Patent Application
20220410328
The invention concerns a driven tool holder, the spindle of which is put into motion by a free jet turbine. The free jet turbine can be driven by a liquid or gaseous fluid (for example, a cooling lubricant or air) or a two-phase mixture.
DE 10 2009 012 805 A1, EP 3 043 957 B1, EP 2 623 258 B1 and DE 10 2016 212 896 B4 describe the use of a free jet turbine to drive the spindle of a tool holder.
DE 100 41 854 A1 describes a spindle head, the spindle of which is driven with compressed air. A proportional valve is installed to regulate the rotational speed of the spindle. A portion of the excess pressure is broken down in the proportional valve in order to reduce the rotational speed of the spindle as needed.
A proportional valve is a (static) valve that not only allows a few discrete switch positions, but also allows a constant transfer of the valve opening or switch position. Flow valves influence the volume flow [cm3/s] of a fluid. Proportional valves with an input and an output are also referred to as flow valves. There are also proportional valves with more than two work ports.
JP 2006 102 835 A describes a spindle unit comprising two rotors. The rotors are connected to a shared compressed air supply. A similar design is described in U.S. Pat. No. 3,055,12, which describes a dentistry drill also driven by compressed air.
U.S. Pat. No. 3,305,214 describes a differential turbine that is also driven by compressed air, and which comprises two turbine wheels rotating in reverse directions on a shaft. The torque transferred by the turbine wheels to the turbine shaft via a frictionally engaged mechanical linkage depends on the difference between the rotational speeds of both turbine wheels.
The spindle of the tool drive has a tool intake for a tool. Low tool diameters require very high rotational speeds in order to facilitate economical and high-quality processing.
Free jet turbines comprise a rotating rotor and one or more fixed nozzles. The fluid exits the nozzle(s) at a high speed. The fluid makes contact with the rotor, causing the rotor and the spindle to rotate.
The pressure energy of the fluid is converted into kinetic energy in the nozzle(s). The pressure difference of the fluid before and after the nozzle determines the maximum achievable speed of the fluid jet. The product of the speed of the fluid and the cross section of the fluid jet emitted by the nozzle determines the available output of the fluid. The rotational speed and torque of the turbine depend on the diameter of the rotor.
The free jet turbines used in power generation (generally Pelton turbines) work with a constant rotational speed specified by the net frequency. The speed of the water emitted by the nozzles is also constant due to the constant pressure head, and the flow rate is defined by the water supply.
The requirements of small-scale turbines for driving a tool differ considerably from this. Various materials (e.g., steel or aluminium) or diameters of the tools used (e.g., milling cutters or drills with 1 mm or 3 mm diameters) require an adjustment of the rotational speed and the available torque to facilitate effective processing.
With the solutions available, the output and rotational speed of the turbine can solely be adjusted via the pressure difference in the nozzle, and thus the jet speed of the fluid, due to the unalterable nozzle cross sections.
If such fluid-driven tool holders are supplied with cooling lubricant as a work fluid, the cooling lubricant pump present on the tool machine is “misappropriated”. These pumps intended for a different purpose (conveying cooling lubricant to the tool sheaths) often do not allow arbitrary adjustment of the conveying pressure and volume flow. Depending on the characteristic curve of the machine's pump, the pressure can drop and further limit the setting range in the event of larger volume flows.
In order to counteract this, the manufacturers of such tool holders offer a wide range of different tool holders, the turbine of which has been optimised for certain rotational speed ranges and torque ranges depending on turbine diameter, turbine design, and nozzle arrangement. If the relatively narrow work range of a driven tool holder is not suitable for the processing of a specific work piece, the user must obtain an additional tool holder, the turbine of which has a suitable work range for the respective task. The investment costs increase more or less in line with the number of tool holders. Furthermore, optimisation or alteration of the work range of the tool holder during processing is not possible, as the entire tool holder must always be replaced with the tool in order to change the rotational speed or torque of the spindle.
The invention aims to provide a tool holder that overcomes the drawbacks of the current state of technology. In particular, a tool holder that can be flexibly adapted to various materials and tools, and with a wide work range, is provided.
This is achieved with a driven tool holder comprising a spindle with a tool intake and a free jet turbine, whereby the free jet turbine comprises a rotor on the spindle, as the free jet turbine comprises two or more nozzle arrangements and at least one directional valve, each nozzle arrangement is assigned a fluid supply line, and the lines are opened and/or closed with the directional valves.
A nozzle arrangement as described by the invention comprises one or more nozzles. By operating the directional valve(s) of the invention, the nozzle arrangements of a tool holder can be individually or jointly supplied with the pressurised work fluid. This increases the work range of the free jet turbine significantly. For example, the torque of the free jet turbine of the invention can be doubled by activating a second nozzle arrangement of identical design if both nozzle arrangements are concordantly facing the rotor. A different design of the nozzle arrangement, e.g., by changing the number of nozzles and/or altering the output surfaces of the nozzles, can be used to control the output of the free jet turbine in another range under equivalent hydraulic marginal conditions.
Contrary to the state of technology, the invention works with directional valves, which are used to control the supply of one or more nozzle arrangements with pressurised fluid. For reasons of linguistic simplicity, sometimes only a “valve” is referred to when discussing the invention; this always refers to a “directional valve”. Following this, the volume flow of the fluid impacting one or more rotors can be regulated or altered. The rotational speed and torque of the spindle of the tool holder are regulated in an energy-efficient way with minimal loss. The regulation of rotational speed and torque described by the invention is sufficiently precise and requires only little installation space.
If, for example, the hydraulic output provided by a second line is twice that provided by an initial line, the output can be altered significantly in three stages by switching between the first and second line, or simultaneous supply of both lines in a very wide range with equal pressure on the fluid:
The torque that can be applied to the spindle or tool intake is controlled by the activation or deactivation (closing or opening) of lines. The lines or the nozzle arrangements attached to them can be directed toward a rotor or various rotors of the spindle.
Changes in fluid pressure can widen the work range even further.
This means that one and the same tool holder can be used for a wide range of processing types. The required torque can be easily controlled by activating a directional valve.
When the invention is designed optimally, the fluid from the at least two lines or nozzle arrangements drives the spindle in opposing directions of rotation. The directional valve needs only be activated once in order to reverse the direction of rotation. The reversal of the direction of rotation can be realised with only one rotor, if the tool holders described by the invention are being used. This is particularly affordable and requires almost no additional installation room, and the tool holder is thus quite compact. However, it is also possible to install one or more rotors for each direction of rotation and rotational speed.
The work range of the tool holder described by the invention can be further widened if the free jet turbine comprises two or more rotors on the spindle, and each rotor is assigned at least one line. Various rotor diameters allow the rotational speed and torque of the free jet turbine to be optimally adjusted for the material being processed, the processing (scrubbing/smoothing), and diameter of the material.
In many cases it is advantageous if two or more rotors with their respective lines are integrated in a tool holder. This means that multiple free jet turbines are available, each of which is optimised for one work range. One way in which this optimisation can be performed is for the main measurements of the turbine (incl. rotor diameter and width of the scoops of the rotor) and the design of the rotor, as well as the number and layout or dimensions of the nozzles to be optimally coordinated with each other. The turbines can be operated individually or together. Only one directional valve need be activated to do this.
In order for the tool holder described by this invention to be as compact as possible in the tool intake, at least one of the rotors can be located at a second end of the spindle. The second end is opposite the first end of the spindle with the tool intake. According to the invention, there is at least one rotor on the first and second end of the spindle. This allows greater freedom in the design of the tool holder.
The spindle of the tool holder is positioned in a tool holder casing in such a manner that it can be rotated, and the rotors are preferably located on the ends of the spindle protruding beyond the bearing. This makes it easier to install and to seal the bearing against the turbines' work fluid.
Overall, the case with all tool holders described by the invention is that the directional or flow valves are manually, electrically, mechanically, hydraulically, or pneumatically activated. Certain switch positions of the directional valve(s) are repeatable and can be automated. The user can thus always apply a suitable setting (tool, material for processing, switch position of the directional valve(s), and conveyance output of the pump) as needed without having to put in the effort of defining and testing the setting.
Another advantage of the tool holder described by the invention is that it can be very flexibly used in a variety of tool machines. For example, if the tool holder is used on a tool machine, the pump of which only offers a small conveyance flow for the cooling lubricant, only one nozzle arrangement is activated. When using the tool holder on a tool machine with more efficient pump, two or more nozzle arrangements can be active.
The directional valve(s) can facilitate a wide range of combinations of activated nozzle arrangements and rotors, depending on design.
If the tool holder and the machine on which the tool holder is used are equipped with an automatic tool alternation system, various cutting tools can be alternated and then operated with the selected, matching turbine.
A nozzle arrangement can comprise one or more nozzles, which generally have the same design.
It is possible for the fluid conveyed by the pump to be distributed among two or more nozzle arrangements (parallel activation). This in itself facilitates the broad regulation of the rotational speed and the torque exerted on the spindle.
Another variation of the rotational speed and the torque exerted on the spindle is achieved by the invention in that there are two or more rotors with various diameters on the spindle. The rotational speed and spindle torque change depending on which of the rotors is supplied with fluid.
Both control methods facilitated by the invention (activation and deactivation of various nozzle arrangements and supplying various rotors with fluid) can be facilitated by a tool holder and work cumulatively. The rotational speed and torque of one and the same tool holder can thus be broadly regulated.
In an ideal variant of the design of the directional valve described by the invention, this comprises a circular positioning ring and an annular or conical sealing surface in the housing that interacts with the positioning ring. The lines that supply the nozzle arrangements with pressurised fluid are distributed along the circumference of the sealing surface via a central angle α. Depending on the rotational position of the positioning ring relative to the housing, the positioning ring closes or releases one or more of the lines. The more lines that are open, the more fluid flows through the lines to the rotor(s) in total. By turning the positioning ring relative to the housing, the number of nozzle arrangements supplied with the pressurised fluid changes, and with it the torque exerted on the spindle by the rotors supplied with the fluid and which is then supplied at the tool intake for the cutting process.
To this end, a particularly advantageous design of the positioning ring comprises a countersurface to complement the sealing surface of the housing, which is in turn designed as a circular ring or cone with a central angle γ (see
So that the fluid chamber that “moves” with the positioning ring can always be supplied with pressurised fluid regardless of the rotational position of the positioning ring relative to the housing, it is recommended that five or six supply holes be provided in the housing that, from a central line, at least partially divide or penetrate the sealing surface in the housing.
In the case of the tool holder described by the invention, there are two possible means for tool intake in the integration of the spindle. The first possibility is that the spindle comprises a tool intake in which the tool is braced. All tool intakes known from the current state of technology describe this. This concept is also illustrated in
The second possibility is that the tool is integrated into the spindle. This integration allows further miniaturisation and results in less rotational inertia of the rotating components (rotors, spindle, tool). This concept is illustrated in
Further advantages and advantageous designs of the invention can be found in the illustrations, description, and patent claims. All characteristics listed in the illustrations, description, and patent claims can be pertinent to the invention either individually or in any combination with one another.
The illustrations show the following:
b, 22c, 22d, and
The tool holder can be used for all types of tool machines (milling centres, rotating centres, multi-task centres, etc.), and be mounted onto the tool machine via all tool intakes known from the current state of technology (e.g., steep taper, HSK, Coromant Capto, cylinder shaft, etc.).
The bearing of the spindle 3 in the housing 1 is indicated by two (roller) bearings 7.
In this example variant, there are a total of three rotors 9, 11, 13 on the spindle 3. The rotors 9, 11, 13 are firmly and (ir-)revocably connected to the spindle (e.g., via press fit, soldering, or welding), or form one component with the spindle 3. Each of these rotors 9, 11, 13 has a different diameter. The rotors 9, 11, 13 can also form one component and be attached to the spindle 3 as one unit. It is also possible to create the rotors 9, 11, 13 and spindle 3 from one piece.
In this example, each rotor 9, 11, 13 is assigned one nozzle arrangement 15, 17, 19. The nozzle arrangements 15, 17, 19 are each supplied with fluid via a respective line 21, 23, 25.
The driven tool holder 57 described by the invention and its housing 1 is fastened, for example, to a revolver 27 of a tool machine. The tool machine comprises a pump 29 with which cooling lubricant or another fluid can be conveyed. The pump 29 is generally driven by an electrical motor (M). The lines 21, 23, 25 are hydraulically connected with a conveying side 31 of the pump 29.
Between the conveying side 31 and lines 21, 23, 25 are, for example, directional valves 33, 35, 37 or a directional valve (not depicted) with multiple work ports. Each of the directional valves 33, 35, 37 depicted here can be actuated individually. If, for example, the directional valves 35, 37 are closed and only the one directional valve 33 is open, the nozzle arrangement 15 is supplied with fluid conveyed by the pump 29. The fluid emitted from the nozzle arrangement 25 drives the rotor 9.
If, for example, the directional valves 33, 37 are closed and only the directional valve 35 is open, the nozzle arrangement 17 is supplied with fluid conveyed by the pump 29. The fluid emitted from the nozzle arrangement 17 drives the rotor 11. Because at least the rotors 9, 11, 13 are designed differently, the spindle 3 exhibits a different operating rotational speed depending on which of the nozzle arrangements 15, 17, and/or 19 is supplied with fluid from the pump 29.
If the various nozzle arrangements are directed toward the same rotor, the torque on the spindle can be regulated via activation and deactivation of individual lines.
In the example variants depicted in
The directional valves 33, 35, 37 can be actuated independently from one another. Actuation of the directional valves 33, 35, 37 facilitates distribution of the fluid conveyed by the pump 29 among one or more rotors 9, 11, 13. The rotational speed and torque present on the spindle 3 can thus be broadly regulated and adapted to the requirements of various machining tasks.
For example, only the nozzle arrangement 15 is supplied with fluid from the pump 29 if the (directional) valves 35, 37 are closed and only the directional valve 33 is open. The nozzle arrangement 15 supplies the rotor 9 with the fluid. Of the three rotors 9, 11, 13, the rotor 9 has the smallest diameter. Thus the rotational speed of the spindle 3 is the highest when the directional valve 33 is open and the rotor 9 is supplied with fluid, pending the identical design of the nozzle arrangements 15, 17, 19.
If a higher torque is required for another machining task, the (directional) valve 37 can be opened and the directional valves 33, 35 closed, for example.
The rotor 13, with the greatest diameter, is supplied with the fluid from the nozzle arrangement 19. In this switch position, the operating rotational speed of the spindle 3 is the lowest, although the torque is the highest.
If only the directional valve 35 is open, the middle rotor 11 is supplied with fluid, resulting in a medium operating rotational speed and medium torque.
The conveyance output of the pump 29 can also be altered.
Any other combination of switch positions of the directional valves 33, 35, 37 is possible to configure the rotational speed and the torque on the spindle 3. Two or more rotors can be simultaneously supplied with fluid.
Of course, the rotational speed and the torque on the spindle 3 can also be regulated via the pressure on the conveying side 31 or the conveyance output of the pump 29.
It goes without saying that this variant is merely an example. Other combinations are possible, some of which are described in
In the example variant of
In the example variant of
It is generally possible to position the rotors behind or between the bearings, and to select the positioning such that optimal installation geometry and optimal external geometry of the tool holder and/or bearing strain and vibration behaviour is achieved.
Furthermore, the installation room requirements for the rotor 9 are very low at the first end of the spindle 3 where the tool intake 5 is located.
In the example variant of
If the directional valve 39 is integrated into the tool holder 57, one fluid interface between the tool machine and tool holder 57 is sufficient. In this example variant, the tool holder has one fluid connection.
The directional valve 39 in this example variant has four switch positions 1, 2, 3, 4. Each of the switch positions 1 to 3 is supplied with work fluid by a respective nozzle arrangement 15, 17, 19.
In the fourth switch position, the nozzle arrangements 15 and 17 supply the rotors 9 and 11 with fluid simultaneously or parallel. This creates greater torque on the spindle 3 than if only one of the rotors 9, 11, 13 is supplied with fluid. In general, the directional valve 39 facilitates the supply of one or more nozzle arrangements 15, 17, 19 with fluid in a wide range of combinations, depending on the design and switch position.
The parallel actuation of two nozzle arrangements 15 and 17 does not necessarily require two separate rotors 9 and 11. It is also possible to design a rotor more broadly so that two nozzle arrangements influence one rotor. One such configuration is shown in
Furthermore it is possible, with a consistent rotor breadth, to position multiple nozzle arrangements 15, 17, 19 in succession around the circumference of a rotor. The respective rotors can be configured for various nozzle arrangements and fluid conditions in this manner.
For example, the nozzle arrangement 15 can be configured such that a maximum output speed of the fluid is achieved. The nozzle arrangement 17 can be configured such that the output speed of the fluid is lower, but the output cross section of the nozzle arrangement 17 is greater. The nozzle arrangement 17 can thus be used to accelerate the spindle 3 for scrubbing work, while the nozzle arrangement 15 is used for smoothing. Both nozzle arrangements 15, 17 can be directed toward the same rotor 9.
With the example variant schematically depicted in
It is thus possible, for example, to supply the smallest rotor 9 with fluid from the nozzle arrangement 15.1 and/or the nozzle arrangement 15.2. Accordingly, the rotors 11, 13 can also optionally be supplied with fluid from the nozzle arrangement 17.1 and/or 17.2 or 19.1 and/or 19.2.
The number of switch combinations is thus more than doubled, and the application range of the tool holder 57 is expanded significantly. The hydraulic connection to the tool machine or pump 29 can be performed via an interface, as pictured, or via multiple connections.
The diameters of both rotors are the same in this example variant. But this is not required.
If the rotor 9 is supplied with fluid via the nozzle arrangement 15, the spindle 3 rotates clockwise. If the rotor 11 is supplied with fluid via the nozzle arrangement 17, the spindle 3 rotates counter-clockwise. The rotational speed and torque are equal in both rotational directions if the hydraulic configuration of the rotors 9 and 11 is the same.
The reversal of the rotational direction described by the invention facilitates new means of use and functionalities, such as thread cutting and the active braking of the spindle 3. The reversal of the rotational direction is also advantageous for complex machining with two-level tools (one level cutting to the left, the second cutting to the right). This option can be used for reverse machining. It also facilitates simple manual repositioning for a left-/right-cutting tool when setting up the machine.
It is also possible to realise this reversal of rotational direction with one rotor; see
The example variant in
Each fluid has a transfer point between the tool machine or the revolver 27 and the driven tool holder 57.
In the switch position of the directional valve 39 shown in
In the second switch position of the directional valve 39 (not pictured), the nozzle arrangement 15 is supplied with fluid from the first pump 29.1. In a third switch position, the nozzle arrangement 17 that supplies the rotor 11 with fluid is supplied with fluid conveyed by the first pump 29.1. In the fourth switch position of the directional valve 39, both nozzle arrangements 15 and 17 are supplied with fluid either from the first pump 29.1 or the second pump 29.2, depending on the design of the directional valve.
The rotational speeds are limited by fluids such as water or cooling lubricant, but the torque is greater. By switching to compressed air as a work fluid, the rotational speed of the spindle 3 can be greatly increased. This means that the scrubbing process, which requires greater torque, can be performed with water as a work fluid. In the subsequent smoothing process, the spindle 3 is driven with compressed air. Very good surface quality can be achieved due to the considerably higher rotational speed.
In this example variant, the directional valve 39 has two switch positions. This example clearly illustrates how simple it is to switch between various nozzle arrangements.
In all example variants, it is necessary that the fluid conveyed by the nozzle arrangements 15, 17, or 19 onto one of the rotors 9, 11, and/or 13 is subsequently guided out of the housing 1 of the tool holder. This expulsion or diversion of the “used” fluid is not pictured in the
A seal 48 is indicated between the tool intake 5 and the rotor 9.
The (roller) bearings 7 are generally separated from the rotors 9, 11, or 13 by one or more seals 49. The seals can be contacting, non-contacting, or a combination of both.
The directional valves 33, 35 are part of the tool machine; it is also possible to control the nozzle arrangements 15, 17 via a directional valve integrated into the tool holder 57 (not pictured).
However, due to the great rotational inertia of the flywheel mass, it is difficult for the spindle 3 to achieve the operating rotational speed with a small, accelerating turbine.
As shown in
In this example variant, there is a joint diverter 43 for the rotors 9, 11.
Evaluation of the rotational speed of the spindle allows, for example, automated and optimised alternation between the various nozzle arrangements 15, 17, 19. The functionality of the control unit can also be integrated into the evaluation unit 53. The control unit connected to the sensors 51 also facilitates the actuation and operation of the directional valve(s) 35 to 39.
The evaluation unit 53 has direct connections 58 (wireless or via grid connection) with the directional valve 39 and the adjustable flow control valve or the throttle 41, so that the directional valve(s) 33 to 39 and/or the throttle 41 can be actuated depending on the rotational speed or other parameters recorded by the sensor 51. The output data from the sensor 51 can be evaluated, and the control signals transmitted via the connections 58 (e.g., signal lines) can be calculated either in the tool machine 58 or in the evaluation unit 53.
If the evaluation is conducted in the evaluation unit 53, data transmitted by the receiver 55 to the evaluation unit 53 can be included in the calculation. If the evaluation is conducted solely on the tool machine's end, the control signals are transmitted from the receiver 55 to the evaluation unit 53, and from there transmitted to the valves via the connections 58.
Various types of actuation of the directional valve 39 based on this configuration are presented below with
If the actuation bolt 65.1 of the directional valve 39 is moved against the stop 63.1, the actuator of the directional valve 39 is activated and the directional valve 39 adopts a different switch position. The other switch positions of the directional valve can be activated in a similar fashion in that the actuation bolt 65.2 on the other side of the directional valve 39 is moved against the second stop 63.2. This mechanical activation of the directional valve 39 is possible without any further steps for any NC-controlled tool machine. This makes it possible to alternate between the various nozzle arrangements or switch positions of the directional valve 39 during the machining without any considerable interruption to the machining process, meaning that the optimal spindle rotational speed is available for each step of the machining process.
The scoops or bowls 61 of the rotor 9 can be a direct or integral component of the spindle 3. They can be welded to the spindle 3 or mounted onto the spindle 3 and are connected via a shaft-hub connection as per the current state of technology. In the simplified example variant shown in
Following are some general remarks on the example variants.
The configuration of the nozzle arrangements can define the jet speed and/or volume flow of the fluid emitted by a nozzle arrangement. For example, the nozzle arrangement 15 can be configured such that fluid exits the nozzle arrangement 15 at a higher speed than from the differently configured nozzle arrangement 17.
In the tool holder shown in
Around the middle of the housing 1 is a collar 67. A positioning ring 69 described by the invention is positioned to the left of the collar 67 in
Additional fluid connections (92) can be positioned on the positioning ring (69). Via one of the fluid connections (91, 92), the tool holder is supplied with the pressurised fluid required for driving the at least one turbine.
The second fluid connection 92 is a radial connection 92 on the positioning ring 69. The distribution space 86 (see
The positioning ring 69 is pressed against a sealing surface (not visible in
A cover or cap 75 is positioned on the left end of the tool holder in
The cutting process B-B is shown in two variants in which the position of the plug 93 is different. In
In these lengthwise cross-sections 22b, 22c, 22d, the spindle 3 and the bearing 7 as well as a very broad rotor 9 are visible. The fluid path through the housing 1 is further explained in
The first fluid connection 91 passes into a blind hole 77 in the shaft 65. There are multiple supply holes 79 on its end. Eight such supply holes 79 are shown in this example variant.
They begin on the end of the blind hole 77 in the immediate vicinity of the lengthwise axis of the shaft 65; they extend to the front end of the tool holder and face outward. In
There is a second collar 95 at the distribution space 86. This second collar 95 contains multiple (axial) grooves 89 and a cone on one side. This “interrupted cone” is also the sealing surface 81. Multiple radial holes pass inward from this sealing surface between the grooves 89 with a tangential component. These holes are the lines 21, 22, 23, 24, 25, which open or pass into the nozzle arrangement 15, 16, 17, 18, 19.
The course of the lines 21, 22, 23, 24, 25 can be determined from
The alignment of the lines 21 to 25 has a tangential component. A nozzle arrangement 15, 16, 17, 18, 19 is connected to each of the lines. The fluid can exit the nozzle arrangements 15 to 19 at a high speed, and exert a tangential influence on the rotor 9 and cause it to rotate.
The repositioning of the directional valve described by the invention occurs as follows: By twisting the positioning ring 69 relative to the housing 1 or the sealing surface 81, the number of opened or closed lines 21, 22, 23, 24, 25 is set. The volume flow of the fluid that passes through the lines 21, 22, 23, 24, 25 and makes contact with the rotor 9 via the nozzle arrangements 15, 16, 17, 18, 19 changes accordingly. There the fluid exerts an influence with a tangential directional component on the rotor and causes it to rotate. The torque of the rotor 9 depends on the volume flow of the fluid making contact with it, among other things. If the number of opened lines 21 to 25 is changed by the twisting of the positioning ring 69, the torque that the rotor 9 exerts on the spindle 3 and thus on the tool intake 5 also changes. In other words: By activating more or fewer lines and nozzles, the tool holder can be easily adjusted to the machining of various materials and tools with different diameters.
The torque and the rotational speed of the spindle 3 also depend on the speed at which the fluid makes contact with the rotor 9.
The positioning ring 69 is shown in more detail in
If one considers the
The recess 85 is shown in the upper part of
When this hydraulic connection is present, the corresponding line 21 supplies a nozzle arrangement 15 with fluid that flows into the line 21 via the blind hole 77, the supply hole 79, the distribution space 86 and the fluid space 87.
In
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2019 124 761.6 | Sep 2019 | DE | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/EP2020/075558 | 9/11/2020 | WO |
