• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a high-speed spindle with a machine spindle (3), a release unit and a clamping unit (2) which is adjustable between a clamping position and a release position and at least one clamping element whose displacement radially to the spindle longitudinal axis (42) by an axial position change of a spring-loaded Tension bolt (6) is realized and which is provided for the axial position fixation of one of the high-frequency spindle associated tool or a tool holder (7) by a positive connection and a radial frictional connection. The at least one tensioning element is realized as a blocking ball (13) held in a ball cage (10) for interaction with a corresponding ball seat (14) in the tool or in the tool holder (7).
    公开号:CH705888B1
    申请号:CH02165/12
    申请日:2012-10-29
    公开日:2017-07-14
    发明作者:Schenk Peter
    申请人:Röhm Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a high-speed spindle with a machine spindle, a release unit and a clamping unit which is adjustable between a clamping position and a release position and has at least one clamping element whose displacement is realized radially to the spindle longitudinal axis by an axial change in position of a spring-loaded tension bolt and the is provided for axially fixing a position of the high-frequency spindle associated tool or a tool holder by a positive connection and a radial frictional connection.
    High-speed spindles are characterized by their high speeds greater than or equal to 50 000 1 / min. There are already known various methods for changing and clamping tools or tool holders. A distinction is made between a manual and an automatic clamping system. With the manual clamping system, the tool change and the clamping of the tool are done by hand. In automatic clamping systems, the tension of the tool via a spring and replaceable collets, as known for example from DE 19 920 264 B4.
    When using collets, however, it may come in operation to an axial displacement of the tool along the spindle longitudinal axis, which leads to inaccuracies in the machining of the workpiece. In addition, there is the problem with high-speed spindles with an automatic clamping system with collets that a change of a tool is associated with an exchange of the collets, which is quite time-consuming. By design, automatic tensioning systems based on a shaft taper or hollow shaft taper require a relatively large spindle diameter. Another problem is the solution of the clamping in an automatic clamping system. In this case, pressure is often exerted via a stationary release piston against the spindle bearing. Especially with high-speed spindles, this axial pressure has negative effects on the service life of the spindle bearing.
    The invention is based on the object that in a high-frequency spindle of the type mentioned above, the disadvantages listed above are reduced.
    This object is achieved according to the invention in a high-frequency spindle of the type mentioned in that at least one clamping element is realized as a retained in a ball cage locking ball for interaction with a corresponding ball seat in the tool or in the tool holder. This results in a simple design, also a very compact design of the high-frequency spindle is possible.
    For the high frequency spindle, it is advantageous if at least two locking balls are present. This leads to a better clamping capability of the tool associated with the high-frequency spindle or of the tool holder and thereby better usability by the user and has a positive influence on the concentricity of the high-frequency spindle.
    For the operational capability of the high-frequency spindle, it has proved to be particularly advantageous when the high-frequency spindle has a Schnellfrequenzspindelaussendurchmesser which is smaller than 15 mm, preferably less than or equal to 10 mm. As a result, the inventive high-frequency spindle can also be used in areas that require very compact dimensions of the high-frequency spindle. By way of example, the dental field may be mentioned here.
    For the inventive high-frequency spindle, it is also advantageous if the machine spindle has a clamping set housing for receiving the ball cage, and when the ball cage in the clamping set housing is axially displaceable. Due to the axial displaceability of the ball cage an axial length compensation is realized by the safe insertion of the tool cone is ensured in the spindle cone. This has a constructive advantages, in addition, the functionality of the high-frequency spindle is also ensured by the axial displaceability of the ball cage.
    For the ease of use of the inventive high-frequency spindles, it has also proved to be particularly favorable that the ball cage has a spring, the spring action of the tension spring of the tie bolt is opposite and the axial displacement of the ball cage relative to the clamping set housing provided in the clamping set housing or in the machine spindle Bolt and corresponding slots in the ball cage is limited, so that an active retraction of the tool or the tool holder by the ball cage associated spring, which ball cage has the locking ball for interaction with the corresponding ball seat in the tool or in the tool holder is realized. The resulting active retraction of the tool or tool holder substantially contributes to the ease of handling the high frequency spindle. In addition, this protects the tension spring of the tension bolt against overloading, which has a positive effect on the service life of the high-frequency spindle.
    It is also favorable for the inventive high-frequency spindle when the tension bolt on the tool or the tool holder facing the end has a clamping cone, which is provided for the radial adjustment of the locking balls. This leads to a high reliability of the clamping unit.
    For the invention, it is also advantageous if the locking balls are designed for interaction with the hollow cone shaped tool or the tool holder, wherein the axial position fixing of the Werkzeu ges or the tool holder on the inside of the hollow cone a ball seat, in particular a gripper groove is provided. As a result, an axial displacement of the tool or the tool holder is prevented in the clamping position.
    For the inventive high-frequency spindle, it has also proven to be favorable when the machine spindle is associated with a spindle taper, which is provided to form a frictional engagement with the outside of the hollow cone of the tool or the tool holder. As a result, the centering of the tool or the tool holder is facilitated during insertion of the tool, which thus has a positive impact on the user-friendliness.
    For the inventive high-frequency spindle, it is also advantageous if the position of the ball cage and the locking balls are axially fixed with respect to the tie bolt and the high-frequency spindle is assigned to protect against contamination by suitable sealing elements tool guide sleeve for receiving a tool shank. This ensures operational safety by preventing the ingress of dirt into the high frequency spindle, and moreover, an even more compact design can be realized, further increasing the operational capability and life of the high frequency spindle.
    It has proved to be particularly advantageous if the tool guide sleeve has a control cam, which is provided for the radial adjustment of the locking balls in an axial adjustment of the tension bolt. The interaction of tension bolts and locking balls ensures a high degree of operational reliability of the inventive high-speed spindle with respect to the clamping of the tool shank.
    It is also advantageous if the release unit is realized by a multi-stage single-acting cylinder, which rotates with the clamping unit and the machine spindle and which consists of several piston discs, each with a piston housing and a piston opposite side. By integrating the release unit in the rotating machine spindle and the consequent simultaneous circulation of the release unit with the machine spindle no pressure is exerted on the bearings. Due to the multi-stage of the single-acting cylinder, a higher power transmission is realized on the tension bolt, which allows the use of significantly reduced pressures on the individual pistons. This reduces the requirements for the installed sealing elements and the available space can be optimally used.
    For the reliability and functionality of the inventive high-frequency spindle, it is also of great advantage if a gap between the piston housing and machine spindle is provided for venting the piston opposite side.
    To be particularly favorable, it has also been found, when the release unit is realized by a double-acting cylinder, which is integrally formed with a booster and a tensioning wedge is assigned to interact with at least one release ball. Since the release unit acts directly on the tension bolt, there is no load on the spindle bearing. This leads to increased reliability of the release unit and ensures a long service life of the high-frequency spindle.
    For ease of use and reliability of the inventive high-frequency spindle, it is also provided that in the cocking position by applying compressed air to a release pressure line for power amplification, an axial displacement of the double-acting cylinder is provided in the direction of the tie bolt, via the clamping wedge in a radial movement the release ball and a resulting axial movement of the tie bolt against the restoring force of the spring of the spring-valued tie bolt can be transferred and which is longer than the axial movement of the tie bolt. The resulting power boost reduces the requirement for the pressure to be provided and the sealing elements within the piston.
    For the invention is also beneficial if the outer diameter of the tool shank is normalized and the tool shank outside circumference a ball seat, in particular a gripper groove has. As a result, different tools can be used, which is the ease of use and the versatility of the inventive high-frequency spindle beneficial.
    For a further miniaturization of the inventive high frequency spindle for a wide application, for example in the dental field, it has proved to be particularly advantageous if the outer diameter of the tool shank is less than or equal to 3 millimeters.
    In the following the invention is explained in more detail in exemplary embodiments illustrated in the drawing; show it:
    1 is a sectional view of a first embodiment of the clamping unit of a high-frequency spindle,
    2 is a sectional view of another embodiment of the clamping unit of a high-frequency spindle,
    3 is a sectional view of a first release unit of a high-frequency spindle,
    Fig. 4 is a sectional view of another release unit of a high-frequency spindle.
    Fig. 1 shows a high-frequency spindle 1 with a first embodiment of a clamping unit 2, which is housed in the machine spindle 3. In the figure, it can be seen that the machine spindle 3 is associated with a clamping set housing 4, which is connected in rotation with the machine spindle 3. The illustration is divided into two and shows in the upper half the clamping unit 2 in the tensioned state and in the lower half in the release position. On clamping set housing 4, a tension spring 5 is provided, which counteracts an axial displacement of the tension bolt 6 in the direction of the tool or the tool holder 7. It can also be seen that a bolt 3 is provided in the clamping set housing 4, which engages in a corresponding slot 9 in the ball cage 10 and makes it possible to axially adjust the ball cage 10 along this elongated hole 9 relative to the clamping set housing 4. This axial displacement counteracts a second spring 11, which serves for active retraction of the tool or the tool holder 7. You can see the clamping cone 12 of the tension bolt 6, which biases in the blocking division the at least one locking ball 13 radially outwardly into the ball seat 14 of the tool or the tool holder 7. By this positive connection of the at least one locking ball 13 with the ball seat 14, which is realized in the illustrated embodiment as a ball groove, there is a radial adhesion, which prevents axial displacement of the tool or the tool holder 7 during operation. It can also be seen that the end of the tool or the tool holder 7 facing the tension bolt 6 is shaped as a hollow cone 43. The outer side 15 of the hollow cone 43 of the tool or the tool holder 7 has the same angle as the inner side 16 of the spindle cone 44 of the machine spindle 3. This results in that when retracting the tool or the tool holder 7, an additional frictional engagement between the outer side 15 of the hollow cone 43 and the inside 16 of the spindle cone 44 of the machine spindle 3 takes place. In the release position it is shown that the tension bolt 6 is adjusted against the tension spring 5 and that the tensioning cone 12 no longer interacts with the locking ball 13 in the release position, whereby this can retreat into the ball cage 10, with the result that the tool or the tool holder 7 can be removed from the high-frequency spindle 1. It should also be noted that the frictional engagement of the outer side 15 of the hollow cone 43 with the inner side 16 of the spindle cone 44 is realized by a pressure of the tension bolt 6 on the plane surface 17 of the hollow cone 43.
    2 shows an inventive high-frequency spindle 1 with a further embodiment of the clamping unit 2. The machine spindle accommodates a tool guide sleeve 18 having an opening 19 for insertion of a tool shank 20 and by suitable sealing elements 21, the interior of the high-frequency spindle 1 from contamination protects. In the upper part of the figure, the further embodiment of the clamping unit 2 of the inventive high-frequency spindle 1 is shown in clamping position. In this case, the ball cage 10 is connected to the tension bolt 6 rotatably and the at least one locking ball 13 is adjusted during axial displacement of the tension bolt 6 by a control cam 22 which is mounted on the inner circumferential side of the tool guide sleeve 13, radially between a release position and a clamping position. In the clamping position, the at least one locking ball 13 is pressed into the outer circumferential side of the tool shank 20 arranged ball receptacle 14 and thereby causes a radial frictional connection, which prevents unintentional axial displacement of the tool shank 20 during operation. In the lower half of the figure, the clamping unit 2 is shown in Lösestallung. It can be seen that an axial displacement of the tension bolt 6 in the direction of the tool shank 20 against the tension spring 5 causes the interlocking of the locking balls 13 is lifted with the ball seat 14 of the tool shank 20. In addition, an axial displacement of the tension bolt 6, an active ejection of the tool shank 20 from the tool guide sleeve 18, since the tension bolt 6 interacts with a flat surface 17 of the tool shank 20. On the right side of the figure, a first release unit 23 is indicated, which is shown in detail in FIG.
    Fig. 3 shows a first embodiment of the release unit 23 of an inventive high-frequency spindle 1. The upper part of the figure shows the release unit 23 in clamping position and the lower part shows the release unit 23 in the release position. Since the inner diameter of the machine spindle 3 is very small, a simple release piston can not be realized, since this would require a very high pressure to release the system. In order to increase the piston area, which requires a lower pressure, a plurality of, in the embodiment shown exactly three, piston discs 24 are glued together and connected in series. The release unit 23 rotates with the clamping unit 2 and the machine spindle 3. This integration of the release unit 23 in the rotating machine spindle 3, no pressure on the bearings of the machine spindle 3 is exerted during the release process. The release pressure is thereby fed in centrally via the rear spindle end 25 of the rotor and guided via center bores 26 in the piston disks 24 into the piston chambers 27. The bleeding of the piston opposite side 28 takes place via the outer casing of the piston housing 29. The return air is discharged via relief bores 30, which are mounted centrally on the rear plane surface of the rotor. A face seal 31, which is mounted between the rotor shaft 32 and the last piston disc 24, prevents the exchange of air between the supply and exhaust air. The release unit 23 is fixed axially in the machine spindle 3 by a securing screw 33. In this case, the adjustment of the piston disks 24 from the clamping position into the release position counteracts a return spring 34.
    Fig. 4 shows another embodiment of the release unit 23 of the inventive high-frequency spindle 1. Again, the release unit 23 is shown in the clamping position and in the lower half of the figure in the release position in the upper half of the figure. In the illustrated embodiment, it should be noted that the release unit 23 is realized by a double-acting cylinder 35. This dual effect is realized in the illustrated embodiment in that two pressure lines are provided, wherein the clamping pressure line 36 for clamping and the release pressure line 37 are provided for releasing the clamping unit 2. In this release unit 23 of the piston 38 of the double-acting cylinder 35 does not act directly on the tensioned with a tension spring 5 draw bolt 6. The piston 38 is a clamping wedge 39 associated with the axial displacement in the direction of the draw bolt 6 a radial displacement of a release ball 40 along causes the tension bolt 6 associated slope 41, which in turn causes an axial displacement of the tension bolt 6 in the release position. In this case, the clamping wedge 39 and the bevel 41 of the tension bolt 8 are designed so that a long axial movement of the piston 38 is converted into a short axial movement of the tension bolt 6.
    List of Reference Numerals 1 high-frequency spindle 2 clamping unit 3 machine spindle 4 clamping unit housing 5 tension spring 6 tension bolt 7 tool or tool holder 8 bolt 9 slot 10 ball cage 11 spring 12 clamping cone 13 blocking ball 14 ball seat 15 outside hollow cone 18 inside spindle cone 17 plane surface 18 tool guide sleeve 19 opening 20 tool shank 21 sealing elements 22 Control cam 23 Release unit 24 Piston disk 25 Spindle end 26 Central bores 27 Piston chamber 28 Piston opposite side 29 Outer jacket of the piston housing 30 Relief bore 31 Face seal
    权利要求:
    Claims (16)
    [1]
    32 Rotor shaft 33 Locking screw 34 Return spring 35 Double-acting cylinder 36 Clamping pressure line 37 Release pressure line 38 Piston 39 Clamping wedge 40 Release ball 41 Slant 42 Spindle longitudinal axis 43 Hollow taper 44 Spindle cone Claims
    1. High-speed spindle with a machine spindle (3), a release unit (23) and a clamping unit (2) which is adjustable between a clamping position and a release position and has at least one clamping element whose displacement radially to the spindle longitudinal axis (42) by an axial change in position of a A spring-loaded tension bolt (6) is realized and which is provided for axially fixing a position of the high-frequency spindle associated tool or a tool holder (7) by a positive connection and a radial frictional connection, characterized in that the at least one clamping element as a in a ball cage (10) supported Locking ball (13) for interaction with a corresponding ball seat (14) in the tool or in the tool holder (7) is realized.
    [2]
    2. High-frequency spindle according to claim 1, characterized in that at least two locking balls (13) are present.
    [3]
    3. High-frequency spindle according to one of claims 1 to 2, characterized in that the high-frequency spindle has a Schnellfrequenzspindelaussendurchmesser which is smaller than 15 mm, preferably less than or equal to 10 mm.
    [4]
    4. High-frequency spindle according to one of claims 1 to 3, characterized in that the machine spindle (3) has a clamping set housing (4) for receiving the ball cage (10), and that the ball cage (10) in the clamping set housing (4) is axially displaceable.
    [5]
    5. High-frequency spindle according to claim 4, characterized in that the ball cage (10) has a spring (11) whose spring action of the tension spring (5) of the tension bolt (6) is opposite and the axial displacement of the ball cage (10) relative to the clamping set housing ( 4) in the clamping set housing (4) or in the machine spindle (3) provided bolt (8) and corresponding slots (9) in the ball cage (10) is limited, so that an active retraction of the tool or the tool holder (7) through the the ball cage (10) associated spring (11), which ball cage (10), the locking ball (13) for interaction with the corresponding ball seat in the tool or in the tool holder is realized.
    [6]
    6. High-frequency spindle according to one of claims 4 to 5, characterized in that the tension bolt (6) on the tool or the tool holder (7) facing the end of a clamping cone (12), which is provided for the radial adjustment of the locking ball (13).
    [7]
    7. High-frequency spindle according to one of claims 4 to 6, characterized in that the locking ball (13) for the interaction with the hollow cone (43) shaped tool or the tool holder (7) is formed, wherein for the axial position fixing of the tool or the tool holder (7) on the inside of the hollow cone (43) a ball receptacle (14), in particular a gripper groove, is provided.
    [8]
    8. High-frequency spindle according to one of claims 4 to 7, characterized in that the machine spindle (3) is associated with a spindle taper (44) which is provided for forming a frictional engagement with the outer side (15) of the hollow cone (44).
    [9]
    9. High-frequency spindle according to one of claims 1 to 3, characterized in that the positions of the ball cage (10) and the locking ball (13) with respect to the tension bolt (6) are axially fixed and the high-frequency spindle to protect against contamination by suitable sealing elements ( 21) protected tool guide sleeve (18) for receiving a tool shank (20) is associated.
    [10]
    10. High-frequency spindle according to claim 9, characterized in that the tool guide sleeve (18) has a control cam (22) which is provided for the radial adjustment of the locking ball (13) with an axial adjustment of the tension bolt (6).
    [11]
    11. High-frequency spindle according to one of claims 1 to 10, characterized in that the release unit (23) is realized by a multi-stage single-acting cylinder which rotates with the clamping unit (2) and the machine spindle (3) and of a plurality of piston discs (24). each with a piston housing (29) and a piston opposite side (28).
    [12]
    12. High-frequency spindle according to claim 11, characterized in that for venting the piston opposite side (28), a gap between the piston housing (29) and machine spindle (3) is provided.
    [13]
    13. High-frequency spindle according to one of claims 1 to 10, characterized in that the release unit (23) by a double-acting cylinder (35) is realized, which is formed integrally with a booster and a clamping wedge (39) for interaction with at least one release ball (40) is assigned.
    [14]
    14. A high-frequency spindle according to claim 13, characterized in that in the clamping position by applying compressed air to a release pressure line (37) for increasing the force axial displacement of the double-acting cylinder (35) in the direction of the draw bolt (6) is provided via the clamping wedge ( 39) in a radial movement of the at least one release ball (40) and a resulting axial movement of the tie bolt (6) against the restoring force of the tension spring (5) of the spring-tensioned tie bolt (6) can be transferred and which is longer than the axial movement of the tie bolt (6) ,
    [15]
    15. Tool with a tool shank (20) for locking in a high-frequency spindle according to one of claims 9 to 14, characterized in that the tool shank (20) on the outer circumference side a ball receptacle (14), in particular a gripper groove.
    [16]
    16. Tool with a tool shank (20) according to claim 15, characterized in that the outer diameter of the tool shank (20) is less than or equal to 3 mm.
    类似技术:
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    同族专利:
    公开号 | 公开日
    DE102011056021A1|2013-06-06|
    JP2013116553A|2013-06-13|
    CH705888A2|2013-06-14|
    US20140154024A1|2014-06-05|
    KR101931380B1|2018-12-20|
    CN103128582A|2013-06-05|
    ES2437540B2|2014-09-30|
    CN103128582B|2018-02-13|
    JP6072528B2|2017-02-01|
    KR20130062881A|2013-06-13|
    ITMI20122012A1|2013-06-06|
    US9352398B2|2016-05-31|
    TW201323144A|2013-06-16|
    ES2437540R1|2014-04-07|
    ES2437540A2|2014-01-10|
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    法律状态:
    2020-05-29| PL| Patent ceased|
    优先权:
    申请号 | 申请日 | 专利标题
    DE102011056021A|DE102011056021A1|2011-12-05|2011-12-05|High-speed frequency spindle for use in dental field, has clamping element designed as check ball that is supported in ball cage for interacting with corresponding ball retainer in tool or tool holder |
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