significantly smaller than the smallest inscribed circle of the centering receptacle, for example, because there are shoulders due to threads or stop edges.
Furthermore, in this exemplary embodiment, the collar 67 absorbs axial forces in both directions. The annular groove 65 is only wider than the collar 67 by a minimum necessary for production. The axial position of the spring housing 19 and therefore the clamping set 4 can therefore be adjusted very precisely.
Because the clamping system 4 is axially fixed by the collar 67 in both directions in the annular groove 65, the tolerance chain is very short and, as a result, the range of different types of mass-produced spindles 1 is very low.
In this exemplary embodiment, the piston 27 runs directly in a section of the stepped receiving bore 9. It is possible for the piston 27 to not be circular, but to have a polygonal outer contour. Accordingly, the associated section of the stepped receiving bore 9 is also designed as a polygon. As a result, the surface of the piston 27 can be increased, so that-assuming the same fluid pressure and the same external dimensions of the spindle 1—the actuating forces of the piston 27 are greater.
The arrangement of a tool holder 85, which is fastened to a turret 83 of a machining center, is illustrated with reference to
The spindle 87 with an indicated jaw chuck carries the workpiece so that the workpiece can be turned in the shown configuration.
1 Spindle
2 Adapter
3 Piston rod
4 Clamping system
5 Tension bolt
6 Cylinder structure
7 Centering receptacle
7.1 Line
7.2 Line
9 Receiving bore
11 Recess
13 Shoulder in the receiving bore
15 Intermediate floor
17 Cylinder sleeve
19 Spring housing
21 Opening
23 Seal
25 Shoulder of the piston rod 3
27 Piston
29 Piston rod sleeve
31 Piston
33 Clamping segment
34 Conical contact surface
35 First pressure chamber
37 Second pressure chamber
39 First control line
41 Second control line
47 Through-bore or central bore
51 Seal
53 Supply space
55 Bore
59 Seal support
60 Shoulder
65 Annular groove
67 Collar
69 Recess
71 Securing pin
75 Seal support
77 Threaded section
79 Annular groove
81 Bore
83 Turret
85 Tool holder
87 Spindle of the machining center
102 Hollow shaft DAB Diameter of the receiving bore 9
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2021 126 778.1 | Oct 2021 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2022/078806 | 10/17/2022 | WO |
